CN102808745B - Speed reducer of wind power generation equipment - Google Patents
Speed reducer of wind power generation equipment Download PDFInfo
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- CN102808745B CN102808745B CN201210165451.1A CN201210165451A CN102808745B CN 102808745 B CN102808745 B CN 102808745B CN 201210165451 A CN201210165451 A CN 201210165451A CN 102808745 B CN102808745 B CN 102808745B
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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
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- 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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- 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
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
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Abstract
The invention provides a speed reducer (G1) of wind power generation equipment, and the speed reducer is used for wind power generation equipment. The final stage is composed of a swinging internal gearing planetary gear mechanism, and the planetary gear mechanism has a plurality of external gears (64A, 64B) and a single internal gear (68), the external gears (64A, 64B) swing and internally engage with the internal gear, and the internal gear (68) is composed of cylindrical tooth pins (68A) and an internal gear body (68B) with keyseats (68B1) having the inner gear pins (68A). The difference between outer teeth of the external gears (64A, 64B) and internal teeth of the internal gear (68) in the number of teeth is 2, and in addition, if the length of each internal gear pin (68A) is L1, and the diameter is d1, when the reduction ratio of the swinging internal gearing planetary gear mechanism is less than 20, L1/d1 is set to be greater than 5; when the reduction ratio is in the range of 21 to 30, L1/d1 is set to be greater than 8; and when the reduction ratio is greater than 31, L1/d1 is set to be greater than 10. In this way, an internal gear of the speed reducer of wind power generation equipment can be manufactured in a short time with low cost.
Description
Technical field
The present invention relates to a kind of speed reducer for wind power plant.
Background technique
In wind power plant, be assembled with the speed reducer that according to motor driving force, nacelle (power compartment) is controlled with respect to the driftage of wind rotation for carrying out in horizontal plane, or for carrying out changing with respect to wind the speed reducer etc. of pitch control of the direction (inclination) of air vane.
On the other hand, in patent documentation 1, disclose the speed reducer of engagement type planetary gears in the what is called swing that possesses engagement in swing limit, external gear limit and internal gear.In this speed reducer, internal gear forms by forming the cylindric interior alligator of internal tooth and having the internal gear main body that this interior alligator is remained to rotation cotter way freely.And, in order to ensure larger transmitting torque, is configured to and arranges in the axial direction 2 external gears of assembling, and each external gear meshes with single internal gear simultaneously.
If think, arrange in the axial direction assembling multi-disc external gear, cause the length of interior alligator of internal gear also elongated.In patent documentation 1, about the elongated undesirable condition that causes being difficult to process this interior alligator and so on of the length because of interior alligator, disclose the technology of having implemented to cut apart in the axial direction the methods such as this interior alligator.
Patent documentation 1: Japanese Patent Publication 2010-14238 communique (paragraph [0005], [0010], Fig. 1)
By possess swing in the speed reducer of engagement type planetary gears while being used as the speed reducer of wind power plant, in order to ensure larger torque capacity, must become and be assembled with the structure of multi-disc external gear as disclosed arrangement in patent documentation 1.And the facewidth of every external gear (thickness axially) also must not be constant large.Therefore, the length of interior alligator of internal tooth that forms internal gear is elongated, and for keeping the length of cotter way of this interior alligator also elongated.
In patent documentation 1, disclose for the elongated undesirable condition producing of the length because of interior alligator and implemented to cut apart in the axial direction the technology of the methods such as interior alligator.But if cut apart in the axial direction interior alligator, the assembly working amount of interior alligator is natural increases by 2 times, time-consuming bothersome on manufacturing, and causes expensiveization.
And, in patent documentation 1, for because keeping the elongated problem producing of length of the cotter way of interior alligator not mention especially.Yet the size of each speed reducer of wind power plant is very large.In so large speed reducer, machining shaft is during to the cotter way of longer internal gear, the existing problems that have that chipping allowance becomes large and process time is elongated and shorten tool life etc. in processing cost.
Summary of the invention
The present invention develops in view of this situation in the past, its problem be possess swing in the speed reducer of wind power plant of engagement type planetary gears, especially at short notice and with low cost fabrication internal gear.
The present invention solves above-mentioned problem by being made as following structure, a kind of speed reducer of wind power plant, wherein, final stage forms by swinging interior engagement type planetary gears, this planetary gears has the single internal gear that interior engagement is carried out on multi-disc external gear and this swing limit, multi-disc external gear limit, described internal gear forms by forming the cylindric interior alligator of internal tooth and having the internal gear main body that this interior alligator is remained to rotation cotter way freely, the number of teeth of the external tooth of described external gear and the internal tooth of described internal gear is poor is 2, and, the length of described interior alligator is made as to L, when diameter is made as d, the reduction speed ratio of L/d engagement type planetary gears in this swing is 20 to be set as more than 5 when following, when reduction speed ratio is 21～30, be more than 8, when reduction speed ratio, be 31 to be more than 10 when above.
The present invention draws by following design, and by interior alligator is attenuated, the internal diameter that (that is, when the length of interior alligator is made as to L, diameter and is made as d, by making L/d become large) also can make to support the cotter way of this thinner interior alligator diminishes.
But, in this swing in engagement type planetary gears, because the diameter of interior alligator is to have the important document of stronger dependency relation with reduction speed ratio, therefore cannot ignore with the relation of reduction speed ratio only by this interior alligator refinement simply.
Therefore, in the present invention, be made as " 2 " by the number of teeth of the internal tooth of the external tooth of external gear and internal gear is poor, on this basis, to make the relative refinement of interior alligator (that is, increasing L/d with respect to reduction speed ratio) with the when relation of size of slowing down, solved thus this problem.
According to this structure, even in the situation that realizing identical reduction speed ratio, also can use thinner (L/d is larger) interior alligator.Therefore, in the speed reducer of the variable large wind power plant of total length, especially can reduce the chipping allowance of the cotter way processing of its internal gear, its result can shorten process time and increase tool life, can be with low cost fabrication internal gear.
Invention effect
Can be at short notice and with the internal gear of the speed reducer of low cost fabrication wind power plant.
Accompanying drawing explanation
Fig. 1 means the sectional view of speed reducer of wind power plant of an example of embodiments of the present invention.
Fig. 2 is the sectional view along the II-II line of the speed reducer of Fig. 1.
Fig. 3 is the sectional view of the speed reducer of the related wind power plant of an example of other mode of executions of the present invention.
Fig. 4 is the sectional view along the IV-IV line of the speed reducer of Fig. 3.
Fig. 5 is the plan view of wind power plant of the speed reducer of application drawing 1.
Fig. 6 is the stereogram that is schematically illustrated in the state of the speed reducer that is assembled with Fig. 1 in the nacelle of above-mentioned wind power plant.
In figure: 10-wind power plant, 11-cylinder pillar, 12-nacelle (power compartment), 14-deviation drive device, 16-pitch drive unit, 22-motor, 24-output pinion, 64A, 64B-external gear, 68-internal gear, alligator in 68A-, 68B-internal gear main body, 68B1-cotter way, the length of alligator in L1-, the external diameter of alligator in d1-.
Embodiment
Below, with reference to accompanying drawing, the speed reducer (power transmitting deice) of the related wind power plant of an example of embodiments of the present invention is elaborated.
First, from applying the summary of deviation drive device of the wind power plant of this speed reducer, describe.
With reference to figure 5 and Fig. 6, this wind power plant 10 possesses nacelle (power compartment) 12 at the topmost part of cylinder pillar 11.Driftage (Yaw) drive unit 14 and pitch (Pitch) drive unit 16 have been described in Fig. 6.Deviation drive device 14 is for controlling nacelle 12 integral body with respect to the device of the angle of rotation of cylinder pillar 11, and pitch drive unit 16 is for controlling the device of the angle of pitch that is installed on 3 air vanes 20 on nose cone 18.
In this embodiment, because the present invention is applied to deviation drive device 14, so deviation drive device 14 is described at this.
This deviation drive device 14 possesses with 4 speed reducer G1～G4 of motor 22 and output pinion 24 and 1 internal gear 28 for revolution meshing with each output pinion 24 (revolution is also external gear with internal gear 28 sometimes).Revolution is fixed on cylinder pillar 11 sides with internal gear 28.Each speed reducer G1～G4 is individually fixed in the precalculated position of the structure 12A (with reference to figure 1) of nacelle 12.
According to this structure, if each output pinion 24 is rotated by the motor 22 of each speed reducer G1～G4 simultaneously, when this output pinion 24 meshes with internal gear 28 with revolution, revolution is revolved round the sun with internal gear 28 center 36 (with reference to figure 6) relatively.Its result, can make the structure 12A of nacelle 12 relatively move with internal gear 28 with respect to the revolution being fixed on cylinder pillar 11, and can make nacelle 12 integral body around internal gear 28 center 36 revolutions for this revolution.Thus, can make nose cone 18 for example, towards desirable direction (direction) windward, and can effectively bear blast.
Because described speed reducer G1～G4 has respectively identical structure, so speed reducer G1 is described at this.
Fig. 1 is the sectional view of the speed reducer of the related wind power plant of an example of embodiments of the present invention, and Fig. 2 is the sectional view along the II-II line of the speed reducer of Fig. 1.
Speed reducer G1 possesses successively in power transfer path motor 22 (in Fig. 1 omit diagram), worm gear box 40 and swing in engagement type planetary gears 44.
Motor 22 omits diagram in Fig. 1, through the construction bolt hole of mounting flange 46 46A, along the direction of the paper perpendicular to this Fig. 1, installs.Motor 22 uses 6 utmost point motors (also can use 4 utmost point motors) in this embodiment.The upper worm screw 48 that has worm gear box 40 via not shown coupling link of the motor drive shaft of motor 22 (omitting diagram).Worm screw 48 and worm gear 50 engagements, carry out 90 degree changes to the direction of transfer of power.
In this mode of execution, the reduction speed ratio of worm gear box 40 is " 40 " (it is 1/40 that the rotation of input is slowed down).This is because attempt to make worm gear box 40 to have the desirable auto-lock function of aftermentioned (function that can not rotate because of the load from outlet side).The auto-lock function of worm gear box 40 is determined with the friction factor of the contacting part of worm gear 50 by angle of lead and the worm screw 48 of worm screw 48, but when cylindrical worm for shown in present embodiment, if reduction speed ratio is more than 30, more preferably more than 40, can guarantee that the driftage of wind power plant controls required reverse and prevent function (function that nacelle 12 can not shake because of wind rocking) by the auto-lock function of worm gear box 40.In this mode of execution, due to by utilizing the auto-lock function of worm gear box 40 that the reaction force with respect to the external force from output pinion 24 sides is provided, so on motor 22 without arrestment mechanism is set, can seek to reduce the cost of its respective amount.
In swinging, the input shaft 56 of engagement type planetary gears 44 is by the 1st bearing the 59, the 2nd bearing 60 supportings.On input shaft 56 through key 58 be assembled with can one eccentric body 60A, the 60B of rotation.Eccentric body 60A, 60B are respectively with respect to the axle center O1 of input shaft 56 eccentric Δ e round about each other.In the periphery of each eccentric body 60A, 60B, through roller 62A, 62B, be assembled with external gear 64A, the 64B that can slide and rotate.
In the lump with reference to figure 2, external gear 64A, 64B respectively with the interior engagement of internal gear 68.In this mode of execution, the internal tooth of internal gear 68 is by interior alligator 68A and have the internal gear main body 68B that this interior alligator 68A is remained to rotation cotter way 68B1 freely and form.Internal gear main body 68B and shell 66 become one.On external gear 64A, 64B, be formed with respectively inner pinhole 70A, 70B.Being enclosed within domestic 74 in interior roller 72 leaves and is embedded in gap this inner pinhole 70A, 70B.Domestic 74 fixing (being pressed into) are in the wheel support body 76A becoming one with output shaft 76.Output shaft 76, by live-rollers (the 3rd bearing) the 78 and the 4th bearing 80 supportings, links through spline 83 and above-mentioned output pinion 24.
In this mode of execution, be not only arranged with in the axial direction 2 external gear 64A, 64B, and between external gear 64A and external gear 64B, be provided with for carrying out the support plate 82 of the axially locating of this external gear 64A, 64B.And the cotter way 68B1 of internal gear 68 more extends to axial outside than the engaging position with external gear 64A, 64B, in the part of this extension to be assembled with the described live-rollers (the 3rd bearing) 78 of support roller support body 76A with the coaxial mode of interior alligator 68A.Live-rollers 78 is same diameter with interior alligator 68A.
Therefore, the axial length L d1 of the cotter way 68B1 of internal gear 68 is except having the length L 1 of interior alligator 68A, also comprises the length with support plate 82 and live-rollers 78 respective amount, and it is extremely long that Ld1 becomes.In addition, though between external gear 64A and external gear 64B, sometimes also sandwich function and above-mentioned support plate 82 slightly different for example as described in disclosed sheet material (symbol 39 of Fig. 4 of patent documentation 1) in Fig. 4 of patent documentation 1, even if but while such sheet material being set between external gear 64A and external gear 64B, also still cause the length of interior alligator 68A elongated.
Therefore, in this mode of execution, adopt following structure, seek the processing of internal gear 68 and easily change.
As clearly known from Fig. 2, in this mode of execution, the outer number of teeth of external gear 64A, 64B is " 56 ", and the internal tooth of internal gear 68 (number of interior alligator 68A) is " 58 ".That is, the number of teeth of the internal tooth of the external tooth of external gear 64A, 64B and internal gear 68 is poor is 58 to deduct 56 " 2 ".In addition, about for the formation method etc. that the number of teeth is poor is made as the profile of tooth of " 2 " is had for No. 1208548 open in detail at Japan Patent.
Poor in the number of teeth is in the swing of " 2 " in engagement type planetary gears 44, in the usage mode of rotation of taking out external gear 64A, 64B according to above mode of execution, can access the reduction speed ratio of the outer number of teeth of external gear " number of teeth is poor/".Therefore, conventionally in this swing in engagement type planetary gears 44, in order to obtain high reduction speed ratio by 1 grade, the number of teeth is poor is set as " 1 ".Often in order to improve reduction speed ratio, increase the number of teeth (number of teeth of internal gear 68) of external gear 64A, 64B.When reduction speed ratio is lower, the external diameter of internal gear 68 has the tendency that becomes large conversely speaking.But, by being set as 2 by the number of teeth is poor, can utilize the interior alligator 68A of the thickness that is equivalent to reduction speed ratio 56 to realize reduction speed ratio 28 (2/56=28).In present embodiment, utilize this qualitative tendency, by the length L of interior alligator 68A 1 be made as 80mm, outside diameter d 1 is set as 8mm, can realize L1/d1 and be the design of 10.0 " thinner interior alligator ".And the cotter way 68B1 that this thinner interior alligator 68A is remained to rotation internal gear main body 68B freely also can be set as internal diameter and compare and carefully reach D1 with length L d1.
By the way, preferably, when being that in the situation of the driftage of the wind power plant speed reducer G1 that drives use, when being 4 utmost point motor, total reduction ratio is set as 1500～3000, is set as 1000～2000 when being 6 utmost point motor.In this mode of execution, use 6 utmost point motors, the reduction speed ratio of worm gear box is " 40 ", so the total reduction ratio of speed reducer integral body becomes 40 * 28,1120.
In addition, in this mode of execution, in swinging, the reduction speed ratio of engagement type planetary gears 44 is 28, when the length of interior alligator 68A is made as to L1, external diameter and is made as d1, L1/d1 is set as to 10.0.But the preferred value of this L/d is as the aforementioned impact that is subject to reduction speed ratio.Therefore, particularly, take and be made as " 2 " as prerequisite by the number of teeth is poor, when the length of interior alligator is made as to L, external diameter and is made as d, the reduction speed ratio of L/d engagement type planetary gears in this swing is 20 to be made as more than 5 when following, in reduction speed ratio, being to be made as more than 8 for 21～30 o'clock, is 31 to be made as more than 10 when above in reduction speed ratio.By being made as this value, as a result of the internal diameter of the cotter way of internal gear main body can being made as to the internal diameter of the length that is less than this cotter way, and can being made as the less cotter way of chipping allowance (bite).
In addition, aim from " using thinner interior alligator 68A " and so in the present invention is considered, the upper limit of L/d is also not particularly limited, but more preferably in this swing, the reduction speed ratio of engagement type planetary gears 44 is to be set as 6～12 at 10～20 o'clock, in this reduction speed ratio, being to be set as 8～15 at 21～30 o'clock, is within 31～40 o'clock, to be set as in 10～18 scope in this reduction speed ratio.These upper limits according to the intensity of interior alligator 68A guarantee or be difficult for degree of deformation etc. draw.
Then, the effect of this speed reducer G1 is described.
The worm screw 48 of the rotation of the motor drive shaft of motor 22 by worm gear box 40 with the engagement of worm gear 50 by elementary deceleration, through spline 54 be passed to swing in the input shaft 56 of engagement type planetary gears 44.
If input shaft 56 rotation 1 circles, swing external gear 64A, 64B 1 time via eccentric body 60A, 60B and roller 62A, 62B.In this mode of execution, because internal gear main body 68B and shell 66 become one in stationary state, so this external gear 64A, 64B due to swinging for 1 time of carrying out of external gear 64A, 64B with respect to 2 teeth (with the poor corresponding amount of the number of teeth) of 68 rotations relatively of internal gear (to the opposite direction rotation of input shaft 56 rotations).
The rotation of wheel support body 76A is passed to this takes turns the output shaft 76 that support body 76A becomes one.Aforementioned output pinion 24 is fixed and is linked on this output shaft 76 through spline 83, so this output pinion 24 and internal gear 28 Fig. 6 for the revolution having illustrated) engagement, whole nacelle 12 rotates by this engagement.
In the speed reducer of wind power plant in the past, due to poor being set as of the number of teeth " 1 " of external gear and internal gear, therefore when realize same reduction speed ratio, the external diameter of interior alligator also must not constant (chap) greatly.Particularly, for example, when reduction speed ratio is 28, the L/d of interior alligator is in the past 4～5 left and right, and outside diameter d is thicker with respect to length L.Therefore, result, the internal diameter overstriking of also having to make keep the cotter way of this thicker interior alligator, and need larger chipping allowance, also produce a large amount of smear metals.Certainly, also tool life have been shortened.
But, according to present embodiment, compare with the poor cotter way for " 1 " of the number of teeth, because the inside diameter D 1 of the cotter way 68B1 of every is less, therefore (even if the formation number of cotter way 68B1 at double) also can reduce total chipping allowance (bite), and can shorten process time, can seek the long lifetime of instrument.And, if poor with the number of teeth, be that 1 interior alligator is compared, the profile d1 of interior alligator 68A diminishes, but number becomes 2 times, therefore can prevent that intensity from declining, in addition, because the interval of the circumferencial direction of every interior alligator 68A is less, the advantage such as pulse in the time of therefore can also obtaining external gear 64A, 64B with internal gear 68 engagement less.
Fig. 3, Fig. 4 illustrate the example of other mode of executions of the present invention.
In Fig. 3, Fig. 4, other speed reducer G1b using in the deviation drive device 14 (with reference to figure 6) of wind power plant is shown.This speed reducer G1b possesses the interior engagement type planetary gears 102 of swing that what is called is called distribution type.
The worm screw 48 of the rotation of motor 103 (omit diagram) by worm gear box 40 with the engagement of worm gear 50 by elementary deceleration.Identical with mode of execution before so far.The output shaft 104 of worm gear box 40 becomes one with the input shaft 107 that swings the servo deceleration mechanism 105 of interior engagement type planetary gears 102.
The front end of input shaft 107 is provided with small gear 106.Small gear 106 and 3 gear 111～113 engagements (forming servo deceleration mechanism 105).
3 gears 111～113 are individually fixed in 3 eccentric shafts 121～123.On eccentric shaft 121～123, be disposed with vertically eccentric body 151A～153A and eccentric body 151B～153B.Eccentric body 151A～153A and eccentric body 151B～153B are eccentric with cophasing with respect to eccentric shaft 121～123 respectively, and chimeric with external gear 144A, 144B respectively via bearing 146A～148A, 146B～148B.That is, eccentric shaft 121～123 runs through external gear 144A, 144B in the position of the axle center O2 skew from input shaft 107.
In this mode of execution, external gear 144A, 144B by each eccentric body 151A～153A, 151B～153B respectively simultaneously with same phase and the rotation of same rotating speed and mutually swing with 180 degree phase differences, and respectively with the interior engagement of internal gear 160.Slightly different with mode of execution before for the mechanism that external gear 144A, 144B are swung, but the effect about this external gear 144A, swing limit, 144B limit and internal gear 160 interior engagements, can obtain the effect identical with mode of execution before, can realize (number of teeth of external gear 144A, 144B and internal gear 160 is poor)/reduction speed ratio that (number of teeth of external gear) is " 2/56=28 ".
Present embodiment is applied to the present invention the driftage driving speed reducer G1b of wind power plant, but when the present invention being applied to driftage and driving with speed reducer G1b by being called the combination of engagement type planetary gears in the swing of distribution type with what is called, can access greatest limit and bring into play the effect of advantage of the present invention.
That is,, when driving with speed reducer G1b for driftage, when during 4 utmost point motor, required total reduction ratio is 1500～3000,6 utmost point motor, required total reduction ratio is 1000～2000 left and right.As aforementioned, for cost degradation, if wish applies to the auto-lock function of worm gear box 40 to provide the reaction force of antagonism air vane 20 sides, the reduction speed ratio in this worm gear box 40 needs more than 30, preferably to need the reduction speed ratio of 40 left and right.In present embodiment, owing to adopting 6 utmost point motors, therefore the reducing gear below 2 grades needs the reduction speed ratio of 25 left and right.If wanting poor by the number of teeth is the reduction speed ratio that the combination of 1 external gear and internal gear realizes this value, in the external diameter of alligator become large, the processing of cotter way is all a problem at aspect the time and the life-span aspect of instrument.Especially, as this mode of execution, the live-rollers (with the live-rollers of interior alligator 160A same diameter) 174 of bearing of wheel support body 172B that forms load opposition side is when interior alligator 160A arranged coaxial is in cotter way 160B1, all the more so.
Yet, in present embodiment, due to by poor being set as of gear " 2 " of external gear 144A, 144B and internal gear 160, therefore by the number of interior alligator 160A is made as to 56, in reduction speed ratio, be domestic 160A can be made as to the thinner outside diameter d 2 corresponding with reduction speed ratio 56 at 28 o'clock, and form the thinner cotter way 168B1 that internal diameter is D2.Therefore, can overcome difficulty of processing.In addition, about this mode of execution, also can grasp in the same manner the length L 2 of interior alligator 160A and its outside diameter d 2 with mode of execution before with the upper limit of the corresponding L2/d2 of reduction speed ratio or suitable scope.By the way, the L2/d2 adopting is in this embodiment 9.0 left and right.
And, in this mode of execution, nonetheless " low reduction speed ratio ", but the prime that also can be made as engagement type planetary gears 102 in swinging possesses engagement type planetary gears in the swing of servo deceleration mechanism 105, therefore the rotation of engagement type planetary gears 102 in swinging can be further reduced to be input to, and rounding and the high efficiency of the rotation that swings interior engagement type planetary gears 102 can be further improved.
The application advocates the preference of No. 2011-124124th, Japanese patent application based on June 2nd, 2011 application.The full content of its application is by reference to being applied in this specification.
Claims (13)
1. a speed reducer for wind power plant, it is used in wind power plant, it is characterized in that,
Final stage forms by swinging interior engagement type planetary gears, and engagement type planetary gears has the single internal gear that interior engagement is carried out on multi-disc external gear and this swing limit, multi-disc external gear limit in this swing,
Described internal gear forms by forming the cylindric interior alligator of internal tooth and having the internal gear main body that this interior alligator is remained to rotation cotter way freely,
The number of teeth of the external tooth of described external gear and the internal tooth of described internal gear is poor is 2, and,
When the length of described interior alligator is made as to L, diameter and is made as d, in this swing, the reduction speed ratio of engagement type planetary gears is that 20 L/d when following are set as more than 5, described in when reduction speed ratio is 21～30, L/d is set as more than 8, when reduction speed ratio be 31 when above described in L/d be set as more than 10.
2. the speed reducer of wind power plant as claimed in claim 1, is characterized in that,
Described in when in this swing, the reduction speed ratio of engagement type planetary gears is 10～20, L/d is set as 6～12, when this reduction speed ratio is 21～30 described in L/d be set as 8～15, when this reduction speed ratio is 31～40 described in L/d be set as 10～18.
3. the speed reducer of wind power plant as claimed in claim 1, is characterized in that,
In than described swing, the more forward level of engagement type planetary gears disposes worm gear box, and the reduction speed ratio of this worm gear box is set as more than 30.
4. the speed reducer of wind power plant as claimed in claim 2, is characterized in that,
In than described swing, the more forward level of engagement type planetary gears disposes worm gear box, and the reduction speed ratio of this worm gear box is set as more than 30.
5. the speed reducer of wind power plant as claimed in claim 3, is characterized in that,
The total reduction ratio that possesses the described speed reducer of engagement type planetary gears in described worm gear box and described swing is set as 1500～3000 when 4 utmost point motor, when 6 utmost point motor, is set as 1000～2000.
6. the speed reducer of wind power plant as claimed in claim 4, is characterized in that,
The total reduction ratio that possesses the described speed reducer of engagement type planetary gears in described worm gear box and described swing is set as 1500～3000 when 4 utmost point motor, when 6 utmost point motor, is set as 1000～2000.
7. the speed reducer of the wind power plant as described in any one in claim 1～6, is characterized in that,
Axial position that the described cotter way of described internal gear meshes with described external gear is compared further and to axial outside, extended, in the part of this extension, be assembled with the live-rollers playing a role as the bearing of the wheel support body of described planetary gears.
8. the speed reducer of the wind power plant as described in any one in claim 1～6, is characterized in that,
Between described external gear and described external gear, be assembled with the support plate of the axially locating of carrying out this external gear.
9. the speed reducer of wind power plant as claimed in claim 7, is characterized in that,
Between described external gear and described external gear, be assembled with the support plate of the axially locating of carrying out this external gear.
10. the speed reducer of the wind power plant as described in any one in claim 1～6, is characterized in that,
The prime of engagement type planetary gears has by being arranged at the small gear of input shaft and the servo deceleration mechanism forming with a plurality of gears that this small gear meshes simultaneously in described swing, and,
Engagement type planetary gears is to possess a plurality of eccentric shafts and the plurality of eccentric shaft in the position of the desaxe of the described input shaft from described servo deceleration mechanism, to run through respectively the planetary gears of described external gear in this swing, is fixed with respectively described a plurality of gear and possesses for swinging the eccentric body of described external gear on described a plurality of eccentric shafts.
The speed reducer of 11. wind power plants as claimed in claim 7, is characterized in that,
The prime of engagement type planetary gears has by being arranged at the small gear of input shaft and the servo deceleration mechanism forming with a plurality of gears that this small gear meshes simultaneously in described swing, and,
Engagement type planetary gears is to possess a plurality of eccentric shafts and the plurality of eccentric shaft in the position of the desaxe of the described input shaft from described servo deceleration mechanism, to run through respectively the planetary gears of described external gear in this swing, is fixed with respectively described a plurality of gear and possesses for swinging the eccentric body of described external gear on described a plurality of eccentric shafts.
The speed reducer of 12. wind power plants as claimed in claim 8, is characterized in that,
The prime of engagement type planetary gears has by being arranged at the small gear of input shaft and the servo deceleration mechanism forming with a plurality of gears that this small gear meshes simultaneously in described swing, and,
Engagement type planetary gears is to possess a plurality of eccentric shafts and the plurality of eccentric shaft in the position of the desaxe of the described input shaft from described servo deceleration mechanism, to run through respectively the planetary gears of described external gear in this swing, is fixed with respectively described a plurality of gear and possesses for swinging the eccentric body of described external gear on described a plurality of eccentric shafts.
The speed reducer of 13. wind power plants as claimed in claim 9, is characterized in that,
The prime of engagement type planetary gears has by being arranged at the small gear of input shaft and the servo deceleration mechanism forming with a plurality of gears that this small gear meshes simultaneously in described swing, and,
Engagement type planetary gears is to possess a plurality of eccentric shafts and the plurality of eccentric shaft in the position of the desaxe of the described input shaft from described servo deceleration mechanism, to run through respectively the planetary gears of described external gear in this swing, is fixed with respectively described a plurality of gear and possesses for swinging the eccentric body of described external gear on described a plurality of eccentric shafts.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-124124 | 2011-06-02 | ||
| JP2011124124A JP2012251595A (en) | 2011-06-02 | 2011-06-02 | Reduction gear device of wind power generating facility |
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| CN102808745A CN102808745A (en) | 2012-12-05 |
| CN102808745B true CN102808745B (en) | 2014-05-07 |
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| CN201210165451.1A Expired - Fee Related CN102808745B (en) | 2011-06-02 | 2012-05-25 | Speed reducer of wind power generation equipment |
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| CN (1) | CN102808745B (en) |
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| CN107314085A (en) * | 2017-08-21 | 2017-11-03 | 戴高楠 | A kind of few teeth difference slowing-down structure |
| CN108580264B (en) * | 2018-05-17 | 2019-12-31 | 淄博康贝医疗器械有限公司 | Eccentric vibration type industrial material processing equipment with linkage disturbance function |
| JP7240217B2 (en) * | 2019-03-19 | 2023-03-15 | マブチモーター株式会社 | Cycloid reducer, its manufacturing method, and motor unit |
| CN112780728B (en) * | 2021-01-07 | 2022-05-17 | 重庆大学 | Cylindrical ring groove type double cycloid small tooth difference planetary reducer |
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| CN102808745A (en) | 2012-12-05 |
| JP2012251595A (en) | 2012-12-20 |
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