CN1035547A - Control hub for adjusting pitch of wind turbo-propeller - Google Patents
Control hub for adjusting pitch of wind turbo-propeller Download PDFInfo
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- CN1035547A CN1035547A CN88101156A CN88101156A CN1035547A CN 1035547 A CN1035547 A CN 1035547A CN 88101156 A CN88101156 A CN 88101156A CN 88101156 A CN88101156 A CN 88101156A CN 1035547 A CN1035547 A CN 1035547A
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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
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Abstract
Becoming slurry in the wind turbine system, slurry elongation degree is decided by a gas-liquid actuator between the crank that is connected on the blade accent oar axle.Oil hydraulic circuit passes in rotor transmission shaft with one heart, by swivel joint, reaches the air charged accumulator on the deflection loader.Transfer the oar axis just to connect, do 1: 1 contrary rotation, be preferably in a side of rotor axis by train of gearings, relative with hydraulic actuator.
Description
The present invention is applied for a patent by Hong Kong Deiya Power Ltd. (Delta Energy Ltd., Hong Kong).The control system of the general relevant wind turbine rotor of invention, the concrete relevant automatic control system that is used for the blade pitch of generator wind turbine, generator links to each other with power supply network.The angle of blade is that pitch can be controlled, and with the adjusting output torque, and in a wind speed scope of design, obtains the highest output power.This is a kind of passive system of fully-machinery type, and is desirable especially, because be not subjected to the influence of environmental factor and sensed system or control system fault relatively, so reliability is arranged.
The controlled rotor of most existing pitches is controlled with positive pitch.Sensor is made sensing to needs, and electromotion system or hydraulic systems are changed pitch.The potential vulnerability in essence of this system is to work as sensed system, or microprocessing systems or actuating system or mechanism can not be adjusted to big propeller pitch angle when breaking down, and turbine is slowed down or stops.
And opposite, even control system has broken down, passive recovery system automatically can be fed back into safe pitch automatically, i.e. the big angle pitch.
General objects of the present invention is to utilize a reliable power machinery system, the output torque of control feather wind turbine, and it controls the pitch of blade automatically with the blade moment variations that wind-force load and centrifugal input cause.
In the passive pitch control system of a kind of double runner rotor of the present invention, the parallel accent oar of two blades axle directly connects with the defeated system of a tooth.The pitch angle depend between the crank on two sharfs, connect the gas-liquid linear actuators.Hydraulic pipe line passes rotor transmission shaft with one heart, by a swivel joint, connects an air charged accumulator.
In the desirable configuration that the contrary wind stabilized deflection wind turbine that waves hub is arranged, parallel blade transfers the oar axis to form a rotor plane, horizontal rotor transmission shaft line, and the rotor transmission shaft line transfers mid point and rotor plane between the oar axis to intersect two.Be bearing on the hub shell with the accent oar axle of transferring oar axis coaxle line respectively.The blade axle head is sizable length of overlap joint mutually.In desirable embodiment, train of gearings connects the side of diaxon at rotor axis.There is being a linear actuators between the crank on the axle, to connect on the opposite side.Best and the train of gearings parallel operation of actuator.Transfer scalable hydraulic pressure leverage and " gas spring " between the oar axle at blade, for direct override capability manually is provided, and can pass through blade feathering autostop.
Fig. 1 shows that for the side of the tower double-leaf contrary wind of the present invention turbine its pitch control rotor hub is in running order.
Fig. 2 be wind turbine along Fig. 1, the overlooking of 2-2 line.
Fig. 3 be rotor hub along Fig. 1, the looking up of 3-3 line.
Fig. 4 is axle head the analysing and observe along the 4-4 line of hub among Fig. 1.
Fig. 5 is the signal of hydraulic system.
Fig. 6 is the wind turbine that is provided with pitch control hub of the present invention, and its predicted power is with respect to the curve of wind speed.
Fig. 1 shows the stabilized deflection installation of using with the synchronous generator coupled of power utilization network of double-leaf wind turbine against the wind.A tower seat 10 is supported liftoff about 70 feet horizontal revolving stage assembly parts 12.A loader 14 is installed on the turntable assembly parts 12, around the vertical axis of turntable assembly parts 12, does the rotation of deflection direction.Transmission axle housing 16 is installed, with the high moment of torsion Hollow Transmission Shafts 17 of shell 16 supporting the insides on the loader 14.
The front end of double runner rotor 18 and transmission shaft is connected, the transmission shaft rear end connects a pair of induction generator 22 and 24 by gear-box 20, and generator can be done the optimization running respectively under the height wind friction velocity, thereby rotor can be rotated by two corresponding designing requirements under optimum operation speed.Be installed in the excess revolutions sprag clutch (not shown) on the gearbox output shaft, can reduce the number of powertrain control circulation and relay box, thereby increase the entire life of equipment, and reduce maintenance.The connection that unidirectional sprag clutch can improve alternator/electrical network with separate.
Fig. 2-4 shows the details of hub 28.Hub 28 has pair of cylinders bearing 34 and 36, and sharf 38 and 40 is bearing in the inside respectively and rotates, and cylindrical bearing 34 and 36 determines blade to transfer the position of oar axis b and c respectively.The eccentric bead 42 and 44 of installing of circle connects the opposite end that blade is transferred oar axle 38 and 40 respectively.Blade 30 and 32(Fig. 1) bead 46 and 48 of coupling is arranged, be installed on bead 42 and 44 with bolt respectively.
The box-shaped pipe stull 50 and 52 that bearing cylinder 34 and 36 usefulness are welded with it forms a firm rigidity square frame.Rotor shaft 17 is connected with hub, shown in Fig. 3 and 4.Mounting bracket 54 will wave hub assembly parts 55 and box-shaped pipe 50 and 52 is rigidly connected.A gear-box 60 is on bearing cylinder 34 and 36 about respective end.Quaternate spur wheel 60 ' be installed in the gear-box and rotate is shown in Fig. 1 and 4.Prototype pitch circle diameter is 9 inches.Two actuation gears 62 and 64 are being transferred coaxial installation on oar axle 38 and 40.Eccentric installation bead 42 is connected with spur wheel 62.Two shaftgears 62 and a pair of driving gear 66 of 64 usefulness and 68 connect does transmission, the plane bias that they are bearing in the gear-box 60 and axis b and c form, as shown in Figure 4.
On the end in addition of bearing cylinder 34 and 36, axis is connected by a rotation bias voltage assembly parts, and the identical crank throw of a pair of placement direction 70 and 72 is arranged in the assembly parts, is rigidly connected with accent oar axle 38 and 40 respectively.Crank throw 72 and the eccentric bead 44-body of installing can be cast when needing.Crank throw 70 and 72 outer end and hydraulic linear actuator 74 are done pivotally connected, and actuator 74 has cylinder body 76, do pivotally connectedly with crank throw 70, and piston rod 78 slides in cylinder, does pivotally connected with crank throw 72.Ideally, compact as far as possible in order to make design, crank throw stretches towards the circular mounting bead, and direction is identical with the knuckle core of gear-box 60, as shown in Figure 2.It is auxiliary that linear actuators 74 can be established the spring bias piece when needing.
Hydraulic system such as Fig. 5 letter are shown.Hydraulic pipe line passes with one heart towards gear-box 20 in rotor transmission shaft, connects by the gentle pressure accumulator of a swivel joint pipe fitting, and other assemblies are installed in the deflection loader 14, as shown in Figure 5.Just hydraulic fluid is freely led to oil groove when forwarding to valve on the closed position, make centrifugal force the complete feathering of blade.
Hydraulic system among Fig. 5 is used to control pitch actuator 74, makes about 70 ° of two blades roll adjustment between feathering and working state.During running, the accent oar moment that the airload on centrifugal force and the blade causes is tended to piston rod is extracted out from linear actuator.This moment increases with wind speed, and direction is identical with wind direction.An air-sac inflated accumulator 80 is arranged, absorb the accent oar moment that piston rod 78 elongations cause and extrude the liquid of linear actuator.Gas-filling bag plays spring action, absorbs the power of aerodynamic moment, thereby the restoring moment that increases is provided, and blade is sent back on the working state.
Some element of hydraulic system is placed in the NEMA 4 casees (NEMA is a U.S. National Electrical Manufacturer Association) as shown in Figure 5
There are four operating modes in this system:
A. pressurization begins operation;
B. load descends the pitch to feathering;
C. during off-load to the pitch of working state;
D. rapid feathering (instruction is stopped).
Shut-off valve 82 cuts out during energising, and electric-motor pump 84 startings increase to running pressure with system pressure.On position when gas spring pressure in the accumulator 80 and liquid stock balance, linear actuator 76 retreat into beginning fully (relative with the working state position in Fig. 5).When reaching running pressure, pump 84 makes it motionless through pressure switch 86.Pump starting when needing is to keep the system pressure of pressure switch area requirement.But when pump quit work, check valve 88 and hydraulic system were isolated.
In operating mode B (pitch turns to feathering under load), the accent oar moment of the centrifugal force when wind speed increases in the turbo driving and aerodynamic increase is tended to piston rod 78 is extracted out from linear actuator 76.The liquid that linear actuator is discharged will be passed through oil hydraulic circuit, suck accumulator 80, bleed valve 90 is arranged, quick-break device 92, the oil hydraulic circuit that from turbine shaft 17 and swivel joint 94, passes through in the loop, quick-break device 96, check valve 98, quick-break device 100 and decompressor 102.Liquid stock increase the gas spring pressure and the system pressure that will increase in the accumulator 80.The accumulator size requirement should be able to absorb the storage under the highest system pressure.Liquid from linear actuator inflow accumulator tends to the rotor blade feathering.
In operating mode C when off-load (on the blade pitch change) to operating condition, the hydraulic fluid reverse flow.When the accent oar moment on the blade reduced because of wind speed, the gas elastic force in the accumulator 80 provided control force, and linear actuator 74 is returned on the working position.This control force is in operating mode B, because of length of spring compressed is stored.When spring when state of equilibrium is return, liquid is discharged from accumulator, pass-out has valve 104 and does not have the identical oil hydraulic circuit of check valve 98, enters actuator.
Operating mode B and C often occur during turbo driving.Because flowage friction and actuator friction cause the loss of stored energy, just must start by the oar pump, keep the pressure in the system.
Operating mode D(makes the rapid feathering of shutdown) be by with solenoid valve 82 outages, hydraulic fluid row is obtained to liquid storage tank 106.The liquid that linear actuator 76 is discharged by centrifugal force or aerodynamic force feathering moment, by solenoid valve 82, enters liquid storage tank through check valve 98.The liquid stream of discharging from accumulator also is introduced into liquid storage tank.Pump 84 must be reset recovery system pressure after the shutdown.
Increase wind-force load and cause blade moment to rise on blade, it reverses and transfers the oar axle.This moment of torsion that increases will run into the resistance that linear actuators 74 more strengthens.Wind-force load is big more, and the control moment of blade is also big more, and blade just is more prone to feathering.
As among Fig. 6 about shown in the curve of this programme, the power curve of being done comprises the scope of 7 to 30 miles per hour wind speed.In linear actuators 74, increase a spring, can make the envelope of curve broadening of running.The shape of curve, peak output output flat segments curve and shutdown tilting section power curve are decided by that all the pitch that changes with wind speed changes program.Two recline pressure curves are represented the design standard of passive control, and passive control can be adopted fluid power, or in the load control area, increase the combination of spring bias voltage.The blade pitch angle approximative value curve representation of passive control.
The blade pitch controller is a passive mechanical device, makes blade in transferring the oar degrees of freedom, seek the equilibrium position voluntarily when condition changes.Some accent oar moments are comprehensive, the pitch equilibrium code of decision rotor.Blade profile, biasing of blade thrust and the biasing of blade centrifugal force produce transfers oar moment, its vector and decision pitch equilibrium code, the pitch equilibrium code determines the power curve feature again.The size of each moment and change can be by the scrupulous blade center of gravity axis of placing, the biasing of control axis and aerodynamic force axis etc. and being changed.The Eulerian angle of the sweepback of blade and taper axis are when performing an analysis and wave all no less importants of dynamic back coupling angle △ 1 and △ 3.
This complete passive rotor control system utilize wind-force and blade intrinsic be used to power, change the pitch of rotor automatically, at fitful wind, strong wind and zero load protection turbine down.Select suitable gas spring, can be with the rotor pitched on given position, to obtain maximum power curve.Reliability that the automatic rotor hub provides and level of security can be saved break, but the weathercock manually-operable.
100 kilowatts of wind turbine systems for utilizing pitch control hub to design that the application discloses also have following mechanical technique to require:
Gear-box 20:
The speed ratio of two outputs is 25: 1 and 37.5: 1,
Full-load efficiency 95%
Low starting torque
First order planetary pinion
The second level spiral gear that dual output is arranged
The unidirectional sprag clutch of output
Two seal structures
Continuous oil-lubricated bearing
Generator:
100 kilowatts 20 kilowatts of power
1800 rev/mins 1800 rev/mins of rotating speeds
Pattern induction type induction type
480 alternating voltages, 480 alternating voltages
Power factor 0.95 0.85
Efficient 94% 91%
Pedestal 405 worm gear drives 284 worm gear drives
The drip-proof type drip-proof type
Structure H class H class
Deflection driven:
Drive 4 °/per second of deflection efficiency
The coasting design of hypervelocity is arranged
Gear was than 800: 1
1/2 horsepower of reversible inductor motor
The gear of transferring gear 62 on the oar axle and 64 the most handy hot hardenings to handle, AGMA(AGMA) the tolerance level is 11.Preferably these gears hot jacket on the axle of sizing mixing is installed, the installation bead of rotor blade is done adjustable installation with circular cone anchor clamps (not shown) on gear and axle, and the adjustable pine of anchor clamps makes blade can do ten/once " timing ", tightens then.But free gear push-and-pull and rotation are to mesh new tooth.Because free gear is replaceable,, adapt to wearing and tearing so can use the metal manufacturing softer than end gear.Preferably free gear is installed on the eccentric part for ease of regulating.
The extreme stress alternation of dimensional range double-leaf wind turbine during the design of this hub can be handled, dimensional range are 50 to 80 feet.Leaf weight increases with the cube of radius.Gravity load on hub and the blade is when blade rotates the rotation of sub-axis, with the change in orientation of blade.In addition, because the center of gravity of blade is at the rear of transferring the oar axis, the gravity item has the less important alternation effect relevant with angle to the pitch angle.The loading off-load of this alternation is born by the design of rigid mount hub.
With the angular velocity square centrifugal force item that is directly proportional, more important than aerodynamic force item in design, rotating speed is transferred in the oar moment at blade reflected.
If needed, the different accumulator of available some pressure, available one or more actuators are handled different load ranges.Yet single actuator/single accumulator can show as all pitch controlling Design of summary of an exquisiteness.
Except that normal operation shown in Figure 6, pitch control hub also can compensate the loss of fitful wind and electric load.Fitful wind is reflected as because the increase of the nose-down pitching moment that the control axis bias causes on blade.This just causes the corresponding direct variation of propeller pitch angle, by blade be used to the power correction, discharge the moment of flexure of blade.The passive spring assembly of pitch control hub can not produce the instantaneous moment of flexure of high torque peak and blade, and make it to reduce by corresponding passive release of fitful wind load.
Just produce the corresponding hypervelocity of rotor along with the reduction of load.The load that the design of passive rotor also can cause hypervelocity descends and is controlled in the safety margin.At last, use passive pitch control hub also can save complicated electronic control logic, interactive sensors and be difficult to check and the feedback loop of running program complexity.With telescopic hydraulic pressure leverage, form direct and effective override capability at blade pitch load and gas spring chien shih, further improve the reliability of system.Feathering by blade provides automatic and manual shutdown function, just need not increase braking member or control unit.
Above-mentioned embodiment purpose is only for narrating not for being restricted. Can do many variations and increase and decrease to the system that discloses and not break away from principle and the spirit of invention. For example can be to spur gear 62,64,66 and 68 power train changes on demand, produces and the direct-connected contrary rotation of blade. And gear train and linear actuators can change along the position of transferring oar axis b and c. If any sufficient space, also power train can be placed on other positions, for example be placed on hub in the heart, one (as shown) or a plurality of linear actuators are connected with crank throw on the blade axle head that is connected the bearing cylinder. Also can do to hydraulic system other modification. An available double acting cylinder is for example initiatively shifted blade onto all-cis oar state when needing. In any case scope of the present invention is decided by accompanying claims and the literal that is equal to it.
Claims (22)
1, have in the feather control wind turbine hub following:
A housing has the parallel blade of spacing to transfer the oar axis to be limited in the plane with a pair of, and near the rotor axis this plane and this two mid point of transferring between the oar axis intersects,
A pair of sharf is bearing on this shell, does part rotation at least around the corresponding oar axis of transferring,
A train of gearings (device) two is transferred between oar axis (in a side of this rotor axis) and is laterally connected at this, this sharf is directly connected do contrary rotation, bearing the stress alternation of blade, and the pitch angle of two blades is interrelated,
Separate not directly machine control unit to this train of gearings effect with this train of gearings, with the starting pitch angle bias voltage of this sharf to a demarcation, to bear the total load of blade, the pitch angle during the decision running initiatively.
2, as the hub in the claim 1, it is characterized by this train of gearings has quaternate coplane spur wheel.
3, as the hub in the claim 2, it is characterized by four spur wheels has two driving gears, and each coaxial installation on corresponding accent oar axle has at least two driving gears and driving tooth crop rotation to be in transmission connection.
4, as the hub in the claim 1, it is characterized by have in this control gear following:
Each sharf has the crank of a circumferentially extending,
The device that connects between this crank changes the relative displacement of crank with blade loads, do controllable variation.
5, as the hub in the claim 4, it is characterized by this machine control unit that connects between this crank has a linear actuators, and its cylinder body and a crank are done pivotally connected, and a piston rod and another crank are done pivotally connected.
6, as the hub in the claim 5, it is characterized by this linear actuators is oil hydraulic cylinder.
7,, and a hydraulic system is arranged in addition as the hub in the claim 5, wherein have pressurization device and with the oil hydraulic circuit of this rotor axis coaxial line, this pressurization device is connected with this oil hydraulic cylinder.
8,, it is characterized by this pressurization device and this rotor axis relative fixed as the hub in the claim 7.
9, as the hub in the claim 8, it is characterized by this hydraulic system has on-off valve device in circuit apparatus for hydraulic in addition, so that make manual feathering.
10, as the hub in the claim 6, it is characterized by this linear actuators has spring-loaded.
11, as the hub in the claim 5, and a pair of circular blade mounting flange is arranged in addition, respectively determine a blade installation Flange Plane, have device that each mounting flange is connected with the respective vanes eccentric shaft, Flange Plane is laterally transferred the oar axis, and the center-biased of blade flange.
12, as the hub in the claim 11, it is characterized by each blade installation flange at same direction upper offset, crank roughly stretches to the axis of respective vanes flange.
13, have in the feather control wind turbine system following:
A deflection loader,
A rotor wherein has a hub, has the blade of two variablepistons at least, be installed on the hub on the accent oar axle of skew,
Driveline is done rotatable the connection with this rotor with this loader,
A hydraulic actuator (device) is directly pivotally connected between this two accent oar axle, thereby corresponding blade pitch load directly acts on mutually by this actuator,
Inflation hydraulic accumulator on this loader, the pressure oil pressurization to the inside,
The hydraulic connecting rod device makes this actuator devices be connected with this accumulator apparatus this hydraulic fluid guiding.
14,, and there is device will transfer the oar axle to do 1: 1 contrary rotation in addition as the system in the claim 13.
15, as the system in the claim 13, and control valve unit is arranged in addition, discharge the pressure in this hydraulic pressure leverage device according to halt instruction.
16, as the system in the claim 15, and the electric-motor pump device is arranged in addition, hydraulic fluid is injected this accumulator apparatus,, be elevated to predetermined working pressure by this hydraulic pressure leverage.
17, as the system in the claim 16, and there is pressure switch apparatus to be connected in addition,, keeps rated working pressure to this energising of electric-motor pump device or outage with this hydraulic pressure leverage.
18, as the system in the claim 15, it is characterized by this control valve unit is solenoid valve.
19,, it is characterized by this leverage device essentially concentric in this driveline and pass as the system in the claim 13.
20, have in the feather control wind turbine hub following:
A housing has the parallel blade of spacing to transfer the oar axis to be limited in the plane with a pair of, and near the rotor axis this plane and this two mid point of transferring between the oar axis intersects,
A pair of turbine blade axle is bearing on this shell, does part rotation at least around the corresponding oar axis of transferring,
Transfer the coplane train of gearings that laterally connects between oar axis at this for one, directly be connected with this sharf and do counter-rotating, bear the stress alternation of blade, and the propeller pitch angle of blade is interrelated,
Being installed in this train of gearings has a pair of corresponding crank on this a pair of sharf of spacing,
A remote-controlled gas-liquid linear actuators directly connects between this crank.
21, as the hub in the claim 20, it is characterized by this axle that this train of gearings connects this rotor axis one side, this linear actuators is connected this rotor axis this between centers of side in addition.
22, as the hub in the claim 1, it is characterized by has an elastomeric hub that waves in this housing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN88101156A CN1009020B (en) | 1988-02-29 | 1988-02-29 | Control hub for adjusting pitch of wind turbo-propeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN88101156A CN1009020B (en) | 1988-02-29 | 1988-02-29 | Control hub for adjusting pitch of wind turbo-propeller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1035547A true CN1035547A (en) | 1989-09-13 |
| CN1009020B CN1009020B (en) | 1990-08-01 |
Family
ID=4831658
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN88101156A Expired CN1009020B (en) | 1988-02-29 | 1988-02-29 | Control hub for adjusting pitch of wind turbo-propeller |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1009020B (en) |
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN100390426C (en) * | 2002-04-24 | 2008-05-28 | 威斯塔斯风力系统公开有限公司 | Wind turbine, hydraulic system, air bleed system and method for controlling at least two wind turbine blades |
| CN101487446A (en) * | 2008-01-18 | 2009-07-22 | 通用电气公司 | Speed controlled pitch system |
| CN101608603A (en) * | 2008-06-09 | 2009-12-23 | 歌美飒创新技术公司 | The method of the blade pitch in wind energy facility and the modification wind energy facility |
| CN101713375A (en) * | 2008-09-30 | 2010-05-26 | 通用电气公司 | System and method for controlling a wind turbine during loss of grid power and changing wind conditions |
| CN101994649A (en) * | 2009-08-12 | 2011-03-30 | 再生动力系统股份公司 | Method and assembly for automatic configuration parameter monitoring in wind energy assemblies |
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| CN102317622A (en) * | 2008-12-15 | 2012-01-11 | 维斯塔斯风力系统集团公司 | Pitch control of a wind turbine |
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- 1988-02-29 CN CN88101156A patent/CN1009020B/en not_active Expired
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| CN100390426C (en) * | 2002-04-24 | 2008-05-28 | 威斯塔斯风力系统公开有限公司 | Wind turbine, hydraulic system, air bleed system and method for controlling at least two wind turbine blades |
| CN101583793B (en) * | 2006-10-11 | 2011-11-30 | 歌美飒创新技术公司 | System for rotating a wind turbine blade |
| CN101319655B (en) * | 2007-06-04 | 2013-03-20 | 西门子公司 | Method and device for controlling load reduction for a wind turbine rotor |
| CN101387267B (en) * | 2007-09-12 | 2013-05-29 | 西门子公司 | wind turbine , Yaw system, controller and method for reducing the system load |
| CN101868621B (en) * | 2007-12-28 | 2013-01-16 | 川崎重工业株式会社 | Upwind type wind wheel and method of operating the same |
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| CN102203411B (en) * | 2008-09-25 | 2014-09-03 | 桑基奥能源公司 | Device for adjusting the blade pitch of a wind generator |
| CN101713375A (en) * | 2008-09-30 | 2010-05-26 | 通用电气公司 | System and method for controlling a wind turbine during loss of grid power and changing wind conditions |
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