CN100443779C - Big load planetary gear bearing support device - Google Patents

Big load planetary gear bearing support device Download PDF

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Publication number
CN100443779C
CN100443779C CNB2006100950391A CN200610095039A CN100443779C CN 100443779 C CN100443779 C CN 100443779C CN B2006100950391 A CNB2006100950391 A CN B2006100950391A CN 200610095039 A CN200610095039 A CN 200610095039A CN 100443779 C CN100443779 C CN 100443779C
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China
Prior art keywords
bearing
roller bearing
ring
planet
planetary gear
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CNB2006100950391A
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Chinese (zh)
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CN1908470A (en
Inventor
杜木信
颜克君
刘阳
赵俊渝
曾明
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Chongqing Gearbox Co Ltd
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Chongqing Gearbox Co Ltd
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Priority to CNB2006100950391A priority Critical patent/CN100443779C/en
Publication of CN1908470A publication Critical patent/CN1908470A/en
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Publication of CN100443779C publication Critical patent/CN100443779C/en
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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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row of rollers
    • 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
    • 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

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  • General Details Of Gearings (AREA)
  • Support Of The Bearing (AREA)
  • Retarders (AREA)

Abstract

The invention relates to a bearing support of large-load planet gear, belonging to the planet gear transmission technique, wherein it comprises a planet support (1) and a planet axle (2); the axle (2) is fixed on the support (1); two bearings are parallel arranged along the axle (2) while one bearing is spherical roller bearing (3) and another one is circular roller bearing (4). The invention has high dynamic load ability, better working reliability, simple installment, long service life and lower cost, that 50% reduced cost on bearing.

Description

The bearing support assembly of big load planetary gear
Technical field
The invention belongs to planetary pinion drive technology field, specifically, relate to planetary bearing support assembly.
Background technique
In the gear transmission technology field, hard flank of tooth planetary type gear transmission unit has characteristics such as speed ratio is big, volume is little, bearing capacity height, be used widely in essential industry departments such as wind-power electricity generation, metallurgy, building materials, wind-power electricity generation industry particularly, the main step-up gear of the whole world 70% wind power generating set all adopts the planetary pinion transmission.Along with the develop rapidly of wind generating technology in the world, the transmission power of planetary type gear transmission unit is increasing, reached 5 megawatts at present, and reliability requirement is higher.Blower fan planetary type gear transmission unit with one 1.5 megawatt is an example, if break down, needs it is hung oneself from 70 meters high pylons, again it is lifted up after fixing, therefore expense is very high, requires the planetary type gear transmission unit of blower fan in a single day to devote oneself to work after the operation, and big fault does not have.Through facts have proved, the mechanical failure majority of wind power generating set planetary type gear transmission unit is from the premature failure of planetary pinion spring bearing, for this reason, the various countries technician is according to planetary pinion job requirement heavy duty, shock resistance, long lifetime and lightweight characteristics have designed multiple planetary bearing support assembly, common mainly contains three kinds: a kind of is to be arranged side by side two single-row cylinder full type roller bearings on planet axis, the basic dynamic load rating height of single-row cylinder full type roller bearing, this structural type is the most popular at present, generally believe the most reliable, in being fit to, the large planetary transmission device, but aim at fan design and produce because single-row cylinder full type roller bearing is a German INA company, complex process, supply falls short of demand, costs an arm and a leg; Another kind is to be arranged side by side two spheric roller bearings on planet axis, the basic dynamic load rating of spheric roller bearing is the highest, price is minimum, the designing and calculating life-span is the highest, but owing to add inevitable error in man-hour, the Internal and external cycle end face does not line up usually, though making the Internal and external cycle exterior edge face during assembling has alignd, but make the dislocation that contacts between inside and outside raceway and the roller, thereby cause actual life and designing and calculating life-span too wide in the gap, reliability is undesirable, and this structure is eliminated by external big wind-powered electricity generation manufacturing company; The third is to be arranged side by side two single-row tapered roller bearings on planet axis, and the basic dynamic load rating of single-row tapered roller bearing is higher, and this structure is fit to small-sized planetary driving device, and reliability is better, but the bearing price is higher, and assembling is adjusted inconvenient.
Summary of the invention
It is strong that the problem to be solved in the present invention provides a kind of not only dynamic load bearing capacity, and reliable operation, assembles the bearing support assembly of easy to adjust and the big load planetary gear that cost is low.
For solving the problems of the technologies described above, the bearing support assembly of big load planetary gear of the present invention, have planet carrier and planet axis, planet axis is fixedly mounted on the planet carrier, on planet axis, axially be provided with two bearings side by side, in two bearings on the planet axis, one is spheric roller bearing, and another is the annulus roller bearing.
Because two kinds of employings are dissimilar, but spheric roller bearing that boundary dimension is the same and annulus roller bearing bear planetary working load, their basic dynamic load rating is the highest in all annulars bearing with rolling contact under the identical appearance size condition, it is the strongest bearing of bearing capacity, therefore help improving the life-span and the functional reliability of planetary pinion spring bearing, annulus roller bearing and spheric roller bearing manufacturing process are simple, and cost is low.Spheric roller bearing is being born 50% radial force and less axial force in the present invention, and bears the function of axially locating, because its Internal and external cycle can axial float, can bring into play its potential bearing capacity reliably; And the annulus roller bearing is being born other 50% radial force, and it not only possesses spheric roller bearing self-aligning and the strong characteristic of bearing capacity, but also has the function that bearing capacity takes place not influence after the displacement to axial Internal and external cycle." Internal and external cycle is the placement property to axial " of annulus roller bearing plays two key effects in the present invention: the first does not influence the proper functioning and the characteristic performance of spheric roller bearing, its two the radial clearance of two kinds of bearings can be adjusted to the same, improved the problem of two bearings and planetary pinion unbalance loading, thus working life of having improved bearing and gear.
Effect of the present invention is: not only the dynamic load bearing capacity is strong, and functional reliability is good, install easy to adjust, in having solved, the high-power planetary pinion heavy load transmission condition lower supporting bearing life-span is short, the problem that rate of fault is high, the bearing purchase cost has descended at least 50%.
Description of drawings
Below in conjunction with the drawings and specific embodiments the present invention is described in further detail.
Fig. 1 is a structural representation of the present invention.
Embodiment
As shown in Figure 1, the bearing support assembly of big load planetary gear of the present invention has planet carrier 1 and planet axis 2, planet axis 2 is fixedly mounted on the planet carrier 1, axially be provided with two bearings on planet axis 2 side by side, one of them is a spheric roller bearing 3, and another is an annulus roller bearing 4.The pure radial load ability of spheric roller bearing 3 is strong, can bear and axially reach united load, bigger angular error is arranged during permission work, can the initial angle error of shaft axis be compensated, be used as one of planetary spring bearing with it, therefore can play the effect of axial float self-aligning; The pure radial load ability of annulus roller bearing 4 is stronger, angular error during same permission work, key is its good rigidity, after Internal and external cycle axially misplaces, contacting between inside and outside raceway and the roller is still fine, therefore can give full play to the axially locating of spheric roller bearing 3 and the function of self-aligning at this with it.Number in the figure 9 is a planetary pinion.
Fig. 1 illustrates between the inner ring of spheric roller bearing 3 and annulus roller bearing 4 supply ring 5 is installed, and distance ring 6 is installed between the outer ring; Axial limiting is carried out by back-up ring 7 and lining ring 8 respectively in the outside of spheric roller bearing 3 and annulus roller bearing 4 Internal and external cycles.Supply ring 5 and the axially locating of lining ring 8 realizations to spheric roller bearing 3 and annulus roller bearing 4 inner rings, distance ring 6 and the axially locating of back-up ring 7 realizations to spheric roller bearing 3 and annulus roller bearing 4 outer rings.When planetary pinion was worked, spheric roller bearing 4 was born about 50% radial load and very little axial force and is brought into play the axially locating effect.The outer ring of spheric roller bearing 4 can move axially self-aligning under the radial force effect, make roller and the raceway camber line centering of coincideing, and spherical bearing roller and raceway will be in normal contact condition operations; Annulus roller bearing 4 is also born about 50% radial load, its outer ring in service can produce with the outer ring of spheric roller bearing 3 and smallly move axially and do not influence bearing capacity, because barrel shaped roller can be adjusted automatically, make the raceway Line of contact remain on operation under the kilter.Characteristics of the present invention are: first adopts two different types of bearing configurations in the planetary pinion spring bearing, select for use to greatest extent and have the heavy-duty bearing of high basic dynamic load rating, and for this class bearing is brought into play separately as well as possiblely speciality provides essential operating conditions, thereby improved the bearing capacity and the reliability of planetary pinion spring bearing most possibly.

Claims (2)

1, a kind of bearing support assembly of big load planetary gear, comprise planet carrier (1) and planet axis (2), planet axis (2) is fixedly mounted on the planet carrier (1), on planet axis (2), axially be provided with two bearings side by side, it is characterized in that: in two bearings on the described planet axis (2), one is spheric roller bearing (3), and another is annulus roller bearing (4).
2, the bearing support assembly of big load planetary gear according to claim 1 is characterized in that: between the inner ring of described spheric roller bearing (3) and annulus roller bearing (4) supply ring (5) is installed, distance ring (6) is installed between the outer ring; The outer end of spheric roller bearing (4) and annulus roller bearing (5) inner ring is by lining ring (7) axial limiting, and the outer end of outer ring is by back-up ring (8) axial limiting.
CNB2006100950391A 2006-08-17 2006-08-17 Big load planetary gear bearing support device Active CN100443779C (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CNB2006100950391A CN100443779C (en) 2006-08-17 2006-08-17 Big load planetary gear bearing support device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CNB2006100950391A CN100443779C (en) 2006-08-17 2006-08-17 Big load planetary gear bearing support device

Publications (2)

Publication Number Publication Date
CN1908470A CN1908470A (en) 2007-02-07
CN100443779C true CN100443779C (en) 2008-12-17

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8062165B2 (en) * 2008-01-25 2011-11-22 GM Global Technology Operations LLC Bearing assembly for planetary gear pinion
JP5345048B2 (en) * 2009-12-15 2013-11-20 三菱重工業株式会社 Wind power transmission and wind power generator
CN101865279A (en) * 2010-06-02 2010-10-20 重庆齿轮箱有限责任公司 Mechanism for balancing load of planetary gear by flexible pin shaft
CN105370869A (en) * 2015-11-24 2016-03-02 徐州科源液压股份有限公司 Axially-adjusted combined planet carrier
CN106151392A (en) * 2016-07-20 2016-11-23 浙江双环传动机械股份有限公司 A kind of load-balancing device of herringbone bear Gear Planet Transmission

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH561870A5 (en) * 1972-12-08 1975-05-15 Klaue Hermann Toothed wheel gearing with power branching - has helical gear wheel and two drive rims, one comprising gear rim the other a helical rim
DE2910602A1 (en) * 1979-03-17 1980-10-02 Thyssen Industrie Epicyclic gear planet wheel carrier - is linked to input shaft from vehicle drive by claw coupling
CN2268149Y (en) * 1996-10-14 1997-11-19 周福尧 Internal-toothed differential mechanism
US5800072A (en) * 1996-03-29 1998-09-01 Skf Gmbh Bearing assembly
DE19857914A1 (en) * 1998-12-16 2000-07-06 Jahnel Kestermann Getriebewerk Gears for wind power installation with gear and shaft coupling planetary and spur gear stages of one piece construction
US6814684B2 (en) * 2000-12-22 2004-11-09 Zf Friedrichshafen Ag Planetary gear
US6872049B2 (en) * 2001-04-02 2005-03-29 Vestas Wind Systems A/S Wind turbine comprising a planetary gear
CN200940676Y (en) * 2006-08-17 2007-08-29 重庆齿轮箱有限责任公司 Planet gear bearing support device

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH561870A5 (en) * 1972-12-08 1975-05-15 Klaue Hermann Toothed wheel gearing with power branching - has helical gear wheel and two drive rims, one comprising gear rim the other a helical rim
DE2910602A1 (en) * 1979-03-17 1980-10-02 Thyssen Industrie Epicyclic gear planet wheel carrier - is linked to input shaft from vehicle drive by claw coupling
US5800072A (en) * 1996-03-29 1998-09-01 Skf Gmbh Bearing assembly
CN2268149Y (en) * 1996-10-14 1997-11-19 周福尧 Internal-toothed differential mechanism
DE19857914A1 (en) * 1998-12-16 2000-07-06 Jahnel Kestermann Getriebewerk Gears for wind power installation with gear and shaft coupling planetary and spur gear stages of one piece construction
US6814684B2 (en) * 2000-12-22 2004-11-09 Zf Friedrichshafen Ag Planetary gear
US6872049B2 (en) * 2001-04-02 2005-03-29 Vestas Wind Systems A/S Wind turbine comprising a planetary gear
CN200940676Y (en) * 2006-08-17 2007-08-29 重庆齿轮箱有限责任公司 Planet gear bearing support device

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
航空游星齿轮轴承受力和变形分析. 余战国，周旭东，曲廷敏，蒋新力，梁英.轴承，第1期. 2006
航空游星齿轮轴承受力和变形分析. 余战国，周旭东，曲廷敏，蒋新力，梁英.轴承，第1期. 2006 *

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