CN104879278B - wind power plant - Google Patents
wind power plant Download PDFInfo
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- CN104879278B CN104879278B CN201410620692.XA CN201410620692A CN104879278B CN 104879278 B CN104879278 B CN 104879278B CN 201410620692 A CN201410620692 A CN 201410620692A CN 104879278 B CN104879278 B CN 104879278B
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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
The present invention provides a kind of wind power plant, can be further reduced the destruction of yawing unit.The wind power plant of the present invention has：Pillar；Nacelle is turned round relative to the pillar；Swiveling gear (20), is set to pillar；1st brake apparatus (Br1) i.e. sliding bearing (18), brakes the revolution of nacelle not via the swiveling gear；And multiple 2nd brake apparatus (Br2) i.e. yawing unit (100) and brake unit (200), with the revolution pinion gear (22) engaged with swiveling gear, and by being braked to brake the revolution of nacelle via swiveling gear to the rotation of the revolution pinion gear, wherein, multiple 2nd brake apparatus include the yawing unit (100) with braking function of revolution driving nacelle, A is set as in the maximum assumed value for the external force for being intended to be turned round nacelle, the brake force of 1st brake apparatus is set as B, when the aggregate value of the brake force of the 2nd brake apparatus of part is set as C, (A B) ＜ C are set up.
Description
This application claims the priority based on 2 months 2014 Japanese patent applications filed in 27 days the 2014-037389th.
The entire content of this Japanese application is incorporated by reference in this manual.
Technical field
The present invention relates to a kind of wind power plants.
Background technology
Just like Fig. 6 and wind power plant shown in Fig. 7 disclosed in patent document 1.
The wind power plant 912 has：Pillar 914；Nacelle 916 is assembled into and is rotated freely relative to the pillar 914；
And blade 917.Nacelle 916 is rotatably assembled in pillar 914 via sliding bearing 918.Pillar 914 is provided with swiveling gear
920, yawing unit 924 is assembled in nacelle 916, the yawing unit 924 has the small tooth of revolution engaged with swiveling gear 920
Wheel 922.Yawing unit 924 is provided with 4 in the wind power plant 912 involved by the patent document 1.
Each yawing unit 924 has motor 930, speed reducer 932 and arrestment mechanism 934, in the output shaft of speed reducer 932
933 are provided with the revolution pinion gear 922.If driving revolution pinion gear 922, the revolution pinion gear 922 is by from revolution
The engagement reaction force of gear 920 and revolve round the sun around the axle center C920 (the axle center C914 of=pillar 914) of swiveling gear 920.
Entire yawing unit 924 revolves round the sun around the axle center C920 of swiveling gear 920 as a result, therefore nacelle 916 can be relative to pillar
914 are turned round.
Also, the arrestment mechanism 934 by making each yawing unit 924 works to carry out the rotation for turning round pinion gear 922
Braking, so as to be braked via swiveling gear 920 to the revolution relative to pillar 914 of nacelle 916.
On the other hand, it as the structure that nacelle 916 is rotatably supported relative to pillar 914, discloses in patent document 1
There are the structure for having used rolling bearing (illustration omitted) and the structure for having used sliding bearing 918.Wherein, sliding bearing has been used
In 918 structure (with reference to figure 7), make the sliding bearing 918 while have the function of to support nacelle 916 and returning to nacelle 916
Turn to assign the braking function braked.Specifically, should be configured to the sliding bearing 918 of braking function, it is fixed on surrounding
The mode of the shaft bearing plate 919 of 914 side of pillar is provided with the 1st~the 3rd material for sliding bearing 921A~921C, and (passes through setting
The resistance to sliding of the sliding bearing 918) defined brake force can be obtained.
Patent document 1 is configured to, and when having a power failure under high wind, reduces the brake force of yawing unit 924, so that 916 energy of nacelle
Enough turned round.
Patent document 1：Japanese Unexamined Patent Publication 2011-127551 bulletins (Fig. 1~Fig. 4)
Patent document 1 is configured to, and when having a power failure under high wind, reduces brake force, so that nacelle can be turned round.However,
Actual conditions are can not fully to prevent the breakage of yawing unit, sometimes result in yawing unit breakage.
Invention content
The present invention completes to solve this existing issue, and subject is that providing one kind can be further reduced
The damaged wind power plant of yawing unit.
The present invention solves the above subject by such as lower structure：A kind of wind power plant, has：Pillar；Nacelle, relatively
It is turned round in the pillar；Swiveling gear is set to the pillar；1st brake apparatus, not via the swiveling gear to described
The revolution of nacelle is braked；And multiple 2nd brake apparatus, there is the revolution pinion gear engaged with the swiveling gear, and logical
It crosses and the rotation of the revolution pinion gear is braked and the revolution of the nacelle is braked via the swiveling gear,
In, the multiple 2nd brake apparatus includes the yawing unit with braking function of nacelle described in revolution driving, is being intended to make institute
The maximum assumed value for stating the external force of nacelle revolution is set as A, the brake force of the 1st brake apparatus is set as to B, by part described the
When the aggregate value of the brake force of 2 brake apparatus is set as C, (A-B) ＜ C are set up.
The inventors of the present invention actually the mechanism of yawing unit breakage is studied, verify as a result, having obtained up to now
The brand-new opinion of design philosophy (different from previous design concept) that can not cope with.Above structure is based on the opinion
Structure (detailed content carry out aftermentioned).
Based on the opinion, of the invention includes revolution driving as the 2nd brake apparatus braked via swiveling gear
The yawing unit of nacelle, also, be intended to make the maximum assumed value of external force that nacelle turns round to be set as A, will be not via swiveling gear
The brake force of the 1st brake apparatus braked to the revolution of nacelle is set as B, by the 2nd brake apparatus of (and not all) part
The aggregate value of brake force when being set as C, (A-B) ＜ C are set up.
And, in the present invention it is possible to by the braking of at least 1 the 2nd brake apparatus in the multiple 2nd brake apparatus
Power is set greater than other the 2nd brake apparatus.
Thereby, it is possible to be further reduced previous inventive concept fail reply yawing unit breakage.
In accordance with the invention it is possible to obtain to be further reduced the damaged wind power plant of yawing unit.
Description of the drawings
Fig. 1 is the diagrammatic top of the major part of the wind power plant involved by an example of embodiments of the present invention
Figure.
Fig. 2 is the sectional view of the configuration example of the yawing unit in the embodiment for represent Fig. 1.
Fig. 3 is the sectional view of the configuration example of the brake unit in the embodiment for represent Fig. 1.
Fig. 4 is the sectional view for the configuration example for representing large capacity yawing unit.
Fig. 5 is the diagrammatic top view of the configuration example of another embodiment of the present invention.
Fig. 6 is the whole diagrammatic side view for representing existing wind power plant.
Fig. 7 is to represent that the major part of the structure near the yawing unit and swiveling gear of existing wind power plant is shown
Meaning sectional view.
In figure：12- wind power plants, 14- pillars, 16- nacelles, 18- sliding bearings (the 1st brake apparatus), 20- revolutions
Gear, 122- revolution pinion gears, 100- yawing units (the 2nd brake apparatus), 200- brake units (the 2nd brake apparatus), outside A-
The maximum assumed value of power, the brake force of the 1st brake apparatus of B-, the aggregate value of the brake force of the 2nd brake apparatus of C- parts.
Specific embodiment
Hereinafter, an example of embodiments of the present invention is described in detail with reference to the accompanying drawings.
As previously mentioned, the present invention is the result gained studied the Breakage Mechanism of yawing unit, verified based on reality
To brand-new opinion and make.
It summarizes to the opinion, approximately as.
[opinion 1] respective revolution pinion gear makes nacelle when each yawing unit driven respectively by the driving force of motor
When being turned round, the direction of the revolution pinion mate swiveling gear imparting torque of each yawing unit is consistent.Each yawing unit is somebody's turn to do
The deviation of torque is also smaller, and each yawing unit pushes the revolution of nacelle jointly.
[opinion 2] however, motor stops and yawing unit has following tendency when entering on-position：With make nacelle into
It is compared during row revolution, the deviation bigger of the load equalization (load that each yawing unit is born) of each yawing unit.But as long as
Remains stationary, there will be no the generations of great load.
[opinion 3] when the arrestment mechanism of yawing unit fail to sustain external force and skid off " after ", it may appear that it is very big
Load is unbalanced (load deflections that each yawing unit is born are very big).In addition to this, after skidding off or even to connect each yaw single
The direction of load suffered by member also becomes different.
Being somebody's turn to do [opinion 3] is and the antipodal concept of the concept of existing opinion.
Think in the past, such as the brake force of yawing unit is set as very strong, even if be applied with stronger external force always
Stationary state is maintained yawing unit to be caused damaged in this method of anti-skidding.Therefore, such as institute in above patent document 1
Show, reduce brake force when having a power failure under high wind nacelle deliberately to be made to be turned round and (be rotated each component of yawing unit),
This is considered as that the yawing unit is protected not played a role by damaged " release mechanism ".
However, the inventors of the present invention actually the Breakage Mechanism of yawing unit is studied, verify as a result, specifying that this is existing
Have that opinion is not appropriate, be easy to cause yawing unit breakage instead.
The reason is not very clear and definite, but it is as follows that may infer that：Nacelle with very big quality is in the most upper of pillar
Portion by the high wind of the brake force more than brake apparatus and when " revolution ", the shaking of the supported mechanism of nacelle, i.e. pillar
The inclined influence of the deviation in axle center and the axle center of nacelle or two axle center becomes apparent.I.e., it is possible to be construed to, it is set to nacelle
The revolution pinion gear of side is directly influenced via the swiveling gear for being set to pillar side by the shaking, therefore is caused single in yaw
Member, which generates great load or direction loaded, becomes different.
Also, it is further acknowledged according to the result of research, verification, is blowing the high wind that can generate this arrestment mechanism and skid off
When, great external force is instantaneous in many cases and is continually applied to yawing unit, and all parts are slided at a high speed from generation
Time until rotation is extremely short.This expression takes the countermeasure of torque-limiting to have little time from the time for the situation,
Actually hardly possible realization.
Based on the above situation, the inventors of the present invention have obtained following opinion：" in braking, it can be with even if being applied on nacelle
It is assumed that maximum external force, the nacelle is made still to maintain stationary state " this design concept be less susceptible to lead to breakage instead.
Therefore, it in the wind power plant involved by an example in embodiments of the present invention, is employed based on the opinion
Such as lower structure.
First, explanation is proceeded by from the basic structure of the wind power plant 12.With reference to figure 1, Fig. 2, the embodiment
Involved wind power plant 12 has：Pillar 14；And nacelle 16, it is assembled into and is turned round freely relative to the pillar 14.Nacelle
16 are pivotally assembled in pillar 14 via the sliding bearing 18 with braking function.
The sliding bearing 18 is equivalent to " the 1st brake apparatus Br1 " of present embodiment.Here, so-called 1st brake apparatus
Br1 refers to the brake apparatus braked not via swiveling gear 20 to the revolution of nacelle 16.
When using " sliding bearing 18 with braking function " as the 1st brake apparatus Br1, specifically, for example may be used
With using structure recorded in the patent document 1 illustrated using Fig. 7.The brake force produced can pass through shaft bearing plate
The selected etc. of the raw material of 919 or the 1st~the 3rd material for sliding bearing 921A~921C is adjusted.As referred to below
, such as following mechanism can be set：For example, material for sliding bearing is adjusted to shaft bearing plate by adjusting the decrement of spring
Pressing force, so as to change the mechanism of brake force.The brake force generated by sliding bearing 18 is either turned round in nacelle 16
When still braking (when static), play a role always.
Pillar 14 is provided with swiveling gear 20, yawing unit 100 as shown in Figure 2 is assembled in nacelle 16.Yaw is single
Member 100 has the revolution pinion gear 122 engaged with swiveling gear 20.As shown in Figure 1, the wind-power electricity generation involved by the embodiment
4 yawing units 100 are provided in equipment 12.
Each yawing unit 100 is respectively equivalent to " the 2nd brake apparatus Br2 " of the embodiment.Here, the 2nd brake apparatus
Br2 refers to " by the rotation for turning round pinion gear 122 brake so as to brake nacelle 16 via swiveling gear 20
Brake apparatus ".Also, it in this embodiment, is also equipped with as the 2nd brake apparatus Br2 dedicated just like braking shown in Fig. 3
Brake unit 200.The revolution pinion gear 222 of the brake unit 200 is also engaged with swiveling gear 20.
In Fig. 1, the side where being equivalent to blade (with reference to the symbol 917 of figure 6) on the upside of paper.As shown in Figure 1,4
Yawing unit 100 is relatively narrow at the interval of 917 side of blade and wider with the interval of blade opposite side, and not in week
The first-class interval setting in direction.Brake unit 200 is configured at the center with 2 yawing units 100 of blade opposite side.But
The configuration of the yawing unit 100 and brake unit 200 is not necessarily limited to the configuration of the Fig. 1.For example, it is also possible to it is configured to partially
Boat unit 100 between circumferential direction on interval it is equal or be configured to including brake unit 200 all units 100,
200 interval in the circumferential direction is equal.Moreover, the number of units of yawing unit 100 and brake unit 200 is also not limited to Fig. 1's
Example.For example, yawing unit 100 may be less than 3 or 5 or more, brake unit 200 may be 2 or more.
The structure of the yawing unit 100 of Fig. 2 is illustrated.
Yawing unit 100 has motor 130, deceleration device 132, revolution pinion gear 122 and arrestment mechanism 134.Slow down dress
It puts 132 and has input side eccentric swing speed reducer 150 and outlet side eccentric swing speed reducer 152.Input side eccentric swing slows down
Machine 150 is the eccentric swing speed reducer for being referred to as centre-crank formula, is had：Input shaft 154 is integrally formed with motor drive shaft 151；
Eccentric body 156 is rotated integrally with the input shaft 154；External gear 158, it is swingable to be rotatably assembled in the outer of the eccentric body 156
Week；And internal gear 160, for 158 internal messing of external gear.The gear ratio external gear 158 of internal gear 160 is slightly more (in this example embodiment
It is only 1 more).
In deceleration device 132, if by the rotation of input shaft 154, external gear 158 is swung via eccentric body 156
Rotation, then the external gear 158 is relative to the slowly progress rotation of internal gear 160.Via through external gear 158 pin member 162, wheel
Frame 164 exports the rotation from output shaft 165.
Outlet side eccentric swing speed reducer 152 also centered on crank-type eccentric swing speed reducer, capacity be more than input
Side eccentric swing speed reducer 150, but basic deceleration mechanism is identical with input side eccentric swing speed reducer 150.Therefore, to tool
There is the position with 150 same or like function of input side eccentric swing speed reducer, mark is attached with the identical of suffix A in the accompanying drawings
Symbol, and omit repeated explanation.The revolution pinion gear 122 is fixed on outlet side eccentric swing by spline and bolt 170 and subtracts
The output shaft 165A of fast machine 152.
Shown with the configuration example for the brake unit 200 for equally constituting the 2nd brake apparatus Br2 in Fig. 3.
The brake unit 200 has deceleration device 232, revolution pinion gear 222 and arrestment mechanism 234.Do not have motor.
That is, brake unit 200 does not have the function of revolution driving nacelle 16.The deceleration device 232 of brake unit 200 has centre-crank
The input side eccentric swing speed reducer 250 of formula and the outlet side eccentric swing speed reducer 252 for being referred to as distribution formula.
Input side eccentric swing speed reducer 250 has identical with the input side eccentric swing speed reducer 150 of yawing unit 100
Deceleration mechanism, therefore in figure 3, to portion functionally similar with the input side eccentric swing speed reducer 150 of yawing unit 100
, the identical symbol of two digits after mark, and omit repeated explanation.
Outlet side eccentric swing speed reducer 252 has：Input shaft 272, the output with input side eccentric swing speed reducer 250
Axis 265 is integrally formed；Pinion gear 274 is inputted, is integrally formed at the input shaft 272；3 distribution gears (only illustrating 1) 276,
It is engaged simultaneously with the input pinion gear 274.Each distribution gear 276 and 3 278 connections of crank axle (only illustrating 1), described 3
Crank axle is configured at the position for the axle center C272 for deviateing input shaft 272.Eccentric body 280 is formed in each crank axle 278, outside
Gear 282 is swingable to be rotatably assembled in the eccentric body 280.External gear 282 and 284 internal messing of internal gear.The tooth of internal gear 284
Number is slightly more than the number of teeth of external gear 282 (only 1 more in this example embodiment).
In the outlet side eccentric swing speed reducer 252, if input shaft 272 is rotated, 3 crank axles 278 pass through
Input pinion gear 274 and distribution gear 276 are rotated with identical rotating speed towards same direction, so as to make to be set to each crank
280 synchronous rotary of eccentric body of axis 278.External gear 282 is relativeed to internal gear 284 while swinging and is slowly carried out as a result,
Therefore rotation, revolution of the rotation as crank axle 278 is exported via the wheel carrier 286 of load-side from output shaft 288.Output shaft
288 are integrally formed by spline 290 and bolt 292 with the revolution pinion gear 222.
The rated output torque of the motor 130 of yawing unit 100 is Rp130, and the brake force of arrestment mechanism 134 is Bp134,
The reduction ratio of deceleration device 132 is Sr132.Therefore, the brake force of the revolution pinion gear 122 of yawing unit 100 is arrestment mechanism
The product Bp100 (=Bp134 × Sr132) of the 134 brake force Bp134 and reduction ratio Sr132 of deceleration device 132.
The brake force of the arrestment mechanism 234 of brake unit 200 is Bp234, and the reduction ratio of deceleration device 232 is Sr232.Cause
This, the brake force of the revolution pinion gear 222 of brake unit 200 is the brake force Bp234 of arrestment mechanism 234 and deceleration device 232
Reduction ratio Sr232 product Bp200 (=Bp234 × Sr232).
Also, the brake force Bp234 of the arrestment mechanism 234 of brake unit 200 is more than the arrestment mechanism of yawing unit 100
134 brake force Bp134 (Bp134 ＜ Bp234).Also, the reduction ratio Sr232 of the deceleration device 232 of brake unit 200 is more than
The reduction ratio Sr132 (Sr132 ＜ Sr232) of the deceleration device 132 of yawing unit 100.Therefore, the revolution of brake unit 200 is small
The brake force Bp200 (=Bp234 × Sr232) of gear 222 is far longer than the braking of the revolution pinion gear 122 of yawing unit 100
Power Bp100 (=Bp134 × Sr132) (Bp100<<Bp200).
In addition, the revolution that the pitch diameter Pc222 of the revolution pinion gear 222 of brake unit 200 is more than yawing unit 100 is small
The pitch diameter Pc122 (Pc122 ＜ Pc222) of gear 122.On the other hand, due to the revolution pinion gear 222 of brake unit 200
It need to be engaged, therefore be set as identical modulus with same swiveling gear 20 with the revolution pinion gear 122 of yawing unit 100.But
In the embodiment, the revolution pinion gear 222 of brake unit 200 is set as being less than yaw list relative to the backlash of swiveling gear 20
Member 100 revolution pinion gear 122 relative to swiveling gear 20 backlash.In order to reduce backlash, specifically can will for example make
Transverse tooth thickness on the pitch circle of the revolution pinion gear 222 of moving cell 200 is set greater than the revolution pinion gear 122 of yawing unit 100
Transverse tooth thickness on pitch circle.Alternatively, can also backlash be set as smaller by the following method, this method is as follows：By brake unit
200 when being assemblied in nacelle 16, so that the axle center of the revolution pinion gear 222 of the brake unit 200 is closer to 20 side of swiveling gear
Mode is assembled.
In addition, reduction ratio at this time is the denominator value of speed ratio.From revolution pinion gear 122, from 222 sides, reduction ratio into
For speed increasing ratio.
According to the above, in this embodiment, more than using yawing unit 100 come to wind power plant 12
The revolution of nacelle 16 is braked, but carries out the braking by 12 entirety of wind power plant.That is, in present embodiment
In, pass through combination journal bearing 18 (the 1st brake apparatus Br1) and 4 yawing units 100 and brake unit 200 (multiple 2nd systems
Dynamic device Br2) realize the braking of the revolution to nacelle 16, the sliding bearing band 18 have not via swiveling gear 20 and into
The braking function of row braking, 4 yawing units and brake unit pass through the rotation system to turning round pinion gear 122,222
It moves and is braked via swiveling gear 20.
And A, the system by the 1st brake apparatus Br1 are set as using the maximum assumed value for the external force for being intended to turn round nacelle 16
When power is set as B, the aggregate value of the brake force of the 2nd brake apparatus Br2 of part is set as C, the structure of (A-B) ＜ C establishments.Separately
Outside, " brake force of the 2nd brake apparatus Br2 " here refers to turn round brake force Bp100, Bp200 of pinion gear 122,222.
Specifically, in this embodiment, the brake force B of the 1st brake apparatus Br1 refers to the slip resistance of sliding bearing 18
Power.In other words, brake force B is equivalent to makes nacelle 16 turn round required power by stationary state.Also, with regard to part the 2nd
For the aggregate value C of the brake force of brake apparatus Br2, in the present embodiment, due to the brake force Bp200 of brake unit 200
Just than (A-B) greatly, therefore the aggregate value refers to the brake force Bp200 of the brake unit 200.
Hereinafter, the technical meaning of the mathematical expression (A-B) ＜ C is described in detail.
Based on the 1~opinion of opinion 3 it is stated that present embodiment on nacelle based on " when being braked, even if apply
Added with the maximum external force that can assume that, the nacelle is made still to maintain stationary state " design concept.In order to realize the design concept,
The maximum assumed value A of determining external force must be removed with some form.However, although the maximum assumed value A of the external force is limited value,
But because it is the value that is generated by the wind-force under natural environment, therefore is not to be determined as specifically being worth from the beginning.
Therefore, in the present embodiment, the maximum assumed value A of the external force is defined as " each yawing unit 100 assembled
Motor 130 rated output torque Rp130 × deceleration device 132 reduction ratio Sr132 aggregate value ".
In addition, in the present embodiment, all yawing units 100 have an identical structure, thus the maximum assumed value A into
For (Rp130 × Sr134 × 4), and if it is mixed with motor with different rated output torques or the different deceleration of reduction ratio
During the yawing unit of device, maximum assumed value A is the aggregate value of each yawing unit.
That is, the motor 130 of offset units 100 is selected to make it have following ability：Even if in the case where blowing high wind
It is also resistant against wind-force and goes to return nacelle 16 through the time of tens seconds to turn around.It (not opens within about 1 second or so that is, have
Dynamic output torque) driving force with lasting rated output torque Rp130 resisting wind-force nacelle 16 is made to carry out revolution degree.
Based on this, if considering the opinion 1 of " during driving nacelle, each yawing unit substantially drives nacelle jointly ",
It can be said that " in the wind power plant 12, the maximum assumed value A of external force is interpreted as to the motor 130 of yawing unit 100
The aggregate value of the reduction ratio Sr132 of rated output torque Rp130 × deceleration device 132, therefore have selected with the rated output
The yawing unit 100 " of the motor 130 of torque Rp130 and the deceleration device 132 of reduction ratio Sr132.According to this definition, this implementation
The maximum assumed value A of external force in mode becomes the concept that can be uniquely determined.
Then, the technical meaning of mathematical expression (A-B) is subtracted from the maximum assumed value A of external force (not via swiveling gear
20) this technical meaning of the brake force B of the 1st brake apparatus Br1 directly braked to the revolution of nacelle 16 illustrates.
When nacelle 16 is static relative to pillar 14, due to centainly being deposited on the supporting device of nacelle 16 (sliding bearing 18)
At steering resistance (i.e. brake force B), therefore for the 2nd brake apparatus Br2 with regard to being braked via swiveling gear 20, as long as energy
Enough provide is subtracted with the brake force of (A-B) of the comparable brake force B of the steering resistance of the supporting device i.e. from maximum assumed value A
It can.This is the 1st meaning of mathematical expression (A-B).
In addition, in mathematical expression (A-B), also other technical meanings.If the 2nd braking in the state of brake force is applied with
Device Br2 is skidded off, then according to the opinion 3, the load that each 2nd brake apparatus Br2 is born can respectively increase severely.This may infer that
" to be shaking (deviation or two axis of the pillar axle center with nacelle axle center because of the supported mechanism of nacelle with very big quality
The inclination of the heart) influence become apparent ", explanation is there has been to this.
In order to cope with the situation, when being braked to the revolution of nacelle 16, the following two kinds knot is preferably energetically used simultaneously
Structure (makes brake force B more energetically increase)：The structure only braked via swiveling gear 20 and not via swiveling gear 20 and
The structure directly braked relative to pillar 14 to nacelle 16.Thereby, it is possible to be further reduced the nacelle 16 under high wind to be propped up
Holding the influence of mechanism shaking becomes the phenomenon that apparent.In addition, in the present embodiment, due to quiet relative to pillar 14 in nacelle 16
Always brake force B is generated when only, therefore the influence of shaking when braking static can be further reduced.This is mathematical expression (A-
B the 2nd meaning).
According to the viewpoint, the preferably brake force B of the 1st brake apparatus Br1, which is at least possessed by such as sliding bearing, to turn round
Value more than resistance can play the value of the degree size of " brake force " function rather than deliberately go to reduce as rolling bearing
The value of steering resistance.Certainly, as described later, the 1st brake apparatus Br1 can also have more energetically nacelle 16 is braked
Structure.
Then, to the aggregate value C in mathematical expression (A-B) ＜ C be " part " the 2nd brake apparatus brake force aggregate value and
This technical meaning of the aggregate value of the brake force of non-" all " the 2nd brake apparatus illustrates.
According to the opinion 2, if nacelle 16 enters braking, stationary state, the load equalization of each yawing unit 100 (with
Compared when being turned round nacelle 16) have the tendency that deviation becomes much larger.For example, during braking at a time is static, if
Just there are backlash between the revolution pinion gear 122 of specific yawing unit 100 and swiveling gear 20, even if then this is specific partially
The arrestment mechanism 134 of boat unit 100 can brake, but therefore can not be to rotary teeth the rotation for turning round pinion gear 122
The rotation of wheel 20 is braked.Now it is necessary to the system using the 2nd brake apparatus Br2 in addition to the specific yawing unit 100
Power brakes swiveling gear 20.In other words, when nacelle 16 is in braking, static state, nacelle can be applied to
The simple aggregate value of the 16 brake force not necessarily brake force of " all " yawing units 100.That is, even if calculating when institute
The aggregate value for having 100 brake force of yawing unit is more than (A-B), but the brake force that can actually generate is also possible to be less than (A-B).
But if it is, the possibility that then nacelle 16 moves will also correspondingly improve.
If also, for example, be applied with excessive external force in specific yawing unit 100, the yawing unit may be caused
100 is damaged.At this point, if the brake force that nacelle 16 can be made static cannot be shared by remaining yawing unit 100, can connect
Connect product gives birth to the breakage of linksystem, as a result may lead to not maintain the stationary state of nacelle 16.But in this regard, only
The brake force of the 2nd brake apparatus Br2 of part is wanted to be more than (A-B), then can further be reduced because of the 2nd all brake apparatus Br2
Nacelle 16 is caused to linksystem to proceed by the possibility of revolution by damaged.
Here it is as the aggregate value C in mathematical expression (A-B) ＜ C using the aggregate value of " part " the 2nd brake apparatus Br2
And the reasons why aggregate value of the brake force of not all 2nd brake apparatus Br2.
In view of this point, more specifically, " the 2nd brake apparatus Br2 of part " are preferably all 2nd brake apparatus Br2 total
Less than half several the 2nd brake apparatus Br2 (for example, the 2nd brake apparatus Br2 sum in the case of 5, less than 2
The 2nd brake apparatus Br2).Moreover, further preferably the brake force of 1 in multiple 2nd brake apparatus Br2 is set as being more than
(A-B).Also, further preferably the brake force of all 2nd brake apparatus Br2 is set as to be more than (A-B).
It is the brake force Bp200 of only 1 the 2nd brake apparatus Br2 using only 1 brake unit 200 in the present embodiment
It is greater than the structure of (A-B).Therefore, even at other yawing units 100 for example because there are rotary teeth can not be participated in during backlash
The braking of wheel 20 or the on-position for being slided and can not being provided original brake force, also can be 1 the 2nd merely with this
Brake apparatus Br2 (brake unit 200) is more than the brake force of (A-B) to provide.It is short therefore, it is possible to be prevented with very high probability
Cabin 16 skids off.
If hereinafter, exemplifying specific numerical value, in the present embodiment, the rated output torque of motor 130 is used
4 yawing units 100 that Rp130 is 2,145kgm, and the reduction ratio Sr132 of the deceleration device 132 of each yawing unit 100 is 1,
075 (reduction ratio 25 of reduction ratio 43 × outlet side eccentric swing speed reducer 152 of input side eccentric swing speed reducer 150).Cause
This, the maximum assumed value A of external force is 2,145 × 1,075 × 4=9,223kgm.
Also, the brake force B of the 1st brake apparatus Br1 (sliding bearing 18) is 5,000kgm.Therefore, (A-B)=9,223-
5,000=4,223kgm.Also, have to have and be just capable of providing more than 4 merely with 1 (the 2nd brake apparatus Br2 of part),
The brake unit 200 of the brake force Bp200 (Bp234 × Sr232=4,500kgm=C) of 223kgm.Therefore, present embodiment institute
The wind power plant being related to meets mathematical expression (A-B) ＜ C.
Then, the effect of the wind power plant involved by present embodiment is illustrated.
If the motor 130 of each yawing unit 100 is made to be rotated so as to drive revolution pinion gear 122, pinion gear is turned round
122 by the engagement reaction force from swiveling gear 20, so as to around the axle center C20 (axle center of pillar 14 of swiveling gear 20
C14 it) is revolved round the sun (with reference to figure 1).Entire yawing unit 100 revolves round the sun around the axle center C20 of swiveling gear 20 as a result, because
This nacelle 16 can be turned round relative to pillar 14.
In addition, brake unit 200 carries out drive rotation non-loadedly at this time.Since brake unit 200 does not have motor, because
This pitch diameter Pc222 (number of teeth) for setting reduction ratio Sr232 anyway and turning round pinion gear 222, will not be with others
Yawing unit 100 generates interference, therefore the degree of freedom designed is high.
When being braked to the revolution of nacelle 16, worked by the arrestment mechanism 134 for making each yawing unit 100 come to returning
The rotation for turning pinion gear 122 is braked, so as to be carried out via swiveling gear 20 to the revolution relative to pillar 14 of nacelle 16
Braking.Also, at the same time, by the way that the arrestment mechanism 234 of brake unit 200 is made to work come the revolution to the brake unit 200
The rotation of pinion gear 222 is braked, and the revolution relative to pillar 14 of nacelle 16 can also be carried out via swiveling gear 20
Braking.
Also, in the present embodiment, directly the revolution of nacelle 16 is carried out due to being equipped with not via swiveling gear 20
The 1st brake apparatus Br1 (being specially sliding bearing 18) of braking, therefore the 2nd system can be correspondingly reduced with the amount of brake force B
The brake force that dynamic device Br2 is undertaken (if the brake force of the 2nd brake apparatus Br2 is set as identical, can be ensured that corresponding to its
Abundant nacelle 16 brake force).
Further, it is possible to when descending the nacelle 16 to start revolution when further suppressing braking or in the braking state, nacelle 16 is opposite
It is corresponding to this in the shaking of pillar 14, excessive load can be reduced and be applied on yawing unit 100.
Also, A is set as using the maximum assumed value for being intended to the external force for being turned round nacelle 16 in the present embodiment, is incited somebody to action
When the brake force of 1st brake apparatus Br1 is set as B, the aggregate value of the brake force of the 2nd brake apparatus of part is set as C, (A-B) ＜ C
The structure of establishment, as long as therefore by wind generate external force in setting range, then nacelle 16 will be static, in the braking state under not
It can skid off.Therefore, it can prevent from becoming the situation of obtained stronger load disorder production in such as opinion 3 in advance, so as to
Enough breakages for further avoiding yawing unit 100.
In particular, in this embodiment, the 1st braking is formed by the sliding bearing 18 being configured between pillar 14 and nacelle 16
Device Br1.Therefore, it is possible to generate braking moment between pillar 14 and nacelle 16 always.That is, by motor 130 energetically
When being turned round nacelle 16, also the brake force of the 1st brake apparatus Br1 can be made to play a role.Therefore, it is possible to be imitated as follows
Fruit：Not only in braking, in usual power generation can also reduce the unnecessary of nacelle rocks.It is especially at low cost, and be not easy
It breaks down.It is held further, it is possible to correspondingly reduce the 2nd brake apparatus Br2 with the amount of the brake force B of the 1st brake apparatus Br1
The brake force of load.
Also, in present embodiment, by least 1 the 2nd brake apparatus Br2 (braking in multiple 2nd brake apparatus Br2
Unit 200) brake force be set as be more than other the 2nd brake apparatus (yawing unit 100).Therefore, even if (brake force is little for other
) the 2nd brake apparatus Br2 due to off-capacity (or because there are backlash when) can not bearing and turning gear 20, brake force setting
The possibility that the swiveling gear 20 can be supported for the 2nd larger brake apparatus Br2 is increased (if only by the system with same size
The brake apparatus of power forms the 2nd brake apparatus Br2, then when specific 2nd brake apparatus Br2 can not be propped up for some reason
When holding swiveling gear 20, can not just make up specific 2nd brake apparatus and bearing and turning gear 20, be finally unable to maintain that revolution
The possibility of the stationary state of gear 20 is higher).
Also, in this embodiment, from the perspective of swiveling gear 222, brake force Bp200 is set as larger
2 brake apparatus Br2 (brake unit 200) have speed increasing ratio Sr232 more than the booster engine of the speed increasing ratio Sr132 of yawing unit 100
Structure.Therefore, with the brake force Bp234 of the arrestment mechanism of brake unit 200 234 in itself than the arrestment mechanism 134 of yawing unit 100
The strong this point of brake force Bp134 be combined, can assign to swiveling gear 20 via revolution pinion gear 222 and (pass through multiplication)
The very strong brake force compared with the brake force Bp100 (=Bp134 × Sr132) of the revolution pinion gear 122 of yawing unit 100
Bp200 (=Bp234 × Sr232).
Also, in the present embodiment, the brake force of 1 (brake unit 200) in multiple 2nd brake apparatus Br2
Bp200 is set greater than above-mentioned (A-B).Therefore, as long as the maximum assumed value A of external force is not higher by hypothesis range, just with other the 2nd
Independently, brake unit 200 can individually prevent swiveling gear 20 from starting to turn round to the braking conditions of brake apparatus Br2.
Also, in the present embodiment, brake force Bp200 is set as the 2nd brake apparatus Br2 (braking bigger than above-mentioned (A-B)
Unit 200) revolution pinion gear 222 pitch diameter Pc222 more than other the 2nd brake apparatus Br2 (yawing unit 100) return
Turn the pitch diameter Pc122 of pinion gear 122.Therefore, even if brake force is larger, revolution pinion gear 222 also can further be reduced
Face pressure, the intensity (or durability) of the revolution pinion gear 222 can be further improved.
Moreover, in the present embodiment, the revolution pinion gear 222 of brake unit 200 relative to swiveling gear 20 backlash
The revolution pinion gear 122 for being set as being less than yawing unit 100 is relative to the backlash of swiveling gear 20.As a result, in braking, more can
Improving such as lower probability, i.e. the revolution pinion gear 222 of brake unit 200 can first join than the revolution pinion gear 122 of yawing unit 100
With the probability of the braking (first bearing load) of swiveling gear 20.Therefore, in the environment of nacelle 16 is intended to be turned round by external force,
The stationary state of the nacelle 16 can be stablized earlier.In addition, when the backlash of specific yawing unit 100 is prior to brake unit
200 are blocked and can not be only by the specific yawing unit 100 come when being braked to the revolution of swiveling gear, swiveling gear 20
Backlash in brake unit 200 is blocked and the phase until the brake force Bp200 of the brake unit 200 is applied to swiveling gear 20
Between slightly move.But as long as swiveling gear 20 discontinuously moves, brake force B would not become dynamic friction.Therefore, will not
The relationship of (A-B) ＜ C is destroyed, it can be by being blocked because of backlash and the brake force of brake unit 200 that can be played a role
Bp200 reliably makes swiveling gear 20 maintain stationary state.In addition, in 130 revolution driving of motor by yawing unit 100
During nacelle 16, brake unit 200 only carries out drive rotation with non-loaded state, therefore, even if by the brake unit 200
Backlash is set as smaller, also hardly generates baneful influence.
In addition, in this embodiment, the braking function of sliding bearing in itself is utilized as the 1st brake apparatus.However,
Structure about the 1st brake apparatus according to the present invention, it is important that as long as it can brake returning for nacelle relative to pillar
The structure turned, is not limited to the structure.For example, as described above, it can actively adjust cunning using retention mechanisms such as bolts
The device of the resistance (i.e. brake force) of dynamic bearing is more preferably effective as the 1st brake apparatus of the present invention.
Also, can certainly have dedicated brake apparatus as the 1st brake apparatus rather than by sliding bearing to be used as
1st brake apparatus.Such as lower structure can also be used：For example, it is revolved in being partially formed coaxial with the axle center of pillar of nacelle pedestal
The cylindrical portion (or plectane portion) turned, the cylinder is pressed on using the active force of spring etc. by the braking chip part for being set to pillar side
Portion, and pass through frictional force and the revolution of nacelle is braked.
In addition, since rotation and braking are opposite relationships, can also be set as such as lower structure：It sets and justifies in pillar side
Canister portion or plectane portion, and braking chip part is set in nacelle side.
By setting this dedicated 1st brake apparatus, the rolling of the supported mechanism of nacelle further can be reliably reduced
Dynamic influence.
Moreover, can also for example be used as the 1st brake apparatus, in order to obtain the pressing force of above-mentioned braking chip part and it is sharp
With the brake apparatus of hydraulic control.The brake apparatus of hydraulic control is utilized although cost is higher, make it is short
Damage when cabin is energetically turned round, the brake force of the 1st brake apparatus " can be closed ", therefore can reduce revolution driving
It loses.And, additionally it is possible to obtain the braking moment of the 1st brake apparatus being set higher than the braking of above-mentioned type of retardation always
The advantages of torque.
Also, 4 yawing units in the above-described embodiment, are employed plus 1 large capacity as the 2nd brake apparatus
The structure of dedicated brake unit is braked, but the present invention is not necessarily defined in the structure.
For example, it is also possible to the brake force using at least 1 the 2nd brake apparatus in multiple 2nd brake apparatus is more than other
The structure of the brake force of 2nd brake apparatus.That is, for example, it is also possible to the brake force of the 2nd brake apparatus of 2 or more is set as big
In other the 2nd brake apparatus.On the contrary, the 2nd brake apparatus that no brake force is set as larger can also be set as (that is, all
The brake force of 2nd brake apparatus is identical).If at this point, brake dedicated 2nd braking for example, also having other than yawing unit
The maximum assumed value of external force is then set as A, the brake force of the 1st brake apparatus is set as to B, by the 2nd brake apparatus of part by device
When the aggregate value of brake force is set as C, it will be able to set up mathematical expression (A-B) ＜ C, so as to obtain the effect of the present invention.And
And can not have and brake dedicated 2nd brake apparatus, that is, all 2nd brake apparatus can be the identical yaw list of structure
Member.For example, all yawing units can be respectively provided with the brake force C more than (A-B).
Also, in the above-described embodiment, from revolution pinion gear side, brake force Bp200 is set as the 2nd larger braking
Device has speed increasing ratio more than the speed increasing mechanism (deceleration device 232) of the speed increasing ratio of yawing unit, but brake force is set as larger
The 2nd brake apparatus be not necessarily to the speed increasing mechanism with speed increasing ratio bigger, for example, it is also possible to by there is only whether there is motor it
Other yawing unit and brake unit form the 2nd brake apparatus.
Certainly, for example, it is also possible to form the brake force of following the 2nd brake apparatus, the i.e. arrestment mechanism of the 2nd brake apparatus
All same, and from during the observation of revolution pinion gear side, there is speed increasing ratio more than the speed increasing mechanism of the speed increasing ratio of yawing unit, thus
Realize that the brake force of revolution pinion gear is different.
Also, in the above-described embodiment, in order to more reliably maintain the braking of nacelle, during with being braked to nacelle
The on-position of each 2nd brake apparatus independently, can be ensured that by the brake force of 1 in multiple 2nd brake apparatus and be more than
The brake force of above-mentioned (A-B), still, as long as the brake force of the 2nd brake apparatus of part, it will be able to it is correspondingly made available the present invention's
Function and effect.Accordingly it is also possible to the aggregate value of the brake force for the 2nd brake apparatus of 2 or more is more than the knot of above-mentioned (A-B)
Structure.
Also, in the above-described embodiment, brake force is set as the 2nd brake apparatus (brake unit bigger than above-mentioned (A-B)
200) the pitch diameter Pc222 of revolution pinion gear 222 is more than the small tooth of revolution of other the 2nd brake apparatus (yawing unit 100)
The pitch diameter Pc122 of wheel 122, especially turning round the teeth portion of pinion gear 222 ensures there is higher intensity.But the present invention is not
It has to be set as this structure, for example, even the pitch diameter of revolution pinion gear is all identical.
Also, in the above-described embodiment, as the 2nd brake apparatus, equipped with the system for the driving for being not involved in swiveling gear
Dedicated brake unit is moved, but can also the 2nd brake apparatus only be formed by yawing unit in the present invention.For example, such as Fig. 5 institutes
Show, the yawing unit 300 of yawing unit 100 and 1 large capacity for having 3 low capacities can also be used, as a result amount to and have 4
The structure of the 2nd brake apparatus Br2 of platform.Specifically, use yawing unit 100 shown in Fig. 2 and yaw list as shown in Figure 4
Member 300.Yawing unit 300 is the unit that motor 330 is attached to brake unit 200.Therefore, for brake unit
200 identical positions are labelled with the identical symbol of rear 2 bit digital, and omit repeated explanation.
In this configuration, the yawing unit 300 of large capacity can be made to have both the function of above-mentioned brake unit 200, so as to nothing
The sum of the 2nd brake apparatus Br2 need to be increased in narrow nacelle 16, in this regard preferably.But with braking dedicated system
Moving cell 200 is different, and yawing unit 300 needs driving swiveling gear 20 synchronous with the yawing unit 100 of low capacity, therefore, needs
The reduction ratio Sr332 of pitch diameter Pc322 and deceleration device 332 for turning round pinion gear 322 are set, so that in little Rong
The tangential velocity of the pitch diameter of the revolution pinion gear 122 of the yawing unit 100 of amount is returned with the yawing unit 300 in large capacity
The tangential velocity for turning the pitch diameter of pinion gear 322 is identical.
In addition, above-mentioned, " brake force of at least 1 the 2nd brake apparatus in multiple 2nd brake apparatus is more than other the 2nd systems
The structure of the brake force of dynamic device ", " brake force is set as increasing when the 2nd larger brake apparatus has from revolution pinion gear side
Speed than more than other the 2nd brake apparatus speed increasing mechanism " structure or " brake force be set as the 2nd larger brake apparatus time
Turn pinion gear pitch diameter be more than other the 2nd brake apparatus revolution pinion gear pitch diameter " structure, even and if external force
Maximum this concept of assumed value A to separate also be the structure with technical meaning.This is because in view of 2 He of above-mentioned opinion
Opinion 3, can be by these Structure Understandings can further avoid braking when swiveling gear revolution structure.
Also, the determining method of the maximum assumed value A of the external force in the above embodiment is only an example, is not discharged
Other determine method.For example, according to the data such as the wind speed measured by (such as 1 year) during certain, nacelle, pillar,
The data that damaged condition and deflection of yawing unit etc. actually measure, for example, by just in the wind power plant
The external force of the maximum external force of practical measurement is reasonable as " the maximum assumed value A of external force ".This method can further consider
To the distinctive geographic basis in place of the actual setting wind power plant, in this regard preferably.
Claims (5)
1. a kind of wind power plant, has：Pillar；Nacelle is turned round relative to the pillar；Swiveling gear is set to institute
State pillar；1st brake apparatus brakes the revolution of the nacelle not via the swiveling gear；And multiple 2nd braking dresses
It puts, there is the revolution pinion gear engaged with the swiveling gear, and by being braked to pass through to the rotation of the revolution pinion gear
The revolution of the nacelle to be braked by the swiveling gear, the wind power plant is characterized in that,
The multiple 2nd brake apparatus includes the yawing unit with braking function of nacelle described in revolution driving,
Be intended to make the maximum assumed value of the external force of the nacelle revolution be set as A, the brake force of the 1st brake apparatus is set as to B,
When the aggregate value of the brake force of part the 2nd brake apparatus is set as C, (A-B) ＜ C are set up,
1st brake apparatus is sliding bearing, and the sliding bearing is configured between the pillar and the nacelle, and is had
There is the adjustment mechanism of adjustment brake force.
2. wind power plant according to claim 1, which is characterized in that
The brake force of at least 1 the 2nd brake apparatus in the multiple 2nd brake apparatus is more than the system of other the 2nd brake apparatus
Power.
3. wind power plant according to claim 2, which is characterized in that
When from the revolution pinion gear side, there is the 2nd brake apparatus that the brake force is set as larger speed increasing ratio to be more than institute
State the speed increasing mechanism of the speed increasing ratio of yawing unit.
4. wind power plant described in any one of claim 1 to 3, which is characterized in that
The brake force of 1 in the multiple 2nd brake apparatus is set greater than (A-B).
5. wind power plant according to claim 4, which is characterized in that
The pitch diameter that the brake force is set as being more than the revolution pinion gear of the 2nd brake apparatus of (A-B) is more than it
The pitch diameter of his the 2nd brake apparatus.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-037389 | 2014-02-27 | ||
| JP2014037389A JP6489599B2 (en) | 2014-02-27 | 2014-02-27 | Wind power generation equipment |
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| Publication Number | Publication Date |
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| CN104879278A CN104879278A (en) | 2015-09-02 |
| CN104879278B true CN104879278B (en) | 2018-06-22 |
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| CN113202693B (en) * | 2021-05-18 | 2022-03-29 | 李慧 | Automatic speed-control wind driven generator |
| CN116336996B (en) * | 2023-05-15 | 2023-07-21 | 沈阳强航时代精密科技有限公司 | Method for detecting deflection of low-pressure turbine blade by using three-coordinate measuring machine |
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|---|---|---|---|---|
| JP2008309097A (en) * | 2007-06-15 | 2008-12-25 | Ebara Corp | Wind power generation equipment and method of controlling windmill for wind power generation |
| JP2011127551A (en) * | 2009-12-18 | 2011-06-30 | Mitsubishi Heavy Ind Ltd | Wind-powered generator apparatus |
| CN102395783A (en) * | 2010-05-31 | 2012-03-28 | 三菱重工业株式会社 | Wind power generation device, gear transmission mechanism, and gear-meshing control method |
| JP2012251522A (en) * | 2011-06-06 | 2012-12-20 | Sumitomo Heavy Ind Ltd | Power transmission device of wind power generation equipment |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004232500A (en) * | 2003-01-28 | 2004-08-19 | Komatsu Ltd | Nacelle turn drive device for wind power generation equipment, and its operating method |
| JP4638298B2 (en) * | 2005-08-18 | 2011-02-23 | 三菱重工業株式会社 | Wind power generator |
| JP2008095664A (en) * | 2006-10-16 | 2008-04-24 | Ebara Corp | Wind turbine device |
| WO2011096078A1 (en) * | 2010-02-08 | 2011-08-11 | 三菱重工業株式会社 | Wind driven generator and method of rotating nacelle |
| WO2013057836A1 (en) * | 2011-10-21 | 2013-04-25 | 三菱重工業株式会社 | Wind power generation device and wind power generation device yaw rotation control method |
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2014
- 2014-02-27 JP JP2014037389A patent/JP6489599B2/en active Active
- 2014-11-05 CN CN201410620692.XA patent/CN104879278B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008309097A (en) * | 2007-06-15 | 2008-12-25 | Ebara Corp | Wind power generation equipment and method of controlling windmill for wind power generation |
| JP2011127551A (en) * | 2009-12-18 | 2011-06-30 | Mitsubishi Heavy Ind Ltd | Wind-powered generator apparatus |
| CN102395783A (en) * | 2010-05-31 | 2012-03-28 | 三菱重工业株式会社 | Wind power generation device, gear transmission mechanism, and gear-meshing control method |
| JP2012251522A (en) * | 2011-06-06 | 2012-12-20 | Sumitomo Heavy Ind Ltd | Power transmission device of wind power generation equipment |
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| CN104879278A (en) | 2015-09-02 |
| JP2015161235A (en) | 2015-09-07 |
| JP6489599B2 (en) | 2019-03-27 |
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