CN101725631B - Slewing bearing - Google Patents

Slewing bearing Download PDF

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Publication number
CN101725631B
CN101725631B CN2009102413243A CN200910241324A CN101725631B CN 101725631 B CN101725631 B CN 101725631B CN 2009102413243 A CN2009102413243 A CN 2009102413243A CN 200910241324 A CN200910241324 A CN 200910241324A CN 101725631 B CN101725631 B CN 101725631B
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CN
China
Prior art keywords
tooth
ring
gear
raceway
floating bearing
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Application number
CN2009102413243A
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Chinese (zh)
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CN101725631A (en
Inventor
蒋建军
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.)
Suote Transmission Equipment Co Ltd
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Suote Transmission Equipment Co Ltd
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 Suote Transmission Equipment Co Ltd filed Critical Suote Transmission Equipment Co Ltd
Priority to CN2009102413243A priority Critical patent/CN101725631B/en
Priority to PCT/CN2010/070737 priority patent/WO2011066732A1/en
Publication of CN101725631A publication Critical patent/CN101725631A/en
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Publication of CN101725631B publication Critical patent/CN101725631B/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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • 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
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • 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
    • 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
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/74—Adjusting of angle of incidence or attack of rotating blades by turning around an axis perpendicular the rotor centre line
    • 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
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/79—Bearing, support or actuation arrangements therefor
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • 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

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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)
  • Rolling Contact Bearings (AREA)

Abstract

The invention relates to a slewing bearing used for fan variation paddle, comprising an inner ring, an outer ring and a plurality of steel balls and a keeper, wherein the steel balls and the keeper are arranged between the raceway of the inner ring and the raceway of the outer ring. The invention is characterized in that one of the inner ring and the outer ring is a gear ring which is partial gear; preferentially, the partial gear at least comprises a 90-degree effective gear region. The slewing bearing of the invention improves gear efficiency and gear surface quenching efficiency, and decreases the machining residual stress and the gear ring deformation, thus greatly improving the slewing bearing capacity of variation paddle.

Description

Pivoting support
Technical field
The present invention relates to field of bearings, relate in particular to the floating bearing that is used for blower variable-pitch.
Background technique
Wind-driven generator pitching slewing support is generally internal gear type at present, and the whole circle of ring gear all has tooth.In fact, wind-driven generator is when becoming oar, and general maximum angle of swing has only 90 °.That is to say that 1/4 the tooth of only having an appointment is effective tooth, all the other teeth of about 3/4 are no.By this mode of the whole circle system tooth of present pitching slewing support, can cause the significant wastage of processing, waste great amount of labor, electric power, device resource.In addition, between pitching slewing support steel ball and the raceway slight interference assembling, the raceway distortion is most important to the pivoting support quality influence.Because whole system teeth, particularly during mill teeth, amount of machining is excessive in the short time, causes residual stress excessive, and the release of final residual stress can cause the gear ring distortion very big, has a strong impact on the performance of pitching slewing support.Therefore, need a kind of new design method in a hurry, reduce unnecessary processing as far as possible, improve the work efficiency of pivoting support when guaranteeing the pitching slewing support quality.
Summary of the invention
The object of the present invention is to provide a kind of wind-driven generator pitching slewing support, it can overcome shortcomings such as the work efficiency that produces when gear ring is all made tooth is low, residual stress is big.
Technological scheme provided by the present invention is: a kind of floating bearing that is used for blower variable-pitch; Comprise inner ring, outer ring, be installed in a plurality of steel balls and the retainer between said inner ring and the said outer ring between the raceway of raceway and said outer ring of said inner ring; It is characterized in that one in said inner ring and the outer ring is that gear ring and said gear ring are made tooth for part.Preferably, said part system tooth comprises effective tooth zone of 90 ° at least.Because wind-driven generator is when becoming oar; General maximum angle of swing has only 90 °; Therefore the part system tooth that has comprised effective tooth zone of 90 ° has just satisfied the needs that become oar; Thereby overcome shortcomings such as the work efficiency that produces when gear ring is all made tooth is low, residual stress is big, and have advantages such as compact structure, work efficiency is high, residual stress is little.
According to a preferred embodiment, the scope of said part system tooth is between 90 °～270 °.That is to say, consider the needs of assembling transition or other needs, system tooth zone can be expanded to both sides from effective tooth zone respectively, and the zone of expansion is not more than 90 ° respectively from both sides.More preferably, the scope of said part system tooth is between 90 °～120 °.
According to a preferred embodiment, said effective tooth zone begins from the position of an angle of the soft band of quenching of the raceway of the said gear ring of distance, and a said angle is an angle value of taking between 30 °～150 °.More preferably, said effective tooth zone begins from 75 ° position of the soft band of quenching of the raceway of the said gear ring of distance to finish to 165 ° position of the soft band of quenching of the raceway of the said gear ring of distance.According to an alternative embodiment, said effective tooth zone begins at a distance of 75 ° position from 180 ° position with the soft band of quenching of the raceway of the said gear ring of distance.Do not have the gear ring of the soft band that quenches for raceway, effectively the tooth zone can be at an arbitrary position.
According to a preferred embodiment, the tooth in said effective tooth zone is complete tooth.
According to a preferred embodiment, quench in said at least effective tooth zone.When being the tooth quenching, can be only to becoming the effective toothed portion quenching of oar or considering other demand, the quenching zone can be expanded to both sides, and spreading range is looked use condition and is decided.
According to a preferred embodiment, said part system tooth can be realized through gear shaping or finish-milling tooth.
The advantage of the relative existing technology of the present invention is: system tooth efficient improves 2 times; Flank of tooth quenching efficiency improves 3.5 times; Machining stress significantly reduces; The gear ring distortion significantly reduces; The pitching slewing support performance significantly improves.
Description of drawings
Below in conjunction with accompanying drawing and embodiment the present invention is further specified:
The pivoting support general structure schematic representation of Fig. 1 blower variable-pitch;
Fig. 2 is according to the gear ring tooth distribution schematic diagram of first embodiment;
Fig. 3 is according to the gear ring tooth distribution schematic diagram of second embodiment.
Embodiment
A kind of blower variable-pitch has been shown among Fig. 1 has used pivoting support, it comprises outer ring 1, steel ball 2, retainer 3, inner ring 4, seal ring 5 etc.Steel ball 2 is installed between the raceway of raceway and inner ring 4 of outer ring 1, and retainer 3 is installed between outer ring 1 and the inner ring 4, and outer ring 1 can relatively rotate 5 oil sealings of seal ring and dustproof effect with inner ring 4.
One in outer ring 1 and the inner ring 4 be gear ring, and to go out inner ring 4 be gear ring to example among Fig. 1.
Inner ring 4 (gear ring) is only made the part tooth, and this part tooth comprises and the corresponding effectively tooth of the maximum angle of swing of wind-driven generator when becoming oar zone at least.When the maximum angle of swing of wind-driven generator was 90 °, this part tooth comprised effective tooth zone of 90 °.System tooth zone can be expanded to both sides from effective tooth zone respectively, and the zone of expansion is not more than 90 ° respectively from both sides, promptly makes the tooth scope between 90 °～270 ° scopes, preferably between 90 °～120 ° scopes.
Do not have the gear ring of the soft band that quenches for raceway, effectively the tooth zone can be at an arbitrary position.
And for according to Fig. 2, the gear ring of having shown in Fig. 3 " the soft band of quenching ", effectively the distributing position in tooth zone is then different.
Fig. 2 shows the gear ring tooth distribution schematic diagram according to first embodiment, and wherein the raceway of inner ring 4 (gear ring) has the soft band S that quenches.Certainly, in unshowned mode of execution, the raceway of inner ring 4 (gear ring) can have two soft bands that quench.Two when quenching soft band, two soft bands can be distributed in same position, also can 180 ° of symmetrical distributions.
Its effective tooth zone begins from the position of an angle of the soft band of quenching of the raceway of the said gear ring of distance when becoming oar, and a said angle is an angle value of taking between 30 °～150 °.In the embodiment shown in this Fig. 2, effectively the tooth zone is part in 90 ° of scopes that begin from distance " soft band " 75 ° of positions to finish to 165 ° of positions.
Fig. 3 shows the gear ring tooth distribution schematic diagram according to second embodiment.In according to the embodiment shown in Fig. 3, the initial position that becomes the effective toothed portion of oar is into beginning at a distance of 75 ° position with the position that apart from soft band S is 180 °.
When the system tooth, requiring the tooth in these 90 ° of scopes is complete tooth.Consider the needs of assembling transition or other needs, system tooth mode can be taked gear shaping mode and finish-milling tooth mode.When adopting the gear shaping mode, system toothed portion two ends allow 3 non-complete teeth respectively.The tooth of inner ring 4 (gear ring) is hardenable, also can not quench.During quenching, consider other demand to becoming the effective toothed portion of oar (in 90 ° of scopes) quenching for general, the quenching zone can be expanded to both sides, and spreading range is looked use condition and decided.
Reference identification
1 outer ring
2 steel balls
3 retainers
4 inner rings
5 seal rings
The soft band of S

Claims (10)

1. floating bearing that is used for blower variable-pitch; Comprise a plurality of steel balls (2) and the retainer (3) between the said outer ring of said inner ring (4) (1) between the raceway of inner ring (4), outer ring (1), the raceway that is installed in said inner ring (4) and said outer ring (1); It is characterized in that an internal tooth for gear ring and said gear ring in said inner ring (4) and said outer ring (1) is made tooth for part.
2. floating bearing according to claim 1 is characterized in that, said part system tooth comprises effective tooth zone of 90 ° at least.
3. floating bearing according to claim 2 is characterized in that, the scope of said part system tooth is between 90 °～270 °.
4. floating bearing according to claim 3 is characterized in that, the scope of said part system tooth is between 90 °～120 °.
5. according to each described floating bearing among the claim 2-4; It is characterized in that; Said effective tooth zone begins from the position of an angle of the soft band of quenching of the raceway of the said gear ring of distance, and a said angle is an angle value of taking between 30 °～150 °.
6. floating bearing according to claim 5 is characterized in that, said effective tooth zone begins from 75 ° the position of the soft band of quenching of the raceway of the said gear ring of distance to finish to 165 ° position of the soft band of quenching of the raceway of the said gear ring of distance.
7. according to each described floating bearing among the claim 2-4, it is characterized in that said effective tooth zone begins at a distance of 75 ° position from 180 ° position with the soft band of quenching of the raceway of the said gear ring of distance.
8. according to each described floating bearing among the claim 2-4, it is characterized in that the tooth in said effective tooth zone is complete tooth.
9. according to each described floating bearing among the claim 2-4, it is characterized in that, quenched in said effective tooth zone at least.
10. according to each described floating bearing among the claim 2-4, it is characterized in that said part system tooth can be realized through gear shaping or finish-milling tooth.
CN2009102413243A 2009-12-04 2009-12-04 Slewing bearing Active CN101725631B (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN2009102413243A CN101725631B (en) 2009-12-04 2009-12-04 Slewing bearing
PCT/CN2010/070737 WO2011066732A1 (en) 2009-12-04 2010-02-24 Rotating bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN2009102413243A CN101725631B (en) 2009-12-04 2009-12-04 Slewing bearing

Publications (2)

Publication Number Publication Date
CN101725631A CN101725631A (en) 2010-06-09
CN101725631B true CN101725631B (en) 2012-06-20

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WO (1) WO2011066732A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2997159B1 (en) * 2012-10-22 2016-11-25 Skf Ab BEARING BEARING, IN PARTICULAR FOR PROPELLER OF SHIPS OR FOR WIND TURBINES
US10563748B2 (en) 2013-09-18 2020-02-18 Kinematics, Llc Slew drive gearbox with torque tube

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1117841A (en) * 1965-02-08 1968-06-26 Nasa Method of improving the reliability of a rolling element system
CN1043439C (en) * 1992-03-20 1999-05-19 方祖彭 planetary transmission
CN200993158Y (en) * 2006-12-22 2007-12-19 洛阳轴研科技股份有限公司 Special bearing for 750KW wind motor yawing mechanism
CN101307750A (en) * 2007-05-15 2008-11-19 罗虹 Wind-driven generator group wheel box
CN201187526Y (en) * 2008-01-02 2009-01-28 代安铭 Wind electric 1.25-2.0 MW paddle-changing double-row ball bearing developed by ultimate design special technique

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7331761B2 (en) * 2005-11-10 2008-02-19 Kaydon Corporation Wind turbine pitch bearing and method
DE102007041508A1 (en) * 2007-08-31 2009-03-05 Schaeffler Kg Rotor bearing for a wind turbine
DE102007062056A1 (en) * 2007-12-21 2009-06-25 Schaeffler Kg Rolling bearing with split outer ring with radial fixation
CN201306384Y (en) * 2008-09-26 2009-09-09 上海联合滚动轴承有限公司 Retainer on pitch bearing of wind-driven generator

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1117841A (en) * 1965-02-08 1968-06-26 Nasa Method of improving the reliability of a rolling element system
CN1043439C (en) * 1992-03-20 1999-05-19 方祖彭 planetary transmission
CN200993158Y (en) * 2006-12-22 2007-12-19 洛阳轴研科技股份有限公司 Special bearing for 750KW wind motor yawing mechanism
CN101307750A (en) * 2007-05-15 2008-11-19 罗虹 Wind-driven generator group wheel box
CN201187526Y (en) * 2008-01-02 2009-01-28 代安铭 Wind electric 1.25-2.0 MW paddle-changing double-row ball bearing developed by ultimate design special technique

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Publication number Publication date
WO2011066732A1 (en) 2011-06-09
CN101725631A (en) 2010-06-09

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Owner name: HU NAN QIU ZEYOU PATENT STRATEGIC PLANNING CO., LT

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