US20030236148A1 - Epicyclic drive with unified planet assemblies - Google Patents

Epicyclic drive with unified planet assemblies Download PDF

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Publication number
US20030236148A1
US20030236148A1 US10/177,492 US17749202A US2003236148A1 US 20030236148 A1 US20030236148 A1 US 20030236148A1 US 17749202 A US17749202 A US 17749202A US 2003236148 A1 US2003236148 A1 US 2003236148A1
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United States
Prior art keywords
raceways
pin
planet
gear
rib
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Abandoned
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US10/177,492
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English (en)
Inventor
Gerald Fox
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Timken Co
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Timken Co
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Filing date
Publication date
Application filed by Timken Co filed Critical Timken Co
Priority to US10/177,492 priority Critical patent/US20030236148A1/en
Assigned to THE TIMKEN COMPANY reassignment THE TIMKEN COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FOX, GERALD P.
Priority to US10/600,227 priority patent/US6770007B2/en
Priority to EP03739238A priority patent/EP1516134B1/en
Priority to AU2003245609A priority patent/AU2003245609A1/en
Priority to PCT/US2003/019533 priority patent/WO2004001256A1/en
Priority to JP2004516042A priority patent/JP2005530968A/ja
Priority to DE60306162T priority patent/DE60306162T2/de
Publication of US20030236148A1 publication Critical patent/US20030236148A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0479—Gears or bearings on 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members 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
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears

Definitions

  • This invention relates in general to epicyclic drives and, more particularly, to an epicyclic drive with unified planet assemblies and to the planet assemblies themselves.
  • the planet gears rotate in a carrier which itself may or may not rotate.
  • the carrier is of the straddle-mounted variety in which pins extend between two carrier plates, and the planet gears rotate on antifriction bearings carried by the pins.
  • each bearing contains two rows of rolling elements, such as tapered rollers or balls, with the rolling elements of the one row being mounted in opposition to the rolling elements of the other row. This enables the bearing for a planet gear to transfer axial loads in both directions, as well as radial loads, between the gear and its pin.
  • the presence of antifriction bearings brings with it demands for a considerable amount of precision.
  • the gears In the first place, the gears must be machined to within close tolerances to receive the outer races of the bearings and the same holds true for the pins over which the inner races fit.
  • the builder During the assembly of an epicyclic gear system the builder must insure that the bearings are adjusted properly. If the bearings are set with too much preload they may fail prematurely. On the other hand, too much end play in the bearings leaves the bearings with excessive internal clearances, and the gear may tilt on its axis and misalign with the sun and ring gears. This produces greater noise and wear in the gears.
  • the invention resides in a planet assembly including a planet gear, a pin extended through the planet gear, and a bearing located between pin and gear.
  • the invention also resides in an epicyclic drive including a carrier in which the planet assembly is installed.
  • the pin may be of a one or a two piece-type assembly.
  • the invention further resides in a process for assembling the planet assemblies.
  • FIG. 1 is a cross-sectional view taken along the axis of a epicyclic drive provided with planet assemblies constructed in accordance with and embodying the present invention
  • FIG. 2 is perspective view, partially broken away and in section, of the planet assembly for the epicyclic gear drive of FIG. 1;
  • FIG. 3 is a cross-sectional view taken along the axis of an epicyclic drive provided with modified planet assemblies.
  • FIG. 4 is a perspective view, partially broken away and in section, of a modified planet assembly.
  • an epicyclic drive A (FIG. 1), which is organized about an axis X, includes a sun gear 2 , a ring gear 4 located around the sun gear 2 , and planet gears 6 located between and engaged with the sun gear 2 and ring gear 4 .
  • the planet gears 6 rotate about axes Y that are located outwardly from, yet parallel to, the axis X.
  • the epicyclic drive A includes a carrier 8 which has its axis coinciding with the axis X, yet establishes the axes Y about which the planet gears 6 rotate.
  • a lubricating oil is discharged onto the gears 2 , 4 , and 6 , or else the ring gear 4 and planet gears 6 rotate through a sump containing oil.
  • Each planet gear 6 forms part of a separate planet assembly B which is assembled apart from the carrier 8 and later installed in the carrier 8 .
  • the carrier 8 includes a cage 12 having pockets 14 in which the planet assemblies B are located.
  • the cage 12 has an end member or portion 16 extending across the end or bottom of each pocket 14 and separators 18 that project axially from the end portion 16 through the spaces between adjacent planet assemblies B, thus forming the sides of the pockets 14 .
  • the end portion 16 has bores 20 centered on the pockets 14 , and the bores 20 lie along the axes Y.
  • the cage 12 has an end plate 22 which lies parallel to the end portion 16 of the cage 12 and is attached to the separators 18 of the cage 12 with cap screws 24 , thus closing the opposite ends of the pockets 14 .
  • the end plate 22 which forms another end member, contains bores 26 which align with the bores 20 in the end portion 16 of the cage 12 and thus also lie along the axes Y.
  • the carrier 12 includes a retaining plate 28 through which cap screws 30 pass and thread into the planet assemblies B to prevent the planet assemblies B from displacing axially in their pockets 14 .
  • the planet assemblies B are anchored in the carrier 8 at each pocket 14 , with the gears 6 being free to rotate in the pockets 14 of the cage 12 about the axes Y.
  • Each planet assembly B in addition to its planet gear 6 , includes (FIGS. 1 and 2) a unitary pin 34 which extends through the gear 6 and a bearing 36 that enables the gear 6 to rotate on its pin 34 without axial displacement or wobble.
  • Each planet assembly B also includes seals 38 which isolate its bearing 36 from the lubricating oil for the gears 2 , 4 and 6 .
  • the pin 34 has cylindrical mounting ends 40 and 42 which project form an enlarged intervening portion 44 that for the most part lies within the planet gear 6 .
  • the end 40 projects from the intervening portion 44 at a shoulder 46 and fits into one of the bores 20 in the end portion 16 of the cage 12 with an interference fit.
  • the cap screws 30 that pass through the retaining plate 28 thread into the mounting end 40 and draw the shoulder 46 against the end portion 16 of the cage 12 .
  • the other mounting end 42 projects from the intervening portion 44 at another shoulder 48 and fits into the aligned bore 26 in the end plate 22 , again with an interference fit.
  • the intervening portion 44 has two raceways 52 and 54 which are machined into it and taper downwardly to a separating rib 56 that lies between them.
  • the raceway 52 leads out to a thrust rib 58 which projects beyond the large end of the raceway 52 and is formed as an integral part of the pin 34 .
  • the thrust rib 58 leads out to the shoulder 46 .
  • the other raceway 54 leads out to a cylindrical seat 60 having a diameter less than the large end of the raceway 54 , there being a small shoulder 62 between the large end of the raceway 54 and the seat 60 .
  • the cylindrical seat 60 leads out to the shoulder 48 .
  • the pin 34 contains a lubrication channel 64 which extends axially from one of its ends and then radially, opening out of the pin 34 at its separating rib 56 .
  • the two raceways 52 and 54 and the thrust rib 56 form part of the bearing 36 .
  • the thrust rib 56 for the raceway 52 is formed integral with the pin 34
  • the thrust rib for the raceway 54 constitutes a separate rib ring 66 which is fitted to the cylindrical seat 60 with an interference fit and has radial positioning face 67 along which it bears against the small shoulder 62 on the pin 34 .
  • the rib ring 66 is secured to the pin 34 , preferably with a weld 68 . Since the rib ring 66 serves as a thrust rib, it has a rib face 70 which projects radially beyond the large end of the raceway 54 .
  • the rib ring 66 likewise forms part of the bearing 36 .
  • the bearing 36 includes two outer raceways 72 and 74 which encircle and are presented toward the two inner raceways 52 and 54 , respectively.
  • the outer raceways 72 and 74 taper downwardly to a separating surface 76 which surrounds the separating rib 56 on the pin 34 .
  • the outer raceway 72 leads out to and at its large end opens into a counterbore 78 in which the thrust rib 58 on the pin 34 is located.
  • the other outer raceway 74 leads out to and at its large end opens into a counterbore 80 in which the rib ring 66 is located.
  • the bearing 36 has tapered rollers 82 arranged in a row between the inner and outer raceways 52 and 72 and more tapered rollers 84 arranged in another row between the inner and outer raceways 54 and 74 .
  • the rollers 82 have their large ends against the integral thrust rib 58 , and indeed the thrust rib 58 prevents the rollers 82 from moving up the raceways 52 and 72 and out of the space between them.
  • the rollers 84 at their large ends bear against the face 70 of the rib ring 66 which prevents the rollers 84 from moving up the raceways 54 and 74 and out of the space between them.
  • the rollers 82 are on apex, meaning that the envelopes defined by the side faces of those rollers 82 have their apices at a common point along the axis Y. Of course, the envelopes formed by the two raceways 52 and 72 have their apices at the same point. Likewise, the rollers 84 are on apex, so the envelopes defined by their tapered side faces have their apices at common point on the axis Y, and the envelopes for the raceways 54 and 74 have their apices at the same point.
  • the on-apex design produces pure rolling contact between the rollers 82 and their raceways 52 and 72 and also between the rollers 84 and the raceways 54 and 74 .
  • the bearing 36 preferably does not contain cages, so each row has a full or maximum complement of rollers 82 and 84 .
  • a tribological coating consisting of nano crystalline metal carbide particles in an amorphous hydrocarbon matrix to retard metal adhesion.
  • the coatings may be applied by physical vapor deposition, chemical vapor deposition, or a combination of the two.
  • U.S. patent application Ser. No. 10/114,832, filed Apr. 2, 2002 for the invention of G. Doll and G. Fox entitled “Full Complement antifriction Bearing” discloses other tribological coatings which will suffice for the rollers 82 and 84 and procedures for applying them. That application is incorporated herein by reference.
  • the bearing 36 contains a lubricant, which is preferably a high performance grease.
  • the axial position of the rib ring 66 along the cylindrical seat 60 on the pin 34 controls the setting of the bearing 36 .
  • the bearing 36 is set to a condition of preload, although light preload. Even so, the initial setting of the bearing 36 should possess enough preload to enable the bearing 36 to remain in preload with beneficial loading on the rollers 82 and 84 during the operation of epicyclic drive A—operation which will normally cause the gear 6 to assume a temperature higher than the pin 34 owing to friction which develops between the teeth of the gear 6 and the teeth of the sun and ring gears 2 and 4 , respectively.
  • the seals 38 fit into the ends of the gear 6 and around the pin 34 to retain the lubricant, preferably a grease, in the bearing 36 and to exclude from the bearing 36 the oil that lubricates the teeth of the gears 2 , 4 , and to exclude 6 and debris as well.
  • One seal 38 fits into the counterbore 78 of the gear 6 and around the integral thrust rib 58 for the pin 34 about which the gear 6 rotates, thus creating a dynamic fluid barrier at that end of the gear 6 .
  • Another seal 38 fits into the other counterbore 80 and around the rib ring 66 , creating another dynamic fluid barrier at the opposite end of the gear 6 .
  • Each seal 38 has a stamped metal case, a shield, and an elastomeric seal element that is bonded to the case and bears against the shield along multiple lips.
  • the cases fit into the counterbores 78 and 80 , whereas the shields fit over the thrust rib 58 and rib ring 66 .
  • each planet assembly B the first row of tapered rollers 82 is placed around the inner raceway 52 on the pin 34 with their large ends against the integral thrust rib 58 .
  • the gear 6 is installed over the pin 34 until its raceway 72 seats against the rollers 82 .
  • the rollers 84 are inserted into the annular space between the raceways 54 and 74 —again the full complement of rollers 84 .
  • the rib ring 66 is pressed over the cylindrical seat 60 on the pin 34 and advanced toward the rollers 84 .
  • the gear 6 is rotated slowly relative to the pin 34 to insure that the rollers 82 seat properly along their raceways 52 and 72 and also along the thrust rib 58 and that the rollers 84 seat properly along their raceways 54 and 74 and also along the face 70 of the rib ring 66 .
  • the advance of the rib ring 66 continues until the rib ring 66 comes against the small shoulder 62 that lies between the large end of the inner raceway 54 and the cylindrical seat 60 .
  • the rib ring 66 controls the setting of the bearing 36 , and when it bears against the shoulder 62 , the bearing 36 should have the proper setting.
  • gauging measurements are made to determine the axial distance between the raceways 52 and 54 on the pin 34 , the axial distance between the raceways 72 and 74 in the planet gear 6 , and the diameters or body sizes of the rollers 82 and 84 . These dimensions having been determined, the correct position of the rib face 70 may be ascertained.
  • the rib ring 66 is ground along its positioning face 67 such that when the ring 66 is over the cylindrical seat 60 on the pin 34 and the positioning face 67 is against the shoulder 62 , the rib face 70 assumes the correct position.
  • the rib face 70 contact the large ends of the rollers 84 and positions the rollers 82 and 84 of both rows such that the bearing 36 possesses the correct setting—a setting of preload.
  • the rib ring 66 is secured to the pin 34 preferably by laser welding, thus producing the weld 68 .
  • the raceways 52 and 72 and likewise the raceways 54 and 74 may be coated with a high performance grease which also should be spread over other critical surfaces such as the face of the thrust rib 58 and the face 70 of the rib ring 66 , or the bearing 36 may be lubricated afterwards by forcing the grease through the lubrication channel 64 .
  • the preassembled planet assemblies B are then installed in the carrier 8 .
  • the mounting ends 40 for the pins 34 of the several planet assemblies B are pressed into the bores 20 in the end portions 16 of the cage 12 , so that the gears 6 of the planet assemblies B occupy the pockets 14 of the cage 12 .
  • the retaining plate 28 is installed against the end portion 16 of the cage 12 and secured to the pins 34 with the cap screws 30 .
  • the mounting ends 42 at the opposites ends of the pins 34 are pressed into the bores 26 in the end plate 22 .
  • the cap screws 24 are passed through the end plate 22 and threaded into the axially directed separators 18 on the cage 12 to attach the end plate 22 to the cage 12 .
  • the sun gear 2 is inserted through the end plate 22 of the carrier 8 and engaged with the planet gears 6 .
  • the ring gear 4 is passed over the carrier 12 and likewise engaged with the planet gears 6 .
  • the teeth of the gears 2 , 4 and 6 receive enough oil to keep them adequately lubricated, but the oil does not exist in enough volume to undergo significant churning. As a consequence, the oil remains relatively cool.
  • the bearings 36 derive their lubrication from the grease that is packed around the pins 34 and within the gears 6 , and the seals 38 isolate this grease from the oil that lubricates the teeth of the gears 2 , 4 , and 6 . Thus, the oil does not dilute and thin the grease, and the grease remains effective.
  • the bearings 36 Insure that the axes Y about which the planet gears 6 rotate remain reasonably unaltered. During operation the bearings 36 should not exhibit excessive internal clearances, since such clearances may alter the axes Y Hence, the planet gears 6 remain aligned with the gears 2 and 4 , and skewing attributable to bearing clearances is reduced, if not eliminated. This in turn reduces noise and extends the lives of the gears 2 , 4 , and 6 .
  • the planet assembly B is assembled with grease along the raceways 54 , 56 , 72 and 74 of its bearing 36 and likewise along the face of the thrust rib 58 and the face 70 of the rib ring 66 , the bearing 36 may from time to time require additional grease.
  • This grease is introduced through the lubrication channel 64 which at the mounting end 42 of the pin 34 may be provided with a grease fitting. Excessive grease purges through the seals 38 .
  • a purge channel may be incorporated into the pin 34 , it beginning at the separating rib 56 and opening out of the mounting end 42 .
  • a modified planet assembly C (FIGS. 3 and 4) utilizes the same planet gear 6 and seals 38 . Moreover, it contains a bearing 88 which is quite similar to the bearing 36 in that it includes outer raceways 72 and 74 machined into the gear 6 and tapered rollers 82 and 84 located along those raceways 72 and 74 . However, instead of a unitary pin 34 , the planet assembly C has a two-piece pin 90 including a sleeve 92 and a core 94 which extends through the sleeve 92 , there being a controlled clearance between the two.
  • the sleeve 92 forms the inner race of the bearing 88 and as such has the two raceways 52 and 54 , the integral thrust rib 58 at the large end of the raceway 52 , the cylindrical seat 60 extended beyond the large end of the other raceway 54 at a lesser diameter, and the separating rib 56 between the two raceways 52 and 54 . Moreover, the sleeve 92 has the rib ring 66 pressed over its cylindrical seat 60 .
  • the core 94 includes a cylindrical mounting end 96 on which one end face of the pin 90 is located and a spindle 98 which projects from the end 96 at a shoulder 100 .
  • the spindle 98 runs out to the other end face of the pin 90 .
  • the sleeve 92 fits over the spindle 98 , and at its integral thrust rib 58 abuts the shoulder 100 .
  • the spindle 98 projects beyond the opposite end of the sleeve 92 to form another cylindrical mounting end 102 on the pin 90 .
  • the planet assembly C is assembled much the same as the planet assembly B. However, the bearing 88 is assembled around the sleeve 92 of the pin 90 in the absence of the core 94 .
  • the two-piece construction of the pin 90 renders the planet assembly C suitable for use with a one-piece carrier 108 having spaced apart end portions 110 and 112 and separators 114 extended between the end portions 110 and 112 to divide the space between them into pockets 116 .
  • the end portion 110 contains bores 118 centered on its pockets 116 , while the end portion 112 has more bores 120 likewise centered on the pockets 116 .
  • the bores 118 and 120 at each pocket 116 align along the axis Y at the pocket 116 .
  • Fitted against the end portion 112 is a retaining plate 122 which is secured with cap screws 124 that pass through it.
  • the planet assembly C is inserted into one of the pockets 116 of the carrier 108 and the bore of its sleeve 92 is aligned with the bores 118 and 120 in the end portions 110 and 112 of the carrier 108 .
  • the core 94 with the mounting end 102 on its spindle 98 leading, is inserted through the bore 118 in the end portion 110 and the spindle 98 is advanced through the sleeve 92 until the shoulder 100 on the core 94 comes against the end of the sleeve 92 at the thrust rib 58 .
  • the mounting end 96 enters the bore 118 in the end portion 110 , whereas the mounting end 102 enters the bore 120 in the end portion 112 .
  • the retaining plate 122 is installed against the end portion 112 and the cap screws 124 are passed through it and threaded into the cores 94 of the pins 90 . This draws the opposite ends of the sleeve 92 against the inside face of the end portion 112 , effectively clamping the sleeve 92 between the shoulder 100 on the core 94 and the end portion 112 of the carrier 108 .
  • the planet assemblies B and C may be provided with other types of antifriction bearings, such as ball bearings, angular contact ball bearings, spherical roller bearings, cylindrical roller bearings, or needle bearings.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)
  • Rolling Contact Bearings (AREA)
US10/177,492 2002-06-21 2002-06-21 Epicyclic drive with unified planet assemblies Abandoned US20030236148A1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US10/177,492 US20030236148A1 (en) 2002-06-21 2002-06-21 Epicyclic drive with unified planet assemblies
US10/600,227 US6770007B2 (en) 2002-06-21 2003-06-20 Epicyclic drive with unified planet assemblies
EP03739238A EP1516134B1 (en) 2002-06-21 2003-06-20 Epicyclic drive with unified planet assemblies
AU2003245609A AU2003245609A1 (en) 2002-06-21 2003-06-20 Epicyclic drive with unified planet assemblies
PCT/US2003/019533 WO2004001256A1 (en) 2002-06-21 2003-06-20 Epicyclic drive with unified planet assemblies
JP2004516042A JP2005530968A (ja) 2002-06-21 2003-06-20 一体式遊星歯車アセンブリを有するエピサイクリック駆動装置
DE60306162T DE60306162T2 (de) 2002-06-21 2003-06-20 Zykloidengetriebe mit einheitlichen planetenanordnungen

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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
US20120003096A1 (en) * 2010-02-12 2012-01-05 Mitsubishi Heavy Industries, Ltd. Gear box for wind turbine generator and wind turbine generator
US20120208669A1 (en) * 2010-02-12 2012-08-16 Mitsubishi Heavy Industries, Ltd. Gear box for wind turbine generator and wind turbine generator
WO2015090789A1 (de) * 2013-12-18 2015-06-25 Zf Friedrichshafen Ag Fixierung und/oder verspannung eines planetenbolzens
WO2016016110A1 (de) * 2014-07-30 2016-02-04 Aktiebolaget Skf Lageranordnung mit vorspannung
US20160377165A1 (en) * 2015-06-24 2016-12-29 United Technologies Corporation Lubricant delivery system for planetary fan drive gear system
CN107013568A (zh) * 2015-10-27 2017-08-04 斯凯孚公司 预紧的轴承组合单元
CN107630981A (zh) * 2016-07-19 2018-01-26 株式会社神崎高级工机制作所 行星齿轮机构
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US20190162293A1 (en) * 2017-11-24 2019-05-30 Rolls-Royce Deutschland Ltd & Co Kg Planetary gearing and planet pin for a planetary gearing
EP3091255B1 (de) 2015-05-07 2019-11-06 Flender GmbH Planetengetriebe
US10767755B2 (en) 2017-11-24 2020-09-08 Rolls-Royce Deutschland Ltd & Co Kg Planetary gearing and planet pin for a planetary gearing
US11085523B2 (en) 2017-11-24 2021-08-10 Rolls-Royce Deutschland Ltd & Co Kg Planetary gearing
CN116441923A (zh) * 2023-06-12 2023-07-18 盛瑞传动股份有限公司 行星轮组件装配方法
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EP4184034A4 (en) * 2020-07-29 2023-12-27 Midea Group Co., Ltd. INTERNALLY GEARED PLANETARY GEAR DEVICE AND ACTUATOR
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Cited By (32)

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Publication number Priority date Publication date Assignee Title
US20070068302A1 (en) * 2005-08-23 2007-03-29 O'leary Michael F Hydraulic active damping system for gears and method
EP1837535A1 (de) * 2006-03-22 2007-09-26 Ab Skf Maschinenteil
EP2045476A3 (de) * 2007-09-19 2012-06-27 Ab Skf Lager
EP2045476A2 (de) 2007-09-19 2009-04-08 Ab Skf Lager
US20090163316A1 (en) * 2007-12-19 2009-06-25 Hansen Transmissions International, Naamloze Vennootschap Planetary type gear unit comprising a planet carrier with a planet bogie plate
US8246505B2 (en) * 2007-12-19 2012-08-21 Zf Wind Power Antwerpen N.V. Planetary type gear unit comprising a planet carrier with a planet bogie plate
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
US20120003096A1 (en) * 2010-02-12 2012-01-05 Mitsubishi Heavy Industries, Ltd. Gear box for wind turbine generator and wind turbine generator
US20120208669A1 (en) * 2010-02-12 2012-08-16 Mitsubishi Heavy Industries, Ltd. Gear box for wind turbine generator and wind turbine generator
CN102792018A (zh) * 2010-02-12 2012-11-21 三菱重工业株式会社 用于的风力涡轮发电机齿轮箱和风力涡轮发电机
US8657578B2 (en) * 2010-02-12 2014-02-25 Mitsubishi Heavy Industries, Ltd. Gear box for wind turbine generator and wind turbine generator
WO2015090789A1 (de) * 2013-12-18 2015-06-25 Zf Friedrichshafen Ag Fixierung und/oder verspannung eines planetenbolzens
CN105849441A (zh) * 2013-12-18 2016-08-10 Zf 腓德烈斯哈芬股份公司 对行星销的固定和/或压紧
US10859119B2 (en) 2014-07-30 2020-12-08 Aktiebolaget Skf Bearing assembly with preload
DE102014214999B4 (de) * 2014-07-30 2021-06-24 Aktiebolaget Skf Lageranordnung mit Vorspannung
WO2016016110A1 (de) * 2014-07-30 2016-02-04 Aktiebolaget Skf Lageranordnung mit vorspannung
EP3091255B1 (de) 2015-05-07 2019-11-06 Flender GmbH Planetengetriebe
US10634237B2 (en) * 2015-06-24 2020-04-28 United Technologies Corporation Lubricant delivery system for planetary fan drive gear system
US20160377165A1 (en) * 2015-06-24 2016-12-29 United Technologies Corporation Lubricant delivery system for planetary fan drive gear system
US10234018B2 (en) * 2015-10-19 2019-03-19 General Electric Company Planet gearbox with cylindrical roller bearing with under race lube scheme
CN107013568A (zh) * 2015-10-27 2017-08-04 斯凯孚公司 预紧的轴承组合单元
CN107630981A (zh) * 2016-07-19 2018-01-26 株式会社神崎高级工机制作所 行星齿轮机构
US10054216B2 (en) * 2016-07-26 2018-08-21 Caterpillar Inc. Assembly guide for sleeved planetary carriers
US12117075B2 (en) * 2017-08-14 2024-10-15 General Electric Company Power gearbox gear arrangement
US20230304573A1 (en) * 2017-08-14 2023-09-28 General Electric Company Power gearbox gear arrangement
US10767755B2 (en) 2017-11-24 2020-09-08 Rolls-Royce Deutschland Ltd & Co Kg Planetary gearing and planet pin for a planetary gearing
US11085523B2 (en) 2017-11-24 2021-08-10 Rolls-Royce Deutschland Ltd & Co Kg Planetary gearing
US10816087B2 (en) * 2017-11-24 2020-10-27 Rolls-Royce Deutschland Ltd & Co Kg Planetary gearing and planet pin for a planetary gearing
US20190162293A1 (en) * 2017-11-24 2019-05-30 Rolls-Royce Deutschland Ltd & Co Kg Planetary gearing and planet pin for a planetary gearing
EP4184034A4 (en) * 2020-07-29 2023-12-27 Midea Group Co., Ltd. INTERNALLY GEARED PLANETARY GEAR DEVICE AND ACTUATOR
US20240116618A1 (en) * 2022-10-05 2024-04-11 Yamaha Hatsudoki Kabushiki Kaisha Marine propulsion device
CN116441923A (zh) * 2023-06-12 2023-07-18 盛瑞传动股份有限公司 行星轮组件装配方法

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DE60306162T2 (de) 2007-04-19
EP1516134B1 (en) 2006-06-14
AU2003245609A1 (en) 2004-01-06
US20040038771A1 (en) 2004-02-26
JP2005530968A (ja) 2005-10-13
WO2004001256B1 (en) 2004-03-04
EP1516134A1 (en) 2005-03-23
US6770007B2 (en) 2004-08-03
DE60306162D1 (de) 2006-07-27
WO2004001256A1 (en) 2003-12-31

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