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WO2011067633A1 - Profil de dent d'engrenage d'une eolienne - Google Patents

Profil de dent d'engrenage d'une eolienne Download PDF

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Publication number
WO2011067633A1
WO2011067633A1 PCT/IB2010/001626 IB2010001626W WO2011067633A1 WO 2011067633 A1 WO2011067633 A1 WO 2011067633A1 IB 2010001626 W IB2010001626 W IB 2010001626W WO 2011067633 A1 WO2011067633 A1 WO 2011067633A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure angle
gear
gears
generating device
electric 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.)
Ceased
Application number
PCT/IB2010/001626
Other languages
English (en)
Inventor
Edwin C. Hahlbeck
Frank Klein
Amir S. Mikhail
Anthony Chobot
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Clipper Windpower LLC
Original Assignee
Clipper Windpower LLC
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Clipper Windpower LLC filed Critical Clipper Windpower LLC
Publication of WO2011067633A1 publication Critical patent/WO2011067633A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • 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
    • 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
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/25—Wind motors characterised by the driven apparatus the apparatus being an electrical generator
    • 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
    • F05B2250/00—Geometry
    • F05B2250/70—Shape
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • This invention relates to gearing apparatus for distributing a source of energy to one or more multiple rotational devices, and more particularly to a specific gear tooth profile of a planetary gear stage to increase the capacity of a loaded planetary gear stage .
  • an epicyclic gear stage comprises planet gears, a sun gear and a ring gear located around the sun gear.
  • the planet gears are located between the sun and ring gears .
  • planet gear teeth are loaded in both directions since one side engages the sun gear and the opposite side engages the ring gear.
  • the sun gear is generally a much smaller external gear and rotates at a higher speed, thus it not only has lower strength capacity (relative to the larger internal ring gear) but also accumulates more fatigue cycles .
  • the above mentioned objects of the invention are solved by an electric power-generating device that converts fluid flow to electricity.
  • the device comprises a rotor having blades that rotate in response to fluid flow, a main power input shaft coupled to said rotor, and one or more gear stage, coupled to the main power input shaft.
  • the gears of the at least one gear stage comprise an asymmetric gear tooth profile with high and low pressure angle flanks, whereas the high pressure flank has a pressure angle which is greater than the pressure angle of the low pressure angle flank.
  • the invention pertains to a novel gear tooth profile for high torque gears such as those used in wind
  • the invention uses an asymmetric gear tooth-profile on the gears of at least one planetary gear stage.
  • the tooth profile is such that the pressure angle is intentionally
  • the asymmetrical gearing allows for more design freedom in view of larger radii that can be created in the roots of the teeth, thus allowing for a greater rated strength capacity. Further, the differing pressure angles on both sides of each tooth reduce gear tooth stress when loaded on the higher pressure angle side than the other side.
  • the invention provides a solution to the aspect that opposite flanks (profiles) of the gear tooth are functionally different for most gears. The work-load on one profile is significantly higher and/or is applied for longer periods of time than on the opposite one.
  • the asymmetric tooth shape accommodates this functional difference.
  • the design intent of asymmetric teeth is to improve performance of main contacting profiles (driven tooth flank) by sacrificing performance on the opposite profiles (coast tooth flank) . These opposite profiles (coast tooth flank) are unloaded or lightly loaded, and usually work for a relatively short period compared to the highly loaded driven tooth flank. The improved performance could mean
  • the at least one gear stage is a planetary gear stage which
  • Such a planetary gear stage or epicyclic gear system provides the advantages of high power density, large reduction in a small volume, multiple kinematic combinations, pure torsional reactions, and coaxial shafting.
  • the pressure angle of each high pressure angle flank is set to greater than 24°.
  • the pressure angle of each low pressure angle flank is set to less than 21°.
  • the low pressure angle flanks of the teeth of the sun and planet gears and the high pressure angle flanks of the teeth of the ring and planet gears mesh, resulting also in a better mechanical efficiency.
  • the root radius of each tooth of the gears is in the range of R/5 ⁇ R ⁇ R*5.
  • the ring, planet and sun gears may be helical gears, thus leading to a better running smoothness and lower noise emission.
  • a second gear stage is arranged between the main power input shaft and the first gear stage.
  • the second gear stage is a planetary gear stage and comprises ring, planet and sun gears, wherein the ring gear of the first planetary gear stage is coupled to the main power input shaft and the sun gear of the first planetary gear stage is coupled to the ring gear of the second planetary gear stage .
  • the planet gears of the second planetary gear stage are coupled to the main power input shaft.
  • the planetary gear stages or epicyclic stages are interconnected and form a two stage device operating in a differential (coupled) configuration.
  • the electric power-generating device may be used in a wind turbine gearbox .
  • the advantage of this invention is that the planetary stage or stages is such that the pressure angle that corresponds to a lower stress situation is engaged on the sun gear mesh, whereas the pressure angle that corresponds to a higher stress situation is engaged on the ring gear mesh.
  • the invention avoids the drawback of a typical symmetric gear tooth profile that is designed to accommodate the load scenario at the sun mesh and the ring gear mesh which results in an overdesigned gear system.
  • a further advantage of the invention is that gearbox efficiency is improved since the lower pressure angle gear mesh inherently has a better mechanical efficiency.
  • the present invention is uniquely suitable for wind turbine application because the gears are predominantly loaded in one direction, newer megawatt turbines have to contend with
  • This invention has the advantage that it increases the gear- torque capacity rating relative to size and weight of the planetary gear stages. This enables the most optimal lightweight, compact and high efficiency design.
  • FIGURE 1 is a schematic view of a planetary gear stage
  • FIGURE 2 is a detail view of the meshing of sun, planet and ring gear of the planetary gear stage shown in FIGURE 1;
  • FIGURE 3 is a detail view of the gear meshing according to the invention.
  • FIGURE 4 shows a comparison of symmetrical and asymmetrical tooth profiles
  • FIGURE 5 is a schematic representation of a two-stage gearing apparatus
  • FIGURE 6a is a perspective view of a ring gear of the two- stage gearing apparatus shown in FIGURE 5
  • FIGURE 6b shows details of the tooth profile of the ring gear
  • FIGURE 7a is a perspective view of a planet gear of the two- stage gearing apparatus
  • FIGURE 7b shows details of the tooth profile of the planet gear
  • FIGURE 8a is a perspective view of a sun gear of the two- stage gearing apparatus shown in FIGURE 5 .
  • FIGURE 8b shows details of the tooth profile of the sun gear.
  • a wind turbine is a rotating machine, which converts the energy in wind into electrical energy. Rotor blades are
  • gearbox which turns the slow rotation of the blades into a faster rotation that is more suitable to drive electrical generators.
  • the gearbox steps up the rotation of the rotor blades to drive one ore more generators .
  • the invention shown in FIGURES l-8b relates to an electric power-generating device that converts fluid to electricity.
  • the invention relates to a multi-stage gearing apparatus for distributing a source of energy to multiple rotational devices.
  • the device comprises a rotor with blades rotating in response to fluid flow, a main power input shaft coupled to the rotor and at least one epicyclic or planetary gear stage .
  • an epicyclic or planetary gear stage 200 comprises at least one planet gear 210, a sun gear 220 and a ring gear 230 located around the sun gear 220.
  • the sun gear 220 is the central gear which is located along a central axis 205 and comprises sun gear teeth 221 around an outer circumference of the sun gear 220.
  • the planet gears 210 are located between the sun gear 220 and the ring gear 230 and engage both.
  • the planet gears 210 comprise planet gear teeth 211 around an outer circumference of each planet gear 210 and rotate about pins that establish axes that are offset from the central axis.
  • the pins form part of a planet carrier 240 that likewise share the central axis 205.
  • the planet carrier 240 holds peripheral the planet gears 210, all of the same size, that mesh with the sun gear 220.
  • the planet gears 210 are mounted on the planet carrier 240.
  • the ring gear 230 is an outer ring gear or annulus which is centered with respect to the central axis and comprises ring gear teeth 231 around an inner circumference of said ring gear 230.
  • the inward-facing ring gear teeth 231 mesh with the planet gears 210.
  • the planetary carrier 240 is held stationary and the ring gear 230 is used as input, the stationary planet gears 210 rotate about their own axes at a rate determined by the number of teeth in each gear. This rotation of the planet gears 210 in turn drive the sun gear
  • the planetary carrier 240 can be used as an input shaft which may be connected to the rotor blade shaft and will rotate with the rotor blade shaft.
  • FIGURE 3 is a detail of the planetary gear stage shown in FIGURES 1 and 2.
  • the opposite face (the low pressure angle flank 223) comprises a pressure angle ⁇ which is less than the opposite flank pressure angle ⁇ 2 , so that the gear tooth profile of the sun gear 220 comprises an asymmetric gear tooth profile.
  • one face (the low pressure angle flank 232) of the ring gear tooth 231 comprises a pressure angle ⁇ which is less than the opposite flank pressure angle ⁇ 2 .
  • the opposite face (the high pressure angle flank 233) comprises a pressure angle ⁇ 2 which is greater than the opposite flank pressure angle piso that the gear tooth profile of the ring gear 230 comprises also an asymmetric gear tooth profile.
  • each of the planet gear teeth 211 comprises an asymmetric gear tooth profile with differing pressure angles ⁇ and ⁇ 2 on its opposite side faces or flanks
  • the planet gear teeth 211 are loaded on both faces or flanks 212 and 213, since one face or flank 212 of the planet gear tooth 211 engages the sun gear 220 and the opposite side face 213 of the planet gear tooth 211 engages the ring gear 230.
  • the high pressure angle flanks 222, 212 of the teeth 221, 211 of the sun and planet gears 220, 210 and the low pressure angle flanks 233 In operation under forward load conditions, the high pressure angle flanks 222, 212 of the teeth 221, 211 of the sun and planet gears 220, 210 and the low pressure angle flanks 233,
  • the pressure angle ⁇ 2 of the face 222 of each of the sun gear teeth 221 interacting with the planet gear teeth 211 is set to 27°
  • the pressure angle ⁇ 2 of the face 233 of each of the ring gear teeth 231 interacting with the planet gear teeth 211 is set to 17°.
  • the asymmetric gear tooth profile shows a sun gear 220, a planet gear 210 and a ring gear 230 with 17-degree and 27-degree pressure angles.
  • pressure angle ⁇ 2 of each high pressure angle flank 212, 222, 232 is set to greater than 24°, whereas the pressure angle ⁇ ⁇ of each low pressure angle flank 213, 223, 233 is set to less than 21°.
  • the invention uses an asymmetric gear tooth-profile on the gears of a planetary gear stage.
  • the tooth profile is such that the pressure angle is intentionally different on opposite sides of the gear teeth of the sun, planet and ring gears.
  • the advantage of an asymmetric gear tooth profile with the differing pressure angles on both sides of the tooth is that the gear tooth stress is reduced when loaded in one direction (the higher pressure angle flank or drive side flank) than the other (the low pressure angle flank or coast side flank) .
  • Planet gear teeth are loaded in both directions since one side engages the sun gear and the opposite side engages the ring gear.
  • the sun gear is generally a much smaller external gear and rotates at a higher speed, thus it not only has lower strength capacity (relative to the larger internal ring gear) but also accumulates more fatigue cycles.
  • the arrangement shown in FIGURE 3 reduces operating stress or conversely enables a higher torque load capacity for a given size gear net.
  • FIGURE 4 shows a comparison of a symmetrical tooth profile 100 (dotted line) with a pressure angle of 20° and an asymmetrical tooth profile 110 (continuous line) with differing pressure angles.
  • the planetary stage employs asymmetrical tooth forms.
  • the asymmetrical gear tooth form configuration allows use of a larger root fillet and stronger tooth shape as shown in FIGURE 4.
  • the planet to annulus mesh inheriently has greater strength and lower contact stress and the asymmetrical tooth form concept trades this "extra" capacity for increasing the load limiting sun to planet mesh. This effect is depicted in Figure 4.
  • the asymmetrical tooth ' form may be further enhanced by forming the root fillet with a non-generating cutter (gashing) to allow more control over the critical tooth root shape .
  • FIGURE 5 is a schematic representation of a two- stage gearing apparatus or gearbox 300, in which the present invention may be embodied.
  • the gearing apparatus or gearbox 300 consists of two epicyclic or planetary gear stages, namely a first planetary gear stage 310 and a second planetary gear stage 320.
  • the two-stage gearing apparatus 300 is at least part of an electric power-generating device that converts fluid flow to electricity.
  • the first planetary gear stage 310 comprises a sun gear 311, a ring gear 312 located around the sun gear 311 and multiple planet gears 313 located between and engaged with the sun gear 311 and the ring gear or annulus 312.
  • the second planetary gear stage 320 comprises also a sun gear 321, a ring gear 322 located around the sun gear 321 and multiple planet gears 323 located between and engaged with the sun gear 321 and the ring gear or annulus 322. It should be noted that the number of planet gears in each stage of the gear train 300 can be changed according to specific design and/or load
  • the two planetary gear stages 310, 320 operate in a differential (coupled) configuration.
  • the numerical values used in subscripts refer to the stage number.
  • the epicyclic gear elements are named S for sun, P for planet and A for annulus (ring) and combined in subscripts using the stage number.
  • the loads of the gearing apparatus or gearbox 300 are based on rotor torques and speeds transmitted via a main power input shaft ("INPUT" in FIGURE 5) .
  • the main power input shaft (“INPUT") powers the ring gear or annulus 312 of the first planetary gear stage 310 so that the ring gear 312 will rotate with the main power input shaft.
  • the main power input shaft powers the planet gears 323 of the second planetary gear stage 320 so that the input is divided in the second planetary gear stage 320.
  • the gears have tooth flank modifications to improve loaded mesh conditions to compensate for deflections and alignment errors due to manufacturing tolerances. These attributes are considered in a 3D mesh analysis that predicts the peak stress / mean stress ratio to be used in power rating.
  • FIGURE 6a is a perspective view of the ring gear 312 of the first planetary gear stage 310 in FIGURE 5.
  • the ring gear 312 is located around the sun gear 311 and comprises a ring gear tooth profile 330 around its inner circumference.
  • FIGURE 6b shows a detailed view of the fillet between neighbouring teeth.
  • reference numeral 331 denotes the starting points of the fillet between two neighbouring teeth, whereas the nominal depth 332 of the ring gear tooth is measured from the ground of the fillet to the tooth tip.
  • the reference numerals 333, 334 and 335 denote root radii, which can be optimized to achieve a lower stress in the tooth root relative to a gear with symmetric tooth profiles.
  • the tooth form leads to an asymmetrical profile comprising a high pressure angle flank 336 which in one embodiment may have a pressure angle of approx. 27° and a low pressure angle flank 337 with a pressure angle of approx. 17°.
  • FIGURE 7a is a perspective view of one of the planet gears 313 of the two-stage gearing apparatus 300, whereas FIGURE 7b shows the tooth profile 340 of the planet gear 313 shown in FIGURE 7a.
  • the teeth of the planet gear 313 engage with the teeth of both the sun gear 311 and the ring gear 312.
  • reference numeral 341 denotes the starting points of the fillet between two neighbouring teeth, whereas the nominal depth 342 of the planet gear tooth is measured from the ground of the fillet to the tooth tip.
  • the reference numerals 343, 344 and 345 denote root radii, which can be optimized to achieve a lower stress in the tooth root relative to a gear with symmetric tooth profile.
  • embodiment may have a pressure angle of approx. 27° and a low pressure angle flank 347 with a pressure angle of approx. 17°.
  • FIGURE 8a is a perspective view of the sun gear 311 of the two-stage gearing apparatus shown in FIGURE 5, whereas FIGURE 8b shows the tooth profile 350 of the sun gear 311.
  • the teeth of the sun gear 311 engage with the teeth of the planet gears 313.
  • reference numeral 351 denotes the starting points of the fillet between two neighbouring teeth, whereas the nominal depth 352 of the planet gear tooth is measured from the ground of the fillet to the tooth tip.
  • reference numerals 353, 354 and 355 denote root radii, which can be optimized to achieve a lower stress in the tooth root relative to a gear with symmetric tooth profile.
  • FIGURE 8b the tooth form leads to the asymmetrical profile comprising a high pressure angle flank 356 which in one
  • embodiment may have a pressure angle of approx. 27° and a low pressure angle flank 357 with a pressure angle of approx. 17°.
  • a high input torque of a rotor is distributed between one or multiple
  • the generators via a torque-dividing gearbox.
  • the sum of the power producing capacities of the generators is equal to the maximum power delivered by the main shaft.
  • gears shown in the drawings may be replaced by any machine component consisting of a wheel attached to a rotating shaft that operate in pairs to transmit and modify rotary motion and torque
  • main power input shaft may be fitted directly onto a circular gear, or the main shaft may be indirectly linked to the circular gear.
  • a reciprocating main shaft may impart rotational motion to the circular gear or the main shaft may be combined with other gears or linkages to impart
  • the arrangement can have the input and output reversed. That is, the "input” becomes the output , the “output” becomes the input , and intermediate remains the same.
  • the rotational devices become prime movers, and the main shaft is connected to a driven machine .
  • the sources of power and respective appropriate rotational devices driven by the gearing include, but are not limited to (1) fossil fuels, such as diesel motor-generator sets and gas turbines; (2) nuclear fuels, such as steam turbines for nuclear power plants; (3) solar energy; (4) bio-energy technologies, such as making use of renewable plant material animal wastes and industrial waste; (5) thermal energy; (6) automotive energy, such as electric cars; (7) tunnel boring equipment; (8) mining
  • micro-turbines such as those using natural gas, gas from landfills or digester gas
  • marine drives such as rotating cement mixers and earth moving equipment.
  • other heavy equipment with a low speed drive such as rotating cement mixers and earth moving equipment.
  • generators may be replaced by prime movers, such as motors, to create a reduction gearbox to drive machines requiring high torque and slow speeds.

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  • 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)
  • Power Engineering (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un dispositif générateur d'énergie électrique qui transforme l'écoulement fluidique en électricité. Ledit dispositif comprend un rotor doté de pales qui tournent en réponse à l'écoulement fluidique; un arbre d'entrée de puissance principal couplé audit rotor; et au moins un étage de transmission, couplé à l'arbre d'entrée de puissance principal. Les engrenages (210, 220, 230) comprennent un profil de dent d'engrenage asymétrique à flancs de pression grand angle et angle faible (212, 213, 222, 223, 232, 233; 336, 337, 346, 347, 356, 357), le flanc de pression grand angle a un angle de pression (β2) qui est supérieur à l'angle de pression (β1) du flanc de pression angle faible.
PCT/IB2010/001626 2009-12-01 2010-07-02 Profil de dent d'engrenage d'une eolienne Ceased WO2011067633A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US28328709P 2009-12-01 2009-12-01
US61/283,287 2009-12-01

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WO2011067633A1 true WO2011067633A1 (fr) 2011-06-09

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015022129A3 (fr) * 2013-08-15 2015-09-11 Zf Friedrichshafen Ag Denture de crabotage pour une transmission de véhicule et transmission automatique à plusieurs rapports démultipliés de type train planétaire à pignons droits
DE102014208824A1 (de) * 2014-05-12 2015-11-12 Zf Friedrichshafen Ag Retarderhochtreiberstufe für eine Dauerbremseinrichtung, sowie Dauerbremseinrichtung
CN105626820A (zh) * 2015-06-04 2016-06-01 重庆大学 二级直齿行星轮的修形方法
DE102015218544A1 (de) 2015-09-28 2017-03-30 Schaeffler Technologies AG & Co. KG Planetengetriebe mit Planetenrädern mit unterschiedlichen Schrägungswinkeln
JP2017119462A (ja) * 2015-12-28 2017-07-06 株式会社シマノ 歯車およびこれを備える自転車用変速機構
CN118656935A (zh) * 2024-07-15 2024-09-17 东莞市星火齿轮有限公司 一种基于多级蜗杆齿轮传动结构的非对称齿廓设计方法

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GB630465A (en) * 1944-04-14 1949-10-13 Fairfield Mfg Company Gear wheels
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FR2226594A1 (fr) * 1973-04-21 1974-11-15 Zahnradfabrik Friedrichshafen
GB2004973A (en) * 1977-09-29 1979-04-11 Obrabiarek Precyzyj Ponar Cylindrical (spur) helical gear
JPS5590752A (en) * 1978-12-28 1980-07-09 Isuzu Motors Ltd Asymmetric gear apparatus
SU1060839A1 (ru) * 1982-08-27 1983-12-15 Предприятие П/Я В-2504 Зубчата передача
SU1155806A1 (ru) * 1983-12-09 1985-05-15 Предприятие П/Я В-2504 Зубчата эвольвентна передача
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EP1544504A2 (fr) * 2003-12-19 2005-06-22 Winergy AG Transmission planetaire, en particulier pour une centrale d'énergie éolienne
RU2272195C1 (ru) * 2004-10-07 2006-03-20 Федеральное государственное унитарное предприятие "Центральный институт авиационного моторостроения им. П.И. Баранова" Редуктор воздушного винта для турбовинтового авиационного двигателя

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US2403492A (en) * 1944-04-14 1946-07-09 Fairfield Mfg Company Gear
GB630465A (en) * 1944-04-14 1949-10-13 Fairfield Mfg Company Gear wheels
GB760091A (en) * 1954-10-25 1956-10-31 Caterpillar Tractor Co Gear tooth form
FR2226594A1 (fr) * 1973-04-21 1974-11-15 Zahnradfabrik Friedrichshafen
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