US20030008748A1 - Epicyclic gear system - Google Patents

Epicyclic gear system Download PDF

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Publication number
US20030008748A1
US20030008748A1 US09/894,665 US89466501A US2003008748A1 US 20030008748 A1 US20030008748 A1 US 20030008748A1 US 89466501 A US89466501 A US 89466501A US 2003008748 A1 US2003008748 A1 US 2003008748A1
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US
United States
Prior art keywords
carrier
inner race
raceways
gear
raceway
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.)
Abandoned
Application number
US09/894,665
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English (en)
Inventor
Gerald Fox
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to US09/894,665 priority Critical patent/US20030008748A1/en
Priority to JP2003508839A priority patent/JP2004531680A/ja
Priority to DE60205746T priority patent/DE60205746T2/de
Priority to EP02742292A priority patent/EP1399682B1/de
Priority to US10/481,708 priority patent/US7056259B2/en
Priority to PCT/US2002/020069 priority patent/WO2003002891A1/en
Publication of US20030008748A1 publication Critical patent/US20030008748A1/en
Abandoned legal-status Critical Current

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16H1/2836—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 planets relative to the planet carrier or by using free floating planets
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • F16C2240/82—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD
    • F16C2240/84—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD with full complement of balls or rollers, i.e. sum of clearances less than diameter of one rolling element
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • 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
    • F16H1/48—Special means compensating for misalignment of axes, e.g. for equalising distribution of load on the face width of the teeth

Definitions

  • This invention relates in general to gear systems and, more particularly, to an epicyclic gear system.
  • the typical epicyclic or planetary gear system basically has a sun gear provided with external teeth, a ring gear provided with internal teeth, and several planet gears located between the sun and ring gears and having external teeth which mesh with the teeth on the sun and ring gears.
  • the typical system has a carrier to which the planet gears are coupled. Either the sun gear, the ring gear, or the carrier is held fast, while power is delivered to and taken from the remaining two components, and thus power is transferred through the planetary system with a change in angular velocity and an inverse change torque.
  • the sun and ring gears for all intents and purposes share the same axis, a central axis, while the planet gears revolve about radially offset axes that are parallel to the central axis—or at least they should. Often the offset axes and the central axis are not parallel, and as a consequence the planet gears skew slightly between sun and ring gears. This causes excessive wear along the teeth of the planet, sun and ring gears, generates friction and heat, and renders the entire system overly noisy.
  • the present invention resides in an epicyclic gear system that has a sun gear, a ring gear around the sun gear and at least one planet gear located between and engaged with the sun and ring gears.
  • a carrier flange is offset axially from the planet gear and a carrier pin projects from it into the planet gear.
  • An inner race is attached to the carrier pin remote from the carrier flange, and it has a raceway which is presented toward a raceway carried by the planet gear. Rolling elements are organized in a row between the opposed raceways to enable the planet gear to revolve about the carrier pin.
  • the invention also resides in a carrier and bearing for such a gear system.
  • FIG. 1 is an exploded perspective view of an epicyclic gear system constructed in accordance with and embodying the present invention
  • FIG. 2 is a sectional view of the gear system at one of its planet gears and showing the coupling between the planet gear and the carrier;
  • FIG. 3 is a sectional view of the gear system similar to the system of FIG. 2, but showing a modified coupling.
  • a planetary transmission A (FIG. 1), which is actually an epicyclic gear system, has the capacity to transmit power of considerable magnitude, given its size and weight. In short, it has a high power density. In contrast to some planetary transmissions, the transmission A relies on meshing gears that are quite narrow, yet the teeth of those gears remain properly meshed, even when transmitting substantial power and torque.
  • the transmission A has a central axis X of rotation about which torque is transferred to the transmission A and delivered from it.
  • the transmission A basically includes a sun gear 2 having its axis coincident with the central axis X, a ring gear 4 which surrounds the sun gear 2 and shares the axis X with it, and planet gears 6 which mesh with and rotate between the sun and ring gears 2 and 4 about axes Y that are offset radially from, yet parallel to, the central axis X.
  • the transmission A has a carrier 8 to which the planet gears 6 are coupled, and the carrier 8 likewise shares the axis X.
  • the sun gear 2 Referring more specifically to the sun gear 2 , it is attached to a shaft 12 or some other supporting structure with which it normally rotates, but it may be fixed against rotation in some installations.
  • the sun gear 2 has external teeth 14 which are presented outwardly away from the axis X.
  • the ring gear 4 is typically fixed, and thus does not rotate, although it may rotate in some installations. In any event, the ring gear 4 has internal teeth 18 which are presented inwardly toward the axis X and toward the external teeth 14 on the sun gear 2 and lie concentric with them.
  • the ring gear 4 may be part of or integrated into a housing for the transmission A.
  • the carrier 8 includes (FIG. 1) a carrier flange 30 to which all of the planet gears 6 are coupled, it being offset axially beyond corresponding ends on each of the gears 6 .
  • the carrier 8 rotates about the axis X, although it may remain fixed in some installations.
  • the carrier 6 rotates, it is usually coupled to a shaft 32 that lies along the axis X.
  • the carrier 6 has carrier pins 34 which project from the flange 30 into the planet gears 6 , their axes generally corresponding to the axes Y of rotation for the planet gears 6 .
  • the carrier flange 30 opposite each planet gear 6 has a tapered hole 36 (FIG. 2).
  • the carrier pins 34 have tapered surfaces 38 which lead out to threaded ends 40 .
  • the tapered surfaces 38 conform in configuration to the tapered holes 36 in the flange 30 and indeed fit snugly into the tapered holes 36 so that the pins 34 project from the face of the carrier flange 30 that is presented toward the planet gears 6 .
  • the threaded ends 40 project beyond the other face of the carrier flange 30 where they are engaged by nuts 42 which are turned down snugly against that face. This lodges the carrier pins 34 at their tapered surfaces 38 firmly in the carrier flange 30 .
  • each pin 34 is, in effect, cantilevered from the carrier flange 30 .
  • Each carrier pin 34 projects through its planet gear 6 , and at the opposite end of the gear 6 , that is the end remote from the carrier flange 30 , is fitted to an inner race 46 which the planet gear 6 also encircles.
  • the inner race 46 has an end wall 48 and a sleeve 50 formed integral with the end wall 48 . Indeed, the sleeve 50 turns backwardly from the end wall 48 into the interior of the gear 6 and thus encircles the carrier pin 34 .
  • the end wall contains a bore 52 into which the end of the carrier pin 34 fits with an interference fit. At its very end the carrier pin 34 is joined to the end wall 48 along a weld 54 .
  • the interference fit together with the weld 54 secure the inner race 46 firmly to the carrier pin 34 .
  • the interior surface of the sleeve 50 is somewhat larger than the carrier pin 34 , and as a consequence the inner race 46 at its end wall 48 is cantilevered from the remote end of the carrier pin 34 .
  • the sleeve 50 of the inner race 46 lies within the interior of the planet gear 6 and has two tapered raceways 56 which taper downwardly to a separating rib 58 .
  • the raceways 56 which have their centers along the axis Y, are presented outwardly away from the axis Y and toward the raceways 24 on the gear 6 , each raceway 56 on the inner race 46 being opposite one of the raceways 24 on the gear 6 .
  • the separating rib 58 lies opposite the intervening surface 26 of the gear 6 .
  • Each raceway 56 on the inner race 46 tapers in the same direction as the raceway 24 toward which it is presented on the planet gear 6 .
  • the raceway 56 closest to the carrier flange 30 leads out to a thrust rib 60 that is formed integral with the sleeve 50 of the inner race 26 .
  • the other raceway 56 leads out to a cylindrical mounting surface 62 that surrounds the end wall 48 .
  • the mounting surface 62 has a rib ring 64 fitted to it with an interference fit and further secured with a weld 66 at its end.
  • the rib ring 64 extends axially from the weld 66 to the large end of the tapered raceway 56 , so the rib ring 64 forms another thrust rib, similar function to the rib 60 at the end of the inner race 46 that is remote from the carrier flange 30 .
  • each planet gear 6 and inner race 46 that the gear 6 surrounds is occupied by rolling elements in the form of tapered rollers 70 organized into two rows.
  • One row lies along the integral thrust rib 60 that is adjacent to the carrier flange 30 and contacts the opposed raceways 24 and 56 at that end, while the other row lies along the rib ring 64 that surrounds the end wall 48 of the inner race 46 and contacts the raceways 24 and 56 at that end.
  • the tapered rollers 70 contact the raceways 24 and 56 along their tapered side faces, there being generally line contact here. They also bear against the thrust rib 60 and rib ring 64 at their large end faces.
  • the thrust rib 60 and rib ring 64 prevent the rollers 70 from moving up the raceways 24 and 56 and being expelled from the annular region between the planet gear 6 and the inner race 46 .
  • the rollers 70 of each row are on apex, meaning that the conical envelopes in which the side faces of the rollers 70 of a row lie will have their apices located at a common point along the axis Y. This produces pure rolling contact between the side faces of the rollers 70 and the raceways 24 and 56 . While the rollers 70 of each row may be separated with a cage, preferably they are not so confined. This enables each row to contain the maximum number of rollers 70 .
  • the rollers 70 together with the inner race 46 and the raceways 24 on the planet gear 6 form a double row tapered roller bearing 72 that couples the planet gear 6 to the carrier pin 34 about which the gear 6 rotates.
  • the bearing 72 has the capacity to facilitate rotation of the planet gear 6 about the axis Y with minimal friction, while confining the gear 6 radially and axially on the carrier pin 34 .
  • the bearing 72 takes thrust loading in both axial directions.
  • the bearing 72 is set to a condition of light preload, and as a consequence no axial or radial clearances exist within it. This enables the gear 6 to rotate on the carrier pin 34 without axial or radial free motion and without wobbling.
  • the carrier pins 34 possess a measure of flexibly and indeed will flex well within their elastic limits when torque is transferred through the planet gears 6 .
  • the double cantilever arrangement enables the axes Y to remain parallel to the axis X, and hence the planet gears 6 remain properly meshed with the sun and ring gears 2 and 4 .
  • the planet gears 6 and likewise the sun and ring gears 2 and 4 , need not be excessively wide to account for off-center gear contact.
  • each carrier pin 34 at its cylindrical end is forced into the bore 52 in the carrier flange 48 of the inner race 46 for that pin 34 .
  • the carrier pin 34 at its end is welded to the end wall 48 , producing the weld 54 .
  • the rollers 70 for the row remote from the end wall 48 are placed along the raceway 56 that leads up to the thrust rib 60 , with the large end faces of those rollers being 70 against the rib 60 .
  • the planet gear 6 is installed over the inner race 46 and the row of rollers 70 on that race 46 .
  • the leading raceway 24 in the gear 6 seats against the side faces of those tapered rollers 70 .
  • the gear 6 is rotated to insure that the rollers 70 of the two rows seat against the raceways 24 and 56 and along the thrust rib 60 and rib ring 64 .
  • the bearing 72 will enter preload. The advance continues a short distance until the bearing 72 acquires the proper preload. Then the rib ring 64 is welded to the inner race 46 , producing the weld 66 .
  • the gear 6 , rollers 70 , inner race 46 and carrier pin 34 34 34 constitute a subassembly 76 , and enough subassemblies 76 are produced in the foregoing manner to complete the carrier 8 .
  • each subassembly 76 the tapered surface 38 of the carrier pin 34 extends beyond the open end of the sleeve 50 for the inner race 46 and beyond the corresponding end of the planet gear 6 as well.
  • the tapered surface 38 of the carrier pin 34 is inserted into one of the tapered holes 36 of the carrier flange 30 , whereupon one of the nuts 42 is engaged with the threaded end 40 that projects out of the flange 30 .
  • the nut 42 is turned down firmly against the carrier flange 30 to draw the tapered surface 38 of the carrier pin 34 snugly into the tapered hole 36 . This secures the carrier pin 34 and inner race 46 firmly to the carrier flange 30 .
  • the remaining subassemblies 76 are installed on the carrier flange 30 in a like manner.
  • the carrier 8 With the carrier 8 so assembled, it is installed over the sun gear 2 and into the ring gear 4 such that the external teeth 22 on the planet gears 6 engage the external teeth 14 in the sun gear 2 and the internal teeth 18 on the ring gear 4 .
  • the carrier pin 34 is formed integral with the inner race 46 .
  • the cantilever of the carrier pins 34 from the carrier flange 30 and the cantilever of the inner races 46 from the carrier pins 34 insures that the axes Y of rotation for the ring gears 6 remain parallel to the center axis X. As a consequence, the ring gears 6 do not require excessive width to resist skewing.
  • the inner races 46 being mounted directly on the carrier pins 34 , instead of on intervening components, together with the integration of the outer raceways 24 into the planet gears 6 , enables the bearings 72 to be of a diameter that is smaller than the diameters of bearings in more conventional epicyclic gear systems. This, in turn, can permit use of smaller sun and ring gears 2 and 4 , and otherwise render the entire transmission highly compact and light in weight.
  • each planet gear 6 may be coupled to its carrier pin 34 on the carrier 8 with a double row angular contact ball bearing or even with a cylindrical or spherical roller bearing. Also, more or less than four planet gears 6 may be used between the sun gear 2 and ring gear 4 .
  • EPICYCLIC GEAR SYSTEM A transmission X axis Y axes 2 sun gear 4 ring gear 6 planet gears 8 carrier 12 shaft 14 external teeth 18 internal teeth 22 external teeth 24 raceways 26 intervening surface 30 carrier flange 32 shaft 34 carrier pins 36 tapered hole 38 tapered surface 40 threaded ends 42 nut 46 inner race 48 end wall 50 sleeve 52 bore 54 weld 56 tapered raceway 58 separating member 60 thrust rib 62 mounting surface 64 rib ring 66 weld 70 tapered rollers 72 bearing 76 subassembly 78 subassembly

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Support Of The Bearing (AREA)
  • General Details Of Gearings (AREA)
US09/894,665 2001-06-28 2001-06-28 Epicyclic gear system Abandoned US20030008748A1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US09/894,665 US20030008748A1 (en) 2001-06-28 2001-06-28 Epicyclic gear system
JP2003508839A JP2004531680A (ja) 2001-06-28 2002-06-24 遊星ギア・システム
DE60205746T DE60205746T2 (de) 2001-06-28 2002-06-24 Planetengetriebe
EP02742292A EP1399682B1 (de) 2001-06-28 2002-06-24 Planetengetriebe
US10/481,708 US7056259B2 (en) 2001-06-28 2002-06-24 Epicyclic gear system
PCT/US2002/020069 WO2003002891A1 (en) 2001-06-28 2002-06-24 Epicyclic gear system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US09/894,665 US20030008748A1 (en) 2001-06-28 2001-06-28 Epicyclic gear system

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US10481708 Continuation-In-Part 2002-06-24

Publications (1)

Publication Number Publication Date
US20030008748A1 true US20030008748A1 (en) 2003-01-09

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ID=25403364

Family Applications (2)

Application Number Title Priority Date Filing Date
US09/894,665 Abandoned US20030008748A1 (en) 2001-06-28 2001-06-28 Epicyclic gear system
US10/481,708 Expired - Lifetime US7056259B2 (en) 2001-06-28 2002-06-24 Epicyclic gear system

Family Applications After (1)

Application Number Title Priority Date Filing Date
US10/481,708 Expired - Lifetime US7056259B2 (en) 2001-06-28 2002-06-24 Epicyclic gear system

Country Status (5)

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US (2) US20030008748A1 (de)
EP (1) EP1399682B1 (de)
JP (1) JP2004531680A (de)
DE (1) DE60205746T2 (de)
WO (1) WO2003002891A1 (de)

Cited By (30)

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WO2004067998A1 (en) * 2003-01-27 2004-08-12 The Timken Company Epicyclic gear systems
US20040171455A1 (en) * 2001-07-11 2004-09-02 Tillmann Korner Web unit
WO2005012761A1 (en) * 2003-07-29 2005-02-10 Pratt & Whitney Canada Corp. Compact epicyclic gear carrier
US20050075211A1 (en) * 2003-10-07 2005-04-07 Fox Gerald P. Epicyclic gear system
US20060213307A1 (en) * 2005-03-24 2006-09-28 Sumitomo Heavy Industries, Ltd. Power transmission device for driving robot wrist and power transmission device
WO2007016336A3 (en) * 2005-08-01 2007-05-24 Timken Co Epicyclic gear system with flexpins
US20090111639A1 (en) * 2005-11-12 2009-04-30 Mtu Aero Engines Gmbh Planetary Gear
US20100261571A1 (en) * 2008-04-17 2010-10-14 Kawasaki Jukogyo Kabushiki Kaisha Planetary reduction gear apparatus
CN102076992A (zh) * 2008-04-30 2011-05-25 迪姆肯公司 具有挠性销的行星齿轮系统
US8172717B2 (en) * 2011-06-08 2012-05-08 General Electric Company Compliant carrier wall for improved gearbox load sharing
US20120114488A1 (en) * 2008-05-20 2012-05-10 Urs Giger Wind power plant, transmission for a wind power plant and flexpin
EP2551540A1 (de) * 2011-07-28 2013-01-30 Schaeffler Technologies AG & Co. KG Zahnradeinrichtung für einen Getriebestrang
US20130178326A1 (en) * 2010-09-13 2013-07-11 Repower Systems Se Dismantling a gear mechanism of a wind power plant
WO2013158096A1 (en) * 2012-04-19 2013-10-24 Halliburton Energy Services Inc. Drilling assembly with high-speed motor gear system
US20140355920A1 (en) * 2009-07-09 2014-12-04 Aktiebolaget Skf Bearing assembly
DE102010019976B4 (de) * 2010-05-10 2016-10-13 Schaeffler Technologies AG & Co. KG Planetenrad und Planetentrieb
CN108626378A (zh) * 2017-03-17 2018-10-09 通用电气阿维奥有限责任公司 用于行星齿轮装置的行星支架和行星齿轮装置
US10330174B2 (en) * 2017-11-09 2019-06-25 General Electric Company Gear assembly for a wind turbine gearbox having a flexible pin shaft and carrier
DE102017223354A1 (de) * 2017-12-20 2019-06-27 Zf Friedrichshafen Ag Planetenträger für eine Getriebebaureihe
US10408304B2 (en) * 2017-02-07 2019-09-10 General Electric Company Gears having reduced roller element stresses and methods of manufacturing such gears
CN111022615A (zh) * 2019-12-23 2020-04-17 湘潭大学 一种消除行星轮轴向倾角的新型柔性销轴均载结构
US10662879B2 (en) 2017-08-08 2020-05-26 Pratt & Whitney Canada Corp. Epicyclic gear stage
US10682705B2 (en) 2017-11-09 2020-06-16 General Electric Company Gear assembly for a wind turbine gearbox having a flexible pin shaft and carrier
US10724625B2 (en) * 2018-02-20 2020-07-28 Sikorsky Aircraft Corporation Torsionally compliant geartrain carrier assembly
US10760677B2 (en) 2018-01-31 2020-09-01 Pratt & Whitney Canada Corp. Epicyclic gear train with balanced carrier stiffness
US10927944B2 (en) 2018-01-26 2021-02-23 Pratt & Whitney Canada Corp. Compact, twist controlled planet carrier and epicyclic gear train having same
US11015682B2 (en) * 2018-07-11 2021-05-25 Semplika Ltd Fixed-ratio planetary traction gear
CN113931977A (zh) * 2020-07-13 2022-01-14 住友重机械工业株式会社 挠曲啮合式齿轮装置
US11773963B2 (en) 2020-06-29 2023-10-03 General Electric Company Wind turbine gearbox carrier with integrated pin shafts and method of manufacturing same
US11865621B2 (en) 2018-06-25 2024-01-09 General Electric Company Additively manufactured journal bearing for a wind turbine gearbox

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EP1399682A1 (de) 2004-03-24
US7056259B2 (en) 2006-06-06
EP1399682B1 (de) 2005-08-24
JP2004531680A (ja) 2004-10-14

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