WO2011099149A1 - 風力発電装置用の増速機および風力発電装置 - Google Patents
風力発電装置用の増速機および風力発電装置 Download PDFInfo
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- WO2011099149A1 WO2011099149A1 PCT/JP2010/052101 JP2010052101W WO2011099149A1 WO 2011099149 A1 WO2011099149 A1 WO 2011099149A1 JP 2010052101 W JP2010052101 W JP 2010052101W WO 2011099149 A1 WO2011099149 A1 WO 2011099149A1
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- planetary
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- outer ring
- pin
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
- F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/70—Bearing or 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
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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
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/40—Transmission of power
- F05B2260/403—Transmission of power through the shape of the drive components
- F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
- F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/31—Wind motors
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
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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
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/085—Bearings for orbital gears
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Definitions
- the present invention relates to a step-up gear for a wind power generator and a wind power generator, and more particularly, a step-up gear for increasing the speed of rotation input from a rotor blade via a main shaft and outputting the speed to the generator side.
- a step-up gear for increasing the speed of rotation input from a rotor blade via a main shaft and outputting the speed to the generator side is related to wind power generators.
- a wind turbine generator generally includes a rotor head to which a rotor blade is attached, a nacelle that houses a drive train and a generator, and a support column that supports the nacelle.
- the drive train is for transmitting torque from the rotor head side to the generator side.
- a speed increaser is incorporated, so that the rotation of the rotor head is increased and input to the generator. It has become.
- a wind speed generator having a planetary planetary gear mechanism As described in Japanese Patent Application Laid-Open No. 2004-228561, a wind speed generator having a planetary planetary gear mechanism is known.
- a planetary planetary gear mechanism a plurality of planetary pins are provided on a carrier that rotates together with the main shaft on the rotor head side, and planetary gears are attached to the planetary pins via planetary bearings. The sun gear is engaged.
- the planetary gear revolves while rotating with the rotation of the main shaft on the rotor head side, and the increased rotation is output to the sun gear side.
- the speed increaser of Patent Document 1 is provided with an oil bath for storing lubricating oil at the lower portion of the housing, and the planetary bearing passes through the lubricating oil in the oil bath when the planetary gear rotates, and is lubricated. It has become so. Further, a lubricating oil supply passage is formed inside the planetary pin, and the lubricating oil injected from the nozzle is supplied to the planetary bearing through this lubricating oil supply passage.
- the life of the planetary bearing may not be sufficient.
- the viscosity of the lubricating oil increases, and the planetary bearing may not be sufficiently lubricated.
- the present invention has been made in view of the above-described circumstances, and an object thereof is to provide a speed increaser for a wind power generator and a wind power generator that further improve the life of a planetary bearing.
- a speed increaser for a wind power generator according to the present invention is a speed increaser that is connected to a rotor head to which a rotor blade is attached and is used in a wind power generator having a main shaft that rotates together with the rotor head.
- a carrier having a plurality of planetary pins, rotating with the main shaft of the wind power generator to revolve the planetary pins, and attached to the planetary pins of the carrier, and a roller is incorporated between the inner ring and the outer ring
- an oil bath for storing lubricating oil in which the planetary bearing is immersed is provided, and the carrier is provided on an outer periphery and both axial ends of the planetary pin, and has an outer cylinder portion that holds the planetary pin,
- the outer cylinder portion of the carrier is inclined such that a surface facing the planetary bearing is separated from the planetary bearing as the distance from the axial center of the planetary pin increases
- the surface of the outer cylinder portion of the carrier provided on the outer periphery of the planetary pin and at both ends in the axial direction is opposed to the planetary bearing, as the planetary pin becomes farther from the center of the planetary pin. Since it is tilted away from the bearing, the lubricating oil easily passes between the outer cylindrical portion of the carrier and the planetary bearing or planetary gear. Therefore, the planetary bearing can be more reliably lubricated, and the life of the planetary bearing can be further improved. For example, the cooling oil viscosity is likely to increase due to a very low outside air temperature.
- the speed increaser of the present invention can also be suitably used for a land-specific wind power generator.
- the planetary gears are supported by the planetary pins by a pair of planetary bearings spaced from each other, and the planetary pins include the pair of planetary bearings. It is preferable that an oil supply port for introducing lubricating oil is provided at a position between the pair of planetary bearings.
- the load applied to each bearing can be dispersed and the life of the bearing can be further improved.
- the lubrication state of a pair of planetary bearings can be maintained by providing an oil filler port at a position between the pair of planetary bearings.
- the inclination angle ⁇ of the surface of the outer cylinder portion facing the planetary bearing with respect to the radial direction of the planetary pin is within a range of 0 ° ⁇ ⁇ 40 °. preferable.
- the inclination angle ⁇ is more preferably in the range of 20 ° ⁇ ⁇ ⁇ 30 °.
- the inclination angle ⁇ of the surface of the outer cylinder portion of the carrier facing the planetary bearing the more easily the lubricating oil passes between the outer cylinder portion of the carrier and the planetary bearing or planetary gear, and the life of the planetary bearing Can be further improved.
- the inclination angle ⁇ is too large, it is difficult to manufacture the carrier. Therefore, as described above, by setting the inclination angle ⁇ within the range of 0 ° ⁇ ⁇ 40 ° (more preferably, 20 ° ⁇ ⁇ ⁇ 30 °), the life of the planetary bearing can be improved and the carrier can be manufactured. And both.
- the planetary bearing has a concave outer ring raceway formed on the inner circumference of the outer ring, a convex inner ring raceway formed on the outer circumference of the inner ring, and the outer ring raceway and the inner ring raceway.
- a self-aligning roller bearing in which a plurality of rows of rollers are provided between the planetary gear and the planetary gear so that an end surface of the outer ring of the planetary bearing is located inside an end surface of the planetary gear. It is preferable that the outer ring of the bearing is fixed with an interference fit.
- the self-aligning roller bearing having alignment is used as the planetary bearing, the durability of the planetary bearing can be maintained even if vibration or impact load is applied to the planetary bearing due to fluctuations in wind force.
- the present inventors have come to recognize that the use of a self-aligning roller bearing as a planetary bearing may reduce the durability time of the planetary bearing due to flaking.
- the reduction in the durability time of the planetary bearing is due to fluctuations in the load and moment transmitted to the planetary bearing (self-aligning roller bearing) through the rotor blades, the rotor head and the main shaft as a result of intensive studies by the present inventors. It became clear that the outer ring slips outward in the axial direction and the load applied to each roller row becomes uneven.
- the spherical roller is fixed to the outer ring of the planetary bearing with an interference fit so that the end surface of the outer ring of the planetary bearing is located inside the end surface of the planetary gear. Flaking that occurs when the bearing is used as a planetary bearing can be prevented. It is considered that this is because the end of the planetary gear is deformed by an interference fit to serve as a lid, the outer ring of the planetary bearing is prevented from coming out, and the load applied to each roller train can be maintained in a uniform state.
- the surface of the outer cylindrical portion of the carrier provided on the outer periphery of the planetary pin and at both ends in the axial direction is opposed to the planetary bearing. Since it is inclined away from the planetary bearing as it gets farther from the center, even if the end surface of the outer ring of the planetary bearing is moved inward from the end surface of the planetary gear, the space between the outer cylindrical portion and the planetary bearing or planetary gear Lubricating oil can pass through reliably.
- the planetary gear is preferably fixed to the outer ring of the planetary bearing by a shrink fit or a cooling fit.
- a flange portion that restricts the outer ring of the planetary bearing from slipping out is provided at a position between the end surface of the outer ring of the planetary bearing and the end surface of the planetary gear on the inner periphery of the planetary gear. It may be.
- the collar portion may be a C-shaped retaining ring fitted in a groove provided on the inner periphery of the planetary gear, or may be screwed onto a female screw provided on the inner periphery of the planetary gear. It may be a ring member.
- a wind turbine generator includes a rotor blade, a rotor head to which the rotor blade is attached, a main shaft connected to the rotor head and rotating together with the rotor head, and speedup of rotation input from the main shaft. And the above-described speed increaser that is transmitted to the output shaft, and a generator connected to the output shaft of the speed increaser.
- the surface facing the planetary bearing of the outer cylindrical portion of the carrier provided on the outer periphery and both axial ends of the planetary pin is further away from the planetary bearing as the distance from the axial center of the planetary pin increases. Since it is inclined so as to be separated, the lubricating oil easily passes between the outer cylinder portion of the carrier and the planetary bearing or planetary gear. Therefore, the planetary bearing can be more reliably lubricated and the life of the planetary bearing can be further improved.
- the surface of the outer cylindrical portion of the carrier that is provided on the outer periphery of the planetary pin and at both ends in the axial direction is opposed to the planetary bearing. As it becomes so, it is made to incline so that it may leave
- FIG. 4 is a sectional view taken along the line II in FIG. 3. It is an enlarged view which shows the periphery of a planetary bearing in FIG. It is sectional drawing which shows the outer ring
- (A) is sectional drawing which shows the example which provided the collar part in the edge part of a planetary gear
- (b) And (c) is an enlarged view which shows the structural example of a collar part.
- FIG. 1 is a diagram illustrating an example of the overall configuration of the wind turbine generator according to the first embodiment.
- the wind turbine generator 1 is mainly composed of a support column 2 erected on the foundation B, a nacelle 4 installed at the upper end of the support column 2, a rotor head 6 attached to the nacelle 4, A plurality of rotating blades 8 attached to the rotor head 6 are used.
- the column 2 has a column shape extending upward from the base B (upward in FIG. 1).
- the column 2 may be constituted by a single column member, or a plurality of units are connected in the vertical direction. And you may comprise in column shape.
- the support column 2 is composed of a plurality of units, the nacelle 4 is installed on the unit provided at the top.
- the nacelle 4 supports the rotor head 6 and houses the drive train 10 and the generator 18 therein.
- FIG. 2 is a diagram showing details of the drive train 10 and the generator 18 inside the nacelle 4.
- the drive train 10 includes a main shaft 12 connected to the rotor hub 6A of the rotor head 6, a speed increaser 14 connected to the main shaft 12, and a cup connecting the speed increaser 14 to the generator 18. Ring 16.
- the main shaft 12 is coupled to the rotor head 6 ⁇ / b> A so as to rotate together with the rotor blades 8 and the rotor head 6, and is rotatably fixed to the casing side by the main bearing 11.
- a grease replenishing port (not shown) for supplying grease is provided on the upper portion of the main bearing 11.
- the speed increaser 14 is arranged between the main shaft 12 and the coupling 16, and increases the rotation input from the rotor head 6 side via the main shaft 12 and outputs it to the coupling 16. .
- the speed increaser 14 increases the rotation of about 20 rpm input from the rotor head 6 side via the main shaft 12 to about 1800 rpm, and then transmits the rotation to the generator 18 via the coupling 16.
- the specific configuration of the speed increaser 14 will be described in detail later.
- the coupling 16 is a shaft coupling that connects the final output shaft of the speed increaser 14 and the input shaft of the generator 18.
- a flexible shaft coupling that absorbs misalignment between the final output shaft of the speed increaser 14 and the input shaft of the generator 18 can be used.
- a brake device 19 including a brake disk 19A and a brake pad 19B is attached to the coupling 16.
- the brake device 19 brakes the coupling 16 by pressing and holding the brake pad 19B against the front and back surfaces of the brake disc 19A.
- the brake pad 19 ⁇ / b> B is always urged toward the brake disk 19 ⁇ / b> A by a spring (not shown), and the brake pad 19 ⁇ / b> B is resisted against the urging force of the spring by hydraulic force during normal operation. You may comprise so that it may keep away from 19A.
- the braking operation of the wind power generator 1 is usually mainly braking by pitch control described later, and the brake device 19 is auxiliary.
- the rotor blade 8 is shifted to the feathering state by pitch control, and the rotation of the rotating shaft is suppressed. It comes to stop.
- the rotor head 6 is fixed to the nacelle 4 so as to be rotatable about a substantially horizontal axis, and a rotor hub 6A to which the rotor blades 8 are attached, and a head capsule covering the rotor hub 6A. 6B.
- the rotor hub 6A is provided with a pitch driving device 30 that changes the pitch angle of the rotary blade 8 by rotating the rotary blade 8 around the axis (in the direction of the arrow in FIG. 2).
- the pitch driving device 30 includes a cylinder 32 and a shaft portion 34 connected to the rotary blade 8.
- the rotary blade 8 is supported by a bearing 36 so as to be rotatable in the pitch direction. For this reason, the rotating blade 8 rotates in the pitch direction together with the shaft portion 34 when the shaft portion 34 rotates by the cylinder 32 of the pitch driving device 30.
- the pitch driving device 30 provided for each rotor blade 8 may be connected to each other by a link mechanism (not shown), and the pitch angle control of each rotor blade 8 may be performed in conjunction with each other.
- FIG. 3 is a cross-sectional view illustrating a configuration example of the speed increaser 14.
- FIG. 4 is a cross-sectional view taken along the line II in FIG.
- FIG. 5 is an enlarged view showing the periphery of the planetary bearing of the speed increaser 14 shown in FIG.
- the speed increaser 14 includes a planetary speed increasing mechanism 50 and a spur gear speed increasing mechanism 70 housed in the casing body 40.
- the speed increaser 14 accelerates the rotation input from the main shaft 12 on the rotor hub side and transmits it to the final output shaft 13 on the generator side.
- the final output shaft 13 of the speed increaser 14 is connected to the generator 18 side by a coupling 16 shown in FIG.
- the planetary speed increasing mechanism 50 of the speed increaser 14 includes a carrier 52, a planet pin 54 held by the carrier 52, a planetary bearing 56 attached to the planetary pin 54, and a planetary bearing 56.
- the planetary gear 58 is supported by the planetary pin 54 via the ring, and the ring gear 60 and the sun gear 62 that mesh with the planetary gear 58 are included.
- the carrier 52 is a holding plate for holding a plurality of (three in this example) planetary pins 54. As shown in FIG. 5, the carrier 52 is formed by outer cylindrical portions 53 provided on the outer periphery and both axial ends of the planetary pins 54. The planetary pin 54 is held. As a result, the carrier 52 rotates integrally with the main shaft 12 on the rotor head side and revolves the planetary pin 54 held by the outer cylinder portion 53. The main shaft 12 and the carrier 52 are rotatably supported by a bearing 42.
- the outer cylindrical portion 53 of the carrier 52 has a surface 53A facing the planetary bearing 56.
- the surface 53A of the outer cylindrical portion 53 is separated from the planetary bearing 56 as the distance from the axial center of the planetary pin 54 increases. Inclined to leave.
- the surface 53A of the outer cylindrical portion 53 of the carrier 52 is inclined away from the planetary bearing 56 as the distance from the axial center of the planetary pin 54 increases, so that lubricating oil from an oil bath, which will be described later, can be removed. It becomes easy to pass between the surface 53A of 53 and the planetary bearing 56 or the planetary gear 58.
- the surface 53A of the outer cylindrical portion 53 facing the planetary bearing 56 preferably has an inclination angle ⁇ with respect to the radial direction of the planetary pin 54 within a range of 0 ° ⁇ ⁇ 40 °, and 20 ° ⁇ ⁇ ⁇ 30 °. It is more preferable to be within the range.
- the lubricating oil further passes between the outer cylindrical portion 53 of the carrier 52 and the planetary bearing 56 or the planetary gear 58. Therefore, the life of the planetary bearing 56 can be further improved.
- the inclination angle ⁇ of the surface 53A facing the planetary bearing 56 of the outer cylindrical portion 53 is too large, it is difficult to manufacture the carrier 52.
- the life of the planetary bearing 56 is improved by setting the inclination angle ⁇ of the surface 53A within the range of 0 ° ⁇ ⁇ 40 ° (more preferably, 20 ° ⁇ ⁇ ⁇ 30 °). Both the manufacturability of the carrier 52 can be achieved.
- the planetary bearing 56 is a roller bearing that supports the planetary gear 58 on the planetary pin 54 so as to be capable of rotating, and has a configuration in which a roller 56C is incorporated between an inner ring 56A and an outer ring 56B as shown in FIG.
- FIG. 5 shows an example of the planetary bearing 56 having two rows of rollers 56C, the rollers 56C of the planetary bearing 56 may be one row or three or more rows.
- the planetary bearing 56 it is preferable to use a self-aligning roller bearing having a centering property from the viewpoint of ensuring durability against vibration and impact load caused by fluctuations in wind power.
- the self-aligning roller bearing for example, as shown in FIG. 5, the outer ring 56B has a concave outer ring raceway on its inner periphery, and the inner ring 56A has a convex inner ring raceway on its outer periphery.
- a configuration in which a plurality of rows of rollers 56C are provided between the inner ring raceways can be used.
- the planetary bearing (self-aligning roller bearing) 56 having such a configuration has alignment because the center of the outer ring raceway of the outer ring 56B coincides with the center of the bearing.
- a plurality of planetary bearings 56 may be arranged in parallel as shown in FIGS.
- a plurality of planetary bearings 56 are arranged with a space therebetween, and the planetary pin 54 is provided with an oil supply port 54 ⁇ / b> A for introducing lubricating oil to the planetary bearings 56. It is preferable to provide in the position between. Thereby, the lubrication state of the planetary bearing 56 can be maintained.
- the ring gear 60 is provided on the casing body 40 and has internal teeth that mesh with the planetary gear 58.
- the sun gear 62 is disposed so as to be surrounded by a plurality of planetary gears 58 as shown in FIG.
- a planetary output shaft 64 is fitted in the sun gear 62.
- the spur gear speed increasing mechanism 70 shown in FIG. 3 is an optional speed increasing mechanism in addition to the planetary speed increasing mechanism 50, and further increases the rotation of the planet output shaft 64 and outputs it to the final output shaft 13. It has become.
- the spur gear speed increasing mechanism 70 includes two sets of a first spur gear 72 and a second spur gear 74 that mesh with each other, and a third spur gear 76 and a fourth spur gear 78 that mesh with each other.
- the first spur gear 72 is fixed to the first rotating shaft 80 connected to the planetary output shaft 64
- the second spur gear 74 and the third spur gear 76 are fixed to the second rotating shaft 82.
- the fourth spur gear 78 is fixed to the final output shaft 13.
- the first rotating shaft 80, the second rotating shaft 82, and the final output shaft 13 are rotatably supported by a first bearing 44, a second bearing 46, and a third bearing 48, respectively.
- the number of teeth of the first spur gear 72 is larger than that of the second spur gear 74, so the first rotating shaft 80 connected to the planetary output shaft 64 on the planetary speed increasing mechanism 50 side. Is rotated and transmitted to the second rotating shaft 82. Further, since the number of teeth of the third spur gear 76 is larger than that of the fourth spur gear 78, the rotation of the second rotation shaft 82 is accelerated and transmitted to the final output shaft 13.
- the planetary speed increasing mechanism 50 and the spur gear speed increasing mechanism 70 increase the rotation input from the main shaft 12 on the rotor hub side to the final output shaft 13 on the generator side. I can tell you.
- the carrier 52 of the speed-up gear 14 has the planetary pin 53 whose surface 53A facing the planetary bearing 56 of the outer cylindrical portion 53 provided at the outer periphery of the planetary pin 54 and at both axial ends.
- the lubricant is inclined away from the planetary bearing 56, so that the lubricating oil easily passes between the outer cylindrical portion 53 of the carrier 52 and the planetary bearing 56 or the planetary gear 58. Accordingly, it is possible to more reliably lubricate the planetary bearing 56 and further improve the life of the planetary bearing 56.
- the viscosity of the lubricating oil may increase due to a very low outside air temperature.
- the speed increaser 14 of the present embodiment can also be suitably used for the wind power generation apparatus 1 having a cold district specification.
- the planetary gear 58 of the speed increaser 14 is supported on the planetary pin 54 by a pair of planetary bearings 56 that are spaced apart from each other.
- An oil supply port 54 ⁇ / b> A for guiding lubricating oil to the planetary bearing 56 is provided at a position between the planetary bearings 56.
- the carrier 52 of the speed-up gear 14 has an inclination angle ⁇ of the surface 53A of the outer cylinder portion 53 facing the planetary bearing 56 with respect to the radial direction of the planetary pin 54 0 ° ⁇ ⁇ 40.
- FIG. 6 is an enlarged view showing the periphery of the planetary bearing when a self-aligning roller bearing is used as the planetary bearing 56.
- FIG. 7 is an enlarged view showing the periphery of the planetary bearing of the speed increaser in the wind turbine generator according to the present embodiment. As shown in FIG.
- the present inventors have an outer ring 56B as a planetary bearing 56 having a concave outer ring raceway on its inner periphery, and an inner ring 56A having a convex inner ring raceway on its outer periphery.
- a self-aligning roller bearing having a configuration in which a plurality of rows of rollers 56C are provided between the raceway and the inner ring raceway, it has been recognized that the durability time of the planetary bearing 56 is shortened by flaking.
- the reduction in the durability time of the planetary bearing 56 is due to the load transmitted to the planetary bearing (self-aligning roller bearing) 56 via the rotor blade 8, the rotor head 6 and the main shaft 12.
- the bearing outer ring 56B slips out in the axial direction (in the direction of the arrow in FIG. 6) due to the variation in the moment, and the load applied to each roller array 56C becomes non-uniform.
- the planetary bearing 56 tends to slip out in the axial direction due to the load and moment transmitted from the rotor blade 8.
- the inner ring 56A of the planetary bearing 56 is restricted from moving outward in the axial direction by the outer cylindrical portion 53 of the carrier 52, while the outer ring 56B of the planetary bearing 56 is not restricted in such a manner. Only the outer ring 56B comes out to the outside in the axial direction. For this reason, the load concentrates on the inner roller train 56C (the roller train on the right side in FIG.
- the end surface of the outer ring 56B of the planetary bearing (self-aligning roller bearing) 56 is positioned inside the end surface of the planetary gear 58 (that is, shown in FIG. 7).
- the planetary gear 58 is fixed to the outer ring 56B of the planetary bearing 56 with an interference fit so that the distance d between the end face of the outer ring 56B and the end face of the planetary bearing 56 satisfies the inequality d> 0.
- the end of the planetary gear 58 (the portion indicated by A in the figure) is deformed by an interference fit to serve as a lid, preventing the outer ring 56B of the planetary bearing 56 from slipping out, and the load applied to each roller array 56C. Can be maintained in a uniform state, and the reduction in the durability time of the planetary bearing 56 can be reduced.
- the distance d between the end surface of the outer ring 56B and the end surface of the planetary gear 58 is preferably as large as possible from the viewpoint of reliably preventing a decrease in the durability time of the planetary bearing (self-aligning roller bearing) 56.
- the distance d is preferably 0 mm ⁇ d ⁇ 10 mm.
- FIG. 8 is a graph showing a measurement result of the amount of slipping out of the outer ring 56B of the planetary bearing 56 in the present embodiment.
- the planetary gear 58 is positioned with respect to the outer ring 56B of the planetary bearing 56 so that the end surface of the outer ring 56B of the planetary bearing 56 is positioned on the inner side of the end surface of the planetary gear 58 as in the gearbox 14 of the present embodiment. It has been found that by fixing with an interference fit, the outer ring 56B of the planetary bearing 56 can be prevented from coming out, and the decrease in the durability time of the planetary bearing 56 due to flaking can be suppressed.
- the surface 53A of the outer cylindrical portion 53 of the carrier 52 facing the planetary bearing 56 is separated from the planetary bearing 56 as the distance from the axial center of the planetary pin 54 increases. It is inclined to. Therefore, as described above, even if the end surface of the outer ring 56B of the planetary bearing 56 is brought closer to the inner side than the end surface of the planetary gear 58, the space between the surface 53A of the outer cylindrical portion 53 and the planetary bearing 56 or the planetary gear 58 is lubricated. Oil can pass through reliably. In the example shown in FIG.
- FIG. 9A is a cross-sectional view showing a flange portion provided on the inner periphery of the end of the planetary gear 58
- FIGS. 9B and 9C are enlarged views showing a configuration example of the flange portion.
- symbol is attached
- a collar portion 90 that restricts the outer ring 56 ⁇ / b> B of the planetary bearing 56 from slipping out is provided at a position between the end surface of the outer ring 56 ⁇ / b> B of the planetary bearing 56 and the end surface of the planetary gear 58. .
- the collar 90 is provided on the inner periphery of the planetary gear 58, thereby reliably preventing the outer ring 56B of the planetary bearing 56 from slipping out.
- the decrease in the durability time of the bearing 56 can be further reduced.
- the collar portion 90 may be a C-shaped retaining ring fitted in a groove 92 provided on the inner periphery of the planetary gear 58 as shown in FIG.
- the ring member may be a screw member screwed into a female screw 94 provided on the inner periphery of the planetary gear 58.
Abstract
Description
この点、特許文献1の増速機では、ハウジングの下部に潤滑油を貯留するオイルバスが設けられており、遊星軸受は、遊星歯車の公転時にオイルバス内の潤滑油を通過し、潤滑されるようになっている。さらに、遊星ピンの内部には潤滑油供給路が形成されており、この潤滑油供給路を介して、ノズルから噴射された潤滑油が遊星軸受に供給される。
一方で、本発明者らは、自動調心ころ軸受を遊星軸受として用いると、フレーキングによって遊星軸受の耐久時間が減少してしまう場合があることを認識するに至った。そして、この遊星軸受の耐久時間の減少は、本発明者らによる鋭意検討の結果、回転翼、ロータヘッドおよび主軸を介して遊星軸受(自動調心ころ軸受)に伝わる荷重およびモーメントの変動によって軸受外輪が軸方向外側に抜け出し、各ころ列にかかる荷重が不均一になってしまうことに起因することが明らかになった。
まず、第1実施形態に係る風力発電装置について説明する。
図1は、第1実施形態に係る風力発電装置の全体構成例を示す図である。同図に示すように、風力発電装置1は、主として、基礎B上に立設された支柱2と、支柱2の上端に設置されたナセル4と、ナセル4に取り付けられたロータヘッド6と、ロータヘッド6に取り付けられた複数枚の回転翼8とで構成されている。
また本実施形態では、好ましくは、増速機14の遊星歯車58は、互いに間隔を空けて配置された一対の遊星軸受56によって遊星ピン54に支持されており、遊星ピン54には、一対の遊星軸受56に潤滑油を導く給油口54Aが、遊星軸受56の間の位置に設けられる。このように一対の遊星軸受56を介して遊星ピン54を遊星歯車58に支持することで、各遊星軸受56にかかる荷重を分散させて、遊星軸受56の寿命をさらに向上させることができる。また一対の遊星軸受56の間の位置に給油口54Aを設けることによって、遊星軸受56の潤滑状態を維持することができる。
さらに本実施形態では、好ましくは、増速機14のキャリヤ52は、外筒部53の遊星軸受56に対向する面53Aの、遊星ピン54の半径方向に対する傾斜角αを0°<α≦40°(より好ましくは、20°≦α≦30°)の範囲内とすることで、遊星軸受56の寿命の改善とキャリヤ52の製作性とを両立することができる。
次に、第2実施形態にかかる風力発電装置について説明する。第2実施形態の風力発電装置は、増速機14における遊星軸受56及び遊星歯車58の端面の位置関係を除けば、第1実施形態と同一である。以下では、第1実施形態と同一の構成要素には、共通の符号を付し、その説明を省略する。
図6は、遊星軸受56として自動調心ころ軸受を用いた場合における遊星軸受周辺を示す拡大図である。図7は、本実施形態に係る風力発電装置における増速機の遊星軸受周辺を示す拡大図である。
本発明者らは、図6に示すように、遊星軸受56として、外輪56Bがその内周に凹面の外輪軌道を有し、内輪56Aがその外周に凸面の内輪軌道を有し、これらの外輪軌道及び内輪軌道の間に複数列のころ56Cが設けられた構成の自動調心ころ軸受を用いると、フレーキングによって遊星軸受56の耐久時間が短くなってしまうことを認識するに至った。そして、この遊星軸受56の耐久時間の減少は、本発明者らによる鋭意検討の結果、回転翼8、ロータヘッド6および主軸12を介して遊星軸受(自動調心ころ軸受)56に伝わる荷重およびモーメントの変動によって軸受外輪56Bが軸方向外側(図6の矢印方向)に抜け出し、各ころ列56Cにかかる荷重が不均一になってしまうことに起因することが明らかになった。
具体的には、遊星軸受56は、回転翼8から伝わる荷重およびモーメントによって、軸方向外側に抜け出そうとする。ここで、遊星軸受56の内輪56Aは、キャリヤ52の外筒部53によって軸方向外側への移動が規制されている一方、遊星軸受56の外輪56Bにはそのような規制はなされておらず、外輪56Bのみ軸方向外側に抜け出してしまう。このため、内側のころ列56C(図6の右側のころ列)に荷重が集中してしまい、遊星軸受56のフレーキングが発生してしまう。
そこで、本実施形態では、図7に示すように、遊星軸受(自動調心ころ軸受)56の外輪56Bの端面が遊星歯車58の端面よりも内側に位置するように(すなわち、図7に示す外輪56Bの端面と遊星軸受56の端面との距離dが、不等式d>0を満たすように)、遊星歯車58を遊星軸受56の外輪56Bに対して締りばめで固定している。これにより、遊星歯車58の端部(図中、Aで示す部位)が締りばめで変形して蓋の役割を果たし、遊星軸受56の外輪56Bの抜け出しを抑制し、各ころ列56Cにかかる荷重が均一な状態を維持して、遊星軸受56の耐久時間の減少を低減することができる。
なお、d=10mmの場合およびd=0の場合のいずれも、遊星歯車58の外輪56Bに対する締りばめは、締めしろがP6(0.012~0.079mm)となるように行った。また遊星軸受56には、1.18kNmの平均トルクに相当する負荷を入力した。
ここで、本発明者らによって、外輪56Bの抜け出し量が400μm程度になると、遊星軸受56のフレーキングが発生してしまうことが分かっている。このため、T1及びT2は、それぞれ、d=10mmおよびd=0の場合における遊星軸受56の耐久時間の指標である。このようにして見積もられた遊星軸受の耐久時間T1及びT2は、d=10mmの場合には、一般的な実製品における合格基準である1.3×105(hr)を超えているのに対し、d=0の場合にはこの基準を満たしていない。
以上から、本実施形態の増速機14のように、遊星軸受56の外輪56Bの端面が遊星歯車58の端面よりも内側に位置するように、遊星歯車58を遊星軸受56の外輪56Bに対して締りばめで固定することによって、遊星軸受56の外輪56Bの抜け出しを抑制し、フレーキングによる遊星軸受56の耐久時間の減少を抑制しうることが分かった。
また、本実施形態でも、第1実施形態と同様に、キャリヤ52の外筒部53の遊星軸受56と対向する面53Aを、遊星ピン54の軸中心から遠くなるにつれ、遊星軸受56から離れるように傾斜させている。このため、上述のように、遊星軸受56の外輪56Bの端面を遊星歯車58の端面よりも内側に寄せても、外筒部53の面53Aと遊星軸受56あるいは遊星歯車58との間を潤滑油が確実に通過可能である。
なお図7に示す例では、遊星歯車58の端部を締りばめで変形させることによって、遊星軸受56の外輪56Bの抜け出しを抑制する例について説明したが、より確実に外輪56Bの抜け出しを抑制する観点から、遊星歯車58の端部につば部に設けてもよい。
Claims (9)
- 回転翼が取り付けられたロータヘッドに連結され、前記ロータヘッドとともに回転する主軸を有する風力発電装置に用いられる増速機であって、
ケーシング本体と、
複数の遊星ピンを有し、前記風力発電装置の前記主軸とともに回転して前記遊星ピンを公転させるキャリヤと、
前記キャリヤの前記遊星ピンに取り付けられ、内輪と外輪との間にころが組み込まれた遊星軸受と、
前記遊星軸受を介して前記複数の遊星ピンに自転可能に支持される複数の遊星歯車と、
前記ケーシング本体に設けられ、前記遊星歯車と噛み合う内歯を有するリング歯車と、
前記複数の遊星歯車に囲まれるように配置され、前記遊星歯車と噛み合う太陽歯車と、
前記ケーシング本体の下部に設けられ、前記遊星ピンの公転によって前記遊星軸受が浸漬される潤滑油を貯留するオイルバスとを備え、
前記キャリヤは、前記遊星ピンの外周かつ軸方向両端に設けられ、前記遊星ピンを保持する外筒部を有し、
前記キャリヤの前記外筒部は、前記遊星軸受に対向する面が、前記遊星ピンの軸中心から遠くなるにつれ、前記遊星軸受から離れるように傾斜していることを特徴とする風力発電装置用の増速機。 - 前記遊星歯車は、互いに間隔を空けて配置された一対の前記遊星軸受によって前記遊星ピンに支持されており、
前記遊星ピンには、前記一対の遊星軸受に潤滑油を導く給油口が、前記一対の遊星軸受の間の位置に設けられていることを特徴とする請求項1に記載の風力発電装置用の増速機。 - 前記外筒部の前記遊星軸受に対向する面は、前記遊星ピンの半径方向に対する傾斜角αは0°<α≦40°の範囲内であることを特徴とする請求項1又は2に記載の風力発電装置用の増速機。
- 前記遊星軸受は、前記外輪の内周に凹面の外輪軌道が形成され、前記内輪の外周に凸面の内輪軌道が形成され、前記外輪軌道および前記内輪軌道の間に複数列の前記ころが設けられた自動調心ころ軸受であり、
前記遊星歯車は、前記遊星軸受の前記外輪の端面が前記遊星歯車の端面よりも内側に位置するように、前記遊星軸受の前記外輪に対して締りばめで固定されていることを特徴とする請求項1に記載の風力発電装置用の増速機。 - 前記遊星歯車は、前記遊星軸受の前記外輪に対して焼ばめ又は冷却ばめにより固定されていることを特徴とする請求項4に記載の風力発電装置用の増速機。
- 前記遊星歯車の内周には、前記遊星軸受の前記外輪の抜け出しを規制するつば部が、前記遊星軸受の前記外輪の前記端面と前記遊星歯車の前記端面との間の位置に設けられていることを特徴とする請求項4に記載の風力発電装置用の増速機。
- 前記つば部は、前記遊星歯車の内周に設けられた溝に嵌めこまれたC形止め輪であることを特徴とする請求項6に記載の風力発電装置用の増速機。
- 前記つば部は、前記遊星歯車の内周に設けられた雌ねじに螺着されたリング部材であることを特徴とする請求項6に記載の風力発電装置用の増速機。
- 回転翼と、
前記回転翼が取り付けられたロータヘッドと、
前記ロータヘッドに連結され、前記ロータヘッドとともに回転する主軸と、
前記主軸から入力された回転を増速して出力軸に伝える、請求項1に記載の増速機と、
前記増速機の前記出力軸に連結された発電機とを備えることを特徴とする風力発電装置。
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KR1020107008806A KR101161484B1 (ko) | 2010-02-12 | 2010-02-12 | 풍력 발전 장치용의 증속기 및 풍력 발전 장치 |
CA2694130A CA2694130C (en) | 2010-02-12 | 2010-02-12 | Gear box for wind turbine generator and wind turbine generator |
US12/674,687 US8657578B2 (en) | 2010-02-12 | 2010-02-12 | Gear box for wind turbine generator and wind turbine generator |
CN201080000721.2A CN102792018B (zh) | 2010-02-12 | 2010-02-12 | 用于的风力涡轮发电机齿轮箱和风力涡轮发电机 |
EP10703610A EP2426355A1 (en) | 2010-02-12 | 2010-02-12 | Step-up gear for a wind-powered electrical generator, and wind-powered electrical generator |
PCT/JP2010/052101 WO2011099149A1 (ja) | 2010-02-12 | 2010-02-12 | 風力発電装置用の増速機および風力発電装置 |
JP2010506740A JP5031091B2 (ja) | 2010-02-12 | 2010-02-12 | 風力発電装置用の増速機および風力発電装置 |
BRPI1000011A BRPI1000011A2 (pt) | 2010-02-12 | 2010-02-12 | caixa de engrenagens para gerador de turbina eólica, e, gerador de turbina eólica |
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- 2010-02-12 BR BRPI1000011A patent/BRPI1000011A2/pt not_active IP Right Cessation
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- 2010-02-12 CN CN201080000721.2A patent/CN102792018B/zh active Active
- 2010-02-12 KR KR1020107008806A patent/KR101161484B1/ko not_active IP Right Cessation
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Also Published As
Publication number | Publication date |
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KR101161484B1 (ko) | 2012-07-02 |
KR20110120200A (ko) | 2011-11-03 |
AU2010201623A1 (en) | 2011-09-01 |
AU2010201623B2 (en) | 2011-09-08 |
EP2426355A1 (en) | 2012-03-07 |
CN102792018A (zh) | 2012-11-21 |
BRPI1000011A2 (pt) | 2018-02-14 |
US8657578B2 (en) | 2014-02-25 |
JPWO2011099149A1 (ja) | 2013-06-13 |
JP5031091B2 (ja) | 2012-09-19 |
CA2694130A1 (en) | 2011-08-12 |
CN102792018B (zh) | 2015-04-01 |
US20120003096A1 (en) | 2012-01-05 |
CA2694130C (en) | 2013-04-16 |
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