CN103370537A - Speed increasing gear for wind turbine - Google Patents
Speed increasing gear for wind turbine Download PDFInfo
- Publication number
- CN103370537A CN103370537A CN2011800651219A CN201180065121A CN103370537A CN 103370537 A CN103370537 A CN 103370537A CN 2011800651219 A CN2011800651219 A CN 2011800651219A CN 201180065121 A CN201180065121 A CN 201180065121A CN 103370537 A CN103370537 A CN 103370537A
- Authority
- CN
- China
- Prior art keywords
- sun gear
- planetary gears
- speed increaser
- output shaft
- wind power
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000012545 processing Methods 0.000 claims description 26
- 238000010248 power generation Methods 0.000 claims description 18
- 238000000034 method Methods 0.000 claims description 10
- 230000015572 biosynthetic process Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 230000004323 axial length Effects 0.000 description 3
- 239000000969 carrier Substances 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000012467 final product Substances 0.000 description 2
- 230000002452 interceptive effect Effects 0.000 description 2
- 238000003672 processing method Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 238000011835 investigation Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 210000001226 toe joint Anatomy 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
- F16H1/2845—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the sun gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
- F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/40—Transmission of power
- F05B2260/403—Transmission of power through the shape of the drive components
- F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
- F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/0886—Profiling with corrections along the width, e.g. flank width crowning for better load distribution
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Wind Motors (AREA)
- Retarders (AREA)
Abstract
The purpose of the present invention is to obtain a speed increasing gear for a wind turbine, the speed increasing gear having high reliability and extended life even through being compact, lightweight, and low cost. A speed increasing gear (50) for a wind turbine is provided with a planetary gear mechanism (52) which has a sun gear (72) and a first parallel shaft gear mechanism (54) which is provided at the rear stage of the planetary gear mechanism (52), and the speed increasing gear (50) is configured in such a manner that the sun gear (72) of the planetary gear mechanism (52) is formed integrally with the output shaft (80) of the planetary gear mechanism (52), at least a portion of the output shaft (80) of the planetary gear mechanism (52) in the axial direction is formed as a second small-diameter section (80C); having a smaller diameter than the portions on both sides of the at least a portion of the output shaft (80), and the tooth flanks of the sun gear (72) are crowned so as to be asymmetric with respect to the center of the sun gear (72) in the axial direction.
Description
Technical field
The present invention relates to a kind of used for wind power generation speed increaser.
Background technique
For example in patent documentation 1, disclose such as Fig. 6～used for wind power generation speed increaser shown in Figure 8.
Among Fig. 6 and Fig. 7, wind generating unit 1 has to be erect pillar 2, the nacelle 3 that arranges in the upper end of pillar 2 that is arranged on the ground 6 and is assembled into the rotor head 4 that rotates freely with respect to this nacelle 3.Multi-disc (in the illustrated example being 3) air vane (awe) 5 is installed on the rotor head 4.In the inside of nacelle 3, be connected with speed increaser 20 and generator 11 on the rotor head 4.
When wind was arranged to air vane 5, rotor head 4 can rotate, and the rotation of this rotor head 4 is to be arrived generator 11 by the state transfer of speed increaser 20 speedups.Thus, though rotor head 4(can be had running torque) at a slow speed rotary lifting be speed about 100 times, and can effectively obtain generating output from generator 11.
As shown in Figure 8, described speed increaser 20 possesses planetary gears 22 elementary, and possesses parallel-axes gears mechanism 24,26 at middle rank and rear class.Elementary planetary gears 22 mainly comprises: with input shaft 28 integrated wheel carriers 32, the planet pin 34 that is fixed in this wheel carrier 32, the planetary pinion 36 that is rotatably freely supported on this planet pin 34, and and this planetary pinion 36 internal gear 38 and the sun gear 40 that mesh simultaneously.The planetary gears 22 that this past case is related, the rotation from sun gear 40 outputs from wheel carrier 32 inputs.This sun gear 40 is integrated with the output shaft 42 of planetary gears 22.Output shaft 42 links via the input shaft 45 of coupling 43 with the parallel-axes gears mechanism 24 of next stage.
Rotation after planetary gears 22 by speed increaser 20 and parallel-axes gears mechanism 24, each gear mechanism speedup of 26 is imported into described generator 11.
In addition, symbol 12 shown in Figure 7 is transformer, and 13 is controller, and 14 is inverter, and 15 is the inverter cooling unit, and 16 is lubricant oil cooling apparatus.
The conventional art document
Patent documentation
Patent documentation 1: TOHKEMY 2009-144533 communique (Fig. 6～Fig. 8)
It is about 20 years that wind power plant is designed to its life expectancy.Therefore speed increaser is also required to guarantee at least life-span about 20 years.
Yet, because wind power plant is arranged under the physical environment, be subject to sometimes the attack of blast or strong wind.If there is this high wind to be applied to air vane, then cause speed increaser to be the state that is subject to huge load from input side.Therefore, (even by standard design) also can cause interior each parts of speed increaser to become the reason of initiating failure with the situation generation of too fast rotating speed pressure rotation sometimes.
In a single day speed increaser breaks down, and then its loss is serious, therefore will pay attention to guaranteeing of reliability.Usually, as the effective countermeasure of guaranteeing the speed increaser reliability, establish the safety coefficient (safety factor) of each important document larger during design.But, if the safety coefficient of each important document is established greatlyr, then naturally and understandably make the whole maximization of speed increaser and weight become large, and produce the problem that causes manufacture cost and construction cost to strengthen.
Summary of the invention
The present invention finishes in order to address this is that, the used for wind power generation speed increaser that its basic assignment provides small-sized, lightweight for newfound by overcoming " middle problem (aftermentioned) ", cost is low and reliability is high, the life-span is long.
The present invention solves above-mentioned problem by being made as following structure, it is a kind of used for wind power generation speed increaser, possesses the planetary gears with sun gear, reach the parallel-axes gears mechanism in the rear class setting of this planetary gears, the described sun gear of described planetary gears is formed on the output shaft of this planetary gears, axial at least 1 position of the described output of this planetary gears becomes diameter less than the minor diameter of its both sides, and, asymmetricly the flank of tooth of described sun gear is carried out convex surface processing with respect to the trace direction central authorities of this sun gear.
Because described middle problem of the present invention and solution principle thereof are also unexposed, thereby at this this centre problem and solution principle thereof that the present invention has in mind are elaborated.
When the air vane of wind power plant runs into wind, produce running torque with these each parts at speed increaser.When transmitting this running torque, the planetary gears in the speed increaser or parallel-axes gears mechanism certainly lead to vibration.Yet planetary gears is not identical with pivoting mechanism and the rotating speed of parallel-axes gears mechanism, and the vibration characteristics (frequency content etc.) that therefore produces is also different.Therefore sometimes because of the intensity of the wind of input and the method for pulsation, and cause these vibrations interfering with each other and produce resonance.Its result especially in bearing portion, slides for the roller (or ball) of the contact of rolling causes with inner ring, outer ring etc. originally, easily produces thus to collapse the sign that cutter etc. reduces durability.
The present invention will suppress the generation conduct " middle problem " of the resonance of planetary gears and parallel-axes gears mechanism to greatest extent, and, find out for the structure that solves this centre problem through further investigation for avoiding causing new unfavorable condition.
In the used for wind power generation speed increaser involved in the present invention, the sun gear of planetary gears and the output shaft of this planetary gears are integrally formed.Wherein so-called " integrally formed " do not refer to, links 2 parts (sun gear parts and output shaft assembly) afterwards by integrated via key or spline etc., and refers to that sun gear and output shaft are at the very start as 1 parts and integrated.
And in the present invention, axial at least 1 position of the output of this planetary gears becomes diameter less than the minor diameter of its both sides.By this structure, the part of the output shaft of this planetary gears is weakened intentionally because of the existence of this minor diameter, can absorb/cut off the propagation of planetary gears and the vibration separately of parallel-axes gears mechanism at this.
And, in the present invention, also adopted simultaneously the structure of asymmetricly flank of tooth of sun gear being carried out convex surface processing with respect to the trace direction central authorities of this sun gear.Therefore, cause the axle center to tilt even because the part of the output shaft of planetary gears is weakened this output shaft is waved a little, also can between sun gear and planetary pinion, keep all the time good toe joint and touch.Therefore, can carry out the rotation of sun gear of planetary gears and planetary revolution etc. with very stable state, especially can further prolong the life-span of (comprising planetary bearing) each bearing.
The invention effect
A kind of small-sized, lightweight, cost is low and reliability is high, the life-span is long used for wind power generation speed increaser can be provided according to the present invention.
Description of drawings
Fig. 1 is the integrally-built sectional view of used for wind power generation speed increaser that an example of embodiments of the present invention is shown.
Fig. 2 is the sectional view of major component of the speed increaser of presentation graphs 1.
Fig. 3 is the diagram of formation form that schematically illustrates the convex surface processing of sun gear in the above-mentioned mode of execution.
Fig. 4 is the sectional view of the major component of the related used for wind power generation speed increaser of expression another embodiment of the present invention.
Fig. 5 is the expression of the figure formation form of common convex surface processing is carried out in to(for) gear, and wherein (A) is stereogram, (B) is the diagram corresponding with Fig. 3.
Fig. 6 is the plan view of an integrally-built example that represented in the past the wind power plant of (and the present invention).
Fig. 7 is the stereogram of nacelle internal structure of the wind power plant of presentation graphs 6.
Fig. 8 is the sectional view that expression is arranged on an example of the in the past used for wind power generation speed increaser in the nacelle of wind power plant of Fig. 6.
Embodiment
Below, with reference to the accompanying drawings an example of embodiments of the present invention is elaborated.
About the basic structure of the wind power plant that is assembled with speed increaser involved in the present invention is identical with the structure of utilizing Fig. 6 and Fig. 7 explanation, therefore omit repeat specification, below the structure of speed increaser itself is elaborated.
Fig. 1 is the whole sectional view of used for wind power generation speed increaser 50 of an example of expression embodiments of the present invention, and Fig. 2 is the sectional view of its major component of expression.
At first, with reference to figure 1 as can be known, this used for wind power generation speed increaser 50 possesses planetary gears 52 elementary, and possesses the 1st parallel-axes gears mechanism 54, the 2nd parallel-axes gears mechanism 56 at middle rank and rear class.From the rotation of the rotor head (identical with rotor head 4 in the past: with reference to figure 6 and Fig. 7) of input shaft 58 input by amounting to 3 grades gear mechanism 52,54,56 by speedup, and from output shaft 60 outputs.In output shaft 60 links generator (identical with generator 11 in the past: with reference to figure 7) is arranged, the professional etiquette of going forward side by side is generated electricity surely.
Described planetary gears 52 comprises: be rotatably freely supported on 3 (only illustrating 1 among Fig. 2) planetary pinions 68 of this planet pin 64, this planetary pinion 68 meshed and be fixed in housing simultaneously internal gear 70, the sun gear 72 that reaches planetary pinion 68 simultaneously outer gearings in the planet pin 64 of this wheel carrier 62, via bearing 65 with input shaft 58 integrated wheel carriers 62, dual-supporting.These planetary pinions 68, internal gear 70 and sun gear 72 consist of by spur gear in this embodiment, but also can be made of spiral gear.
The rotation of the rotor head (4) that causes because of wind-force from input shaft 58 integrated wheel carriers 62 inputs, and take out rotation after the speedups from (the planetary gears 52) output shaft 80 that is integrated with sun gear 72.Output shaft 80 former states (directly) of planetary gears 52 become the input shaft of the 1st parallel-axes gears mechanism 54, and the 1st spiral gear 86 of the 1st parallel-axes gears mechanism 54 links via spline 88.
The present invention be applicable to wherein planetary gears 52 and the connecting arrangement (describing in detail in the back) between the 1st parallel-axes gears mechanism 54.
The 1st spiral gear 86 and 90 engagements of the 1st helical pinion.Consist of the 1st parallel-axes gears mechanism 54 by the 1st spiral gear 86 and the 1st helical pinion 90.
The 1st helical pinion 90 vertical cuts are formed at the 2nd jack shaft 92.The 2nd spiral gear 94 links with the 2nd jack shaft 92 in the circumferential direction of the circle via key 96.The 2nd spiral gear 94 and 100 engagements of the 2nd helical pinion.The 2nd helical pinion 100 vertical cuts are formed at the output shaft 60 of this speed increaser 50.Consist of the 2nd parallel-axes gears mechanism 56 by the 2nd spiral gear 94 and the 2nd helical pinion 100.Output shaft 60 is via bearing 103,105, and rotation is supported by housing 74 freely.
Below, main reference Fig. 2 is elaborated near the structure the linking department of planetary gears 52 and the 1st parallel-axes gears mechanism 54.
As mentioned above, in the present embodiment, the sun gear 72 of planetary gears 52 is integrated with the output shaft 80 of this planetary gears 52.Be that sun gear 72 is made by cutting formation sun gear 72 from single part with output shaft 80.The output shaft 80(of planetary gears 52 is without coupling etc.) former state (directly) becomes the input shaft of the 1st parallel-axes gears mechanism 54.
The output shaft 80 of planetary gears 52 possesses the sun gear forming portion 80A that is formed with sun gear 72, the 1st minor diameter 80B, the 2nd minor diameter 80C that forms continuously from this sun gear forming portion 80A and the spline forming portion 80D that is formed with described spline 88.The root diameter of sun gear forming portion 80A is d1, and the outside diameter d 2 of the 1st minor diameter 80B is than the only little 2 Δ 1(d1 of root diameter d1 of this sun gear forming portion 80A＞d2).And the outside diameter d 3 of the 2nd minor diameter 80C is than the outside diameter d 2 only little 2 Δ 2(d2 of the 1st minor diameter 80B＞d3).And the root diameter d4 of spline forming portion 80D is than the outside diameter d 3 of the 2nd minor diameter 80C large 2 Δ 3(d3＜d4) only.Namely, the diameter of the 2nd minor diameter 80C becomes than the 1st minor diameter 80B of its both sides and the less (d3＜d2 of spline forming portion 80D, d3＜d4), and its axial length L 1 account for planetary gears 52 output shaft 80 integral body axial length L o roughly half, combining therewith forms so-called " frangible portion ".
On the other hand, implemented convex surface processing at the sun gear 72 that is integrally formed at output shaft 80 and processed (tooth trace adjustment).In this mode of execution, as shown in Figure 3, the Xc of trace direction central authorities implements this convex surface processing processing " asymmetric " relatively.The dotted line Ko of Fig. 3 carries out the original tooth trace shape (end surface shape of width direction) that convex surface is processed the sun gear 72 before processing, and solid line K1 carries out convex surface processing to process tooth trace shape afterwards.Usually, when the flank of tooth of gear is carried out convex surface processing and processes, shown in Fig. 5 (A), process to carry out convex surface processing with respect to the mode of the central Xc symmetry of trace direction X.Shape Ko, the K2 of front and back are processed in the convex surface processing that even illustrates on the trace direction X, then such as Fig. 5 (B).In addition, the sun gear 72 of present embodiment is spur gear, so trace direction X is consistent with axial (facewidth direction) of sun gear 72.In addition, the shape profiling that the processing of these convex surfaces is processed is the qualitiative trends of processing (convex surface amount of finish) for the ease of understanding convex surface processing on trace direction X, therefore enlarges the convex surface amount of finish with respect to the size of trace direction X and obtains very large.
Return the description of the present embodiment of Fig. 3, (do not implement convex surface processing in the mode of this central Xc symmetry with respect to trace direction X) in the present embodiment, and implement convex surface processing in the mode with respect to the central Xc " asymmetric " of trace direction X.Particularly, at the flank of tooth of sun gear 72, the minimum part Xm that carries out convex surface processing is than the wider scope of the 1st opposition side scope X2 of parallel gears mechanism from the central Xc of the trace direction X of this sun gear 72 is carried out the trace direction X of the 1st parallel-axes gears mechanism side that convex surface processing processes to a lateral deviation opposite with the 1st planar axes gear mechanism from Xs(scope X1).In addition, in this mode of execution, the convex surface amount of finish δ 2 identical (δ 1=δ 2) of the convex surface amount of finish δ 1 of the 1st parallel-axes gears mechanism side and the 1st parallel-axes gears mechanism opposition side in the trace direction end face of sun gear 72.Therefore, finally carrying out the convex surface processing milder than the 1st parallel-axes gears mechanism opposition side in the 1st parallel-axes gears mechanism 54 sides processes.
Then, the effect of the related used for wind power generation speed increaser 50 of this mode of execution described.
The rotation of air vane (5) is passed to the input shaft 58 of speed increaser 50.The rotation of input shaft 58 is input to planetary gears 52 via wheel carrier 62 as the revolution of planetary pinion 68, by the relative rotation of planetary pinion 68, internal gear 70 and sun gear 72 these 3 gears, outputed to output shaft 80 with sun gear 72 integrated (planetary gears 52) by the rotation of speedup.
The rotation of the output shaft 80 of planetary gears 52 is directly delivered to the 1st spiral gear 86 of the 1st parallel-axes gears mechanism 54 via spline 88.The rotation of the 1st spiral gear 86 is delivered to the 1st helical pinion 90, and the 2nd jack shaft 92 is rotated thus.If the rotation of the 2nd jack shaft 92, then the 2nd just rotation of spiral gear 94, and via with the 2nd helical pinion 100 of the 2nd spiral gear 94 engagements, make output shaft 60 rotations of speed increaser 50.
Wherein, near the linking department of planetary gears 52 and the 1st parallel-axes gears mechanism 54, bring into play following effect.
That is, if from input shaft 58 input running torques, when then transmitting this running torque, in planetary gears 52 and the 1st parallel-axes gears mechanism 54, certainly lead to vibration.The vibration of the vibration of planetary gears 52 and the 1st parallel-axes gears mechanism 54, because the equal reason of the machine-processed difference of rotation and rotating speed causes separately frequency characteristic (waveform of vibration) difference, therefore (if not imposing any measure) can cause interfering with each other and produce resonance, and the vibration of speed increaser 50 integral body is further increased.Even do not produce clearly resonance, especially when propagating the vibration of this High Rotation Speed from the 1st parallel-axes gears mechanism 54 side direction planetary gears, 52 sides of High Rotation Speed, (between sun gear 72 and the internal gear 70) of the planetary pinion 68 of planetary gears 52 rotate smoothly and the revolution meeting impaired, especially might affect life-span of bearing 65.
Yet, in this embodiment, there is the 2nd minor diameter 80C in output shaft 80 at planetary gears 52, this minor diameter has the also little diameter d 3 of diameter d 2, d4 than its both sides (the 1st minor diameter 80B and spline forming portion 80D), therefore can make the 2nd minor diameter 80C absorb/cut off the propagation of this vibration as frangible portion performance function.Therefore, the propagation of the vibration between planetary gears 52 and the 1st parallel-axes gears mechanism 54 is effectively suppressed, and the generation of resonance is inhibited.And, especially be transferred to planetary gears 52 sides because prevent vibration from the 1st parallel-axes gears mechanism 54 sides, so the planetary pinion 68 of this planetary gears 52 (between sun gear 72 and the internal gear 70) rotate smoothly and revolve round the sun and guaranteed, especially can prolong the life-span of bearing 65.
The present invention works out various versions.
At first, the minor diameter that is formed on the output shaft (input shaft of parallel-axes gears mechanism) of planetary gears is in said embodiment, long single minor diameter vertically, but for example also can shown in Fig. 4 (A), be out of shape.In the variation shown in Fig. 4 (A), basic structure is identical with described mode of execution, therefore for simplicity, at corresponding part mark rear 2 identical symbols.The axial length L 2 of the 2nd minor diameter 180C of the output shaft 180 of shortening planetary gears 152 more forms the axial central 114C of the 2nd minor diameter 180C specific output axle 180 by sun gear 172 sides.By this structure, waving of the 1st parallel-axes gears mechanism side of minimally inhibition (linking by spline 188 and the 1st spiral gear 186) output shaft 180, the simultaneously convex surface processing by sun gear 172 effectively absorbs waving of planetary gears 152 sides.
And shown in Fig. 4 (B), the minor diameter of the output shaft of planetary gears can be formed on this and export axial a plurality of position.In the example of Fig. 4 (B), output shaft 280 possesses the 1st minor diameter 280B, the 3rd minor diameter 280D that external diameter is d7, and spline forming portion 280F, and has diameter (d8) than these the 2nd also little minor diameter 280C and these 2 minor diameter of the 4th minor diameter 280E.Wherein, itself external diameter of the 2nd minor diameter 280C and the 4th minor diameter 280E is d8, and the outside diameter d 7 of both sides is larger separately, is equivalent to " minor diameter " of the present invention.Such as Fig. 4 (B), if form a plurality of minor diameter, then can more effectively bring into play fragility, and can more improve the spread restraint effect of vibration.
So, in the present invention, minor diameter for which kind of structure specifically to form the output shaft of planetary gears with is not particularly limited, and sets its size, shape, quantity of formation or formation position etc. according to the size of the vibration that will absorb or frequency characteristic etc. and gets final product.
And, with regard to the concrete size or shape (for example asymmetric with which kind of degree from trace direction central authorities) of the convex surface amount of finish in the convex surface processing processing procedure of sun gear, the degree of waving of the output shaft of the planetary gears also formation method because of minor diameter is different, therefore waves degree set according to this and gets final product.
In addition, the concept that in " convex surface processing " of the present invention concept, comprises " end relief (teeth) ".End relief is the processing method at the two end part of the trace direction of the gear of only shooting off from Gear Contact Surface, but is not the processing method that breaks away from aim of the present invention.Be applied to when of the present invention when end relief is processed, key be the scope of teeth trace direction relative to size central be asymmetric.
The present invention can be used in the speed increaser of wind power plant.
The full content of specification, accompanying drawing and the claim of the Japanese publication 2011-063892 of 23 applications March in 2011 is applied in this specification by reference.
The explanation of symbol:
The 1-wind power plant, the 3-nacelle, 4-rotor head, 5-air vane, the 11-generator, the 50-speed increaser, 52-planetary gears, 54-the 1st parallel-axes gears mechanism, 56-the 2nd parallel-axes gears mechanism, the 58-input shaft, 60-output shaft, 80,180, the output shaft (input shaft of the 1st parallel-axes gears mechanism) of 280-planetary gears.
Claims (4)
1. a used for wind power generation speed increaser is characterized in that,
Described used for wind power generation speed increaser possesses planetary gears with sun gear, and in the parallel-axes gears mechanism that the rear class of this planetary gears arranges,
The described sun gear of described planetary gears is formed on the output shaft of this planetary gears,
Axial at least 1 position of the described output of this planetary gears becomes diameter less than the minor diameter of its both sides, and,
Trace direction central authorities with respect to this sun gear asymmetricly carry out convex surface processing to the flank of tooth of described sun gear.
2. used for wind power generation speed increaser according to claim 1 is characterized in that,
Be formed with described minor diameter at the axial a plurality of positions of the output of described planetary gears.
3. used for wind power generation speed increaser according to claim 1 and 2 is characterized in that,
Described minor diameter is formed on than the axial central authorities of the output shaft of described planetary gears and more leans on described sun gear side.
4. each described used for wind power generation speed increaser is characterized in that according to claim 1～3,
On the flank of tooth of described sun gear, minimum carry out part that the processing of described convex surface processes than the trace direction mediad of this a sun gear lateral deviation opposite with parallel-axes gears mechanism from.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-063892 | 2011-03-23 | ||
| JP2011063892A JP2012197773A (en) | 2011-03-23 | 2011-03-23 | Speed increasing gear for wind turbine |
| PCT/JP2011/076769 WO2012127736A1 (en) | 2011-03-23 | 2011-11-21 | Speed increasing gear for wind turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103370537A true CN103370537A (en) | 2013-10-23 |
Family
ID=46878924
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011800651219A Pending CN103370537A (en) | 2011-03-23 | 2011-11-21 | Speed increasing gear for wind turbine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2012197773A (en) |
| CN (1) | CN103370537A (en) |
| WO (1) | WO2012127736A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114655025A (en) * | 2019-12-26 | 2022-06-24 | 株式会社爱信 | Vehicle drive device |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5938359B2 (en) * | 2013-02-28 | 2016-06-22 | 住友重機械工業株式会社 | Reduction gear used for wind power generation equipment |
| KR102193884B1 (en) | 2013-07-08 | 2020-12-23 | 에프엘스미쓰 에이/에스 | Heavy duty drive arrangement and mill |
| CN108506427A (en) * | 2018-05-31 | 2018-09-07 | 福州大学 | A kind of speed increaser and its working method suitable for high-power transmission |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005023978A (en) * | 2003-06-30 | 2005-01-27 | Mitsubishi Heavy Ind Ltd | Helical gear and speed increasing machine for windmill using the same |
| JP2005233277A (en) * | 2004-02-18 | 2005-09-02 | Komatsu Ltd | Gear meshing structure of planetary gear device |
| CN1849468A (en) * | 2003-11-20 | 2006-10-18 | 汉森传动***国际公司 | Gear transmission unit with planetary gears |
| CN101893061A (en) * | 2009-05-20 | 2010-11-24 | 汉森传动***国际公司 | Planetary gear transmission unit |
-
2011
- 2011-03-23 JP JP2011063892A patent/JP2012197773A/en not_active Withdrawn
- 2011-11-21 WO PCT/JP2011/076769 patent/WO2012127736A1/en active Application Filing
- 2011-11-21 CN CN2011800651219A patent/CN103370537A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005023978A (en) * | 2003-06-30 | 2005-01-27 | Mitsubishi Heavy Ind Ltd | Helical gear and speed increasing machine for windmill using the same |
| CN1849468A (en) * | 2003-11-20 | 2006-10-18 | 汉森传动***国际公司 | Gear transmission unit with planetary gears |
| JP2005233277A (en) * | 2004-02-18 | 2005-09-02 | Komatsu Ltd | Gear meshing structure of planetary gear device |
| CN101893061A (en) * | 2009-05-20 | 2010-11-24 | 汉森传动***国际公司 | Planetary gear transmission unit |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114655025A (en) * | 2019-12-26 | 2022-06-24 | 株式会社爱信 | Vehicle drive device |
| CN114655025B (en) * | 2019-12-26 | 2024-03-22 | 株式会社爱信 | Driving device for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012127736A1 (en) | 2012-09-27 |
| JP2012197773A (en) | 2012-10-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20130042711A1 (en) | Double involute pinion-face gear drive system | |
| CN102252062B (en) | Complex precise cycloidal speed reducer | |
| US7291088B2 (en) | Method for effecting low-loss torque transmission in planetary gears | |
| JP5932546B2 (en) | Planetary gear train and corresponding manufacturing method | |
| WO2011161742A1 (en) | Gear with free curved surfaces | |
| CN105473891A (en) | Reducer | |
| US20100061839A1 (en) | Shaft coupling arrangement | |
| CN102472368B (en) | Planetary gear mechanism | |
| JPH06280970A (en) | Planetary gearing device and speed increasing/decreasing gear device | |
| EP2337970B1 (en) | Epicyclic reduction gear device with balanced planet wheels | |
| CN103370537A (en) | Speed increasing gear for wind turbine | |
| CN102619946B (en) | Branch torque transmission structure and mounting method thereof | |
| US20200088105A1 (en) | Gas turbine engine for an aircraft with an engine shaft | |
| CN105121901A (en) | Reduction gear | |
| CN102654104B (en) | Deceleration device for wind power generating apparatus and deceleration device provided with output pinion | |
| Oh et al. | A study on modeling and optimization of tooth microgeometry for a helical gear pair | |
| CN101839308B (en) | Reduction gear for natural energy recovery system | |
| CN203067711U (en) | Differential gear mechanism of bevel gears | |
| EP2699821B1 (en) | Rotors formed using involute curves | |
| CN102817967B (en) | Speed-changing gear device | |
| Zhang et al. | Introduction to mechanisms | |
| EP3822511A1 (en) | High-ratio reducer | |
| KR101690151B1 (en) | Speed reducer with helical conjugate dual cycloid tooth profile | |
| Sheng et al. | Dynamic load sharing characteristics and sun gear radial orbits of double-row planetary gear train | |
| CN107131282A (en) | Merge the high speed roller gear dynamic mesh stiffness computational methods of back of tooth contacting mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20131023 |