CN112253619A - Large-cone-angle double-row tapered roller bearing for wind power main shaft - Google Patents
Large-cone-angle double-row tapered roller bearing for wind power main shaft Download PDFInfo
- Publication number
- CN112253619A CN112253619A CN202011338230.0A CN202011338230A CN112253619A CN 112253619 A CN112253619 A CN 112253619A CN 202011338230 A CN202011338230 A CN 202011338230A CN 112253619 A CN112253619 A CN 112253619A
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- China
- Prior art keywords
- tapered roller
- main shaft
- bearing
- roller bearing
- wind power
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- 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.)
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Classifications
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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
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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
- 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
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
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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
- 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
Abstract
The invention belongs to the technical field of bearing design and manufacture, and particularly relates to a large-taper-angle double-row tapered roller bearing for a wind power main shaft. The tapered roller bearing provided by the invention can be used for carrying out appropriate modification on the two rows of roller buses and the two rows of ferrule raceways according to different stress effects of the two rows of rollers, so that the running effect of the rollers is ensured.
Description
Technical Field
The invention belongs to the technical field of bearing design and manufacture, and particularly relates to a large-taper-angle double-row tapered roller bearing for a wind power main shaft, which is widely applied to the fields of heavy-load working conditions, large-rated load, machinery of long-service-life bearings and the like.
Background
At present, in the bearing industry, during the installation and working processes of the tapered roller bearing, due to the axial force and the unbalance loading action on two rows of rollers, the left row and the right row of rollers are stressed differently, so that the phenomenon of slipping or locking frequently occurs, and the normal operation of the bearing is influenced.
Meanwhile, tapered roller bearings often employ hollow rollers, large and small washers, and strut structures in order to increase the load. The pillar is connected with big and small packing rings, and two packing rings are all fixed with the pillar, and big packing ring screw thread, little packing ring unthreaded hole and pillar welding. But due to the influence of the welding frame, the phenomenon that the axial runout of the outer ring is seriously out of tolerance occurs. And because the welding quality of the support is unstable in the using process, the fracture of the defect part of the welding end of the support is the main reason of bearing failure under the action of repeated impact load. The method comprises the following specific steps:
(1) in the welding process of the retainer, the deformation is easily generated at high temperature, so that the axial runout of the end surface of the bearing outer ring to the raceway is seriously out of tolerance, the rotation flexibility of the bearing is reduced, the sliding friction in the working process of the bearing is increased, and the service life is reduced.
(2) The axial clearance between the retainer and the roller is controlled by the adjusting gaskets, a plurality of adjusting gaskets are evenly placed on the end face of the inner side of the retainer at intervals before welding, the adjusting gaskets are pulled out after welding, the deformation of the retainer causes uneven clearance, and the production efficiency is low.
(3) Welding quality is greatly influenced by human factors, welding slag is easy to fall into a bearing assembly in the welding process and is difficult to remove, the contact surface can be scratched, vibration and noise of the bearing are increased, and the service life of the bearing is shortened.
(4) If no protective atmosphere exists, the atmosphere is in direct contact with a high-temperature fusion welding area, so that materials are oxidized, and nitrogen, water vapor and the like entering the fusion welding area can form defects such as air holes, slag inclusion, cracks and the like in a welding line, so that the quality of the welding line is reduced, the welding line is easy to block, and the working condition cannot be met.
Disclosure of Invention
According to the defects in the prior art, the invention aims to provide the large-taper-angle double-row tapered roller bearing for the wind power main shaft, which can avoid bearing failure and prolong the service life of the bearing.
In order to achieve the purpose, the technical scheme adopted by the invention is as follows: the large-taper-angle double-row tapered roller bearing for the wind power main shaft comprises an inner ring, an outer ring and two rows of rollers, wherein the two rows of rollers are kept between the inner ring and the outer ring through two rows of retainers, the two rows of rollers are arranged differently, and the convexity of a row of roller rolling surface buses close to a motor side is larger than that of a row of roller rolling surface buses close to a hub side.
Further, the inner and outer ring raceway convexities on the motor side are larger than those on the hub side.
Furthermore, the inner ring is of a split structure, and the inner ring on the hub side and the inner ring on the motor side are matched and positioned through a stepped structure.
Furthermore, a boss is arranged on the large end face of the bearing inner ring close to the hub side.
Furthermore, the two rows of the retainers are independent and split, each row of the retainers comprises a support pillar and gaskets connected to two ends of the support pillar, one end of the support pillar is provided with a threaded end, the other end of the support pillar is provided with a smooth end, and the threaded end of the support pillar is connected with the gaskets through threads; the thread turning directions of the threaded ends of the struts on the retainers on the two sides are opposite, and the threads of the threaded ends of the struts are self-locking threads.
Further, the screw thread direction of the screw thread end of the strut near the motor side is right-handed, and the screw thread direction of the screw thread end of the strut near the hub side is left-handed.
Further, the smooth end of the strut is flexibly supported with the washer.
Furthermore, the gasket comprises a large gasket and a small gasket, the large gasket close to the end face of the bearing is provided with a cylindrical through hole and is flexibly supported with the smooth end of the support pillar, and the small gasket close to the center of the bearing is provided with a threaded hole and is in threaded connection with the threaded end of the support pillar.
Further, the rollers are hollow rollers, and the struts can be threaded from the large washers through the rollers to the small washers during assembly.
Further, the roller end face is in contact with the side wall of the bearing inner ring raceway.
Further, the included angle between the support of the large-cone-angle double-row tapered roller bearing and the horizontal plane is 45 degrees, namely the included angle minus the half angle of the roller is 45 degrees.
The invention has the beneficial effects that: the tapered roller bearing provided by the invention can be used for carrying out appropriate modification on the two rows of roller buses and the two rows of ferrule raceways according to different stress effects of the two rows of rollers, so that the running effect of the rollers is ensured.
Drawings
FIG. 1 is a schematic structural view of a tapered roller bearing;
FIG. 2 is a schematic structural view of a large washer of the tapered roller bearing cage;
FIG. 3 is a view A-A of FIG. 2;
in the figure: the wheel hub comprises an outer ring 1, a wheel hub side inner ring 2, a motor side inner ring 3, a wheel hub side conical roller 4, a large gasket 5, a small gasket 6 and a strut 7, wherein the strut 8, a boss 9 and the motor side conical roller are arranged.
Detailed Description
In order to make the structure and function of the present invention clearer, the technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the drawings in the embodiments of the present invention.
Referring to the attached drawings 1-3, the large taper angle double-row tapered roller bearing for the wind power main shaft comprises an inner ring, an outer ring 1 and two rows of rollers, wherein the two rows of rollers are held between the inner ring and the outer ring through two rows of retainers, the two rows of rollers are arranged differently, and the convexity of the right side roller paths of the row of rollers 9, the inner ring 3 and the outer ring 1 close to the motor side is larger than that of the left side roller paths of the row of rollers 4, the inner ring 2 and the outer ring 1 close to the hub side.
Based on the technical scheme, the left row and the right row of rollers are different, and the left row and the right row of rollers are subjected to different modification: because the bearing is under the action of axial force and unbalance loading in work, the left and right rows of rollers are under different stresses, and different designs are required. A row of bearing rollers 9 close to the motor side is large in load, the rollers are not easy to slip, the profile is large, and the clearance needs to be large. The bearing roller 4 near the hub side is slightly stressed, and the roller profile modification height is small. The play needs to be small to avoid the rollers slipping in the raceways. The design of the left and right rows of rollers is different.
Further, the inner ring is of a split structure, and the hub side inner ring 2 and the motor side inner ring 3 are located in a matched mode through a stepped structure.
Further, a boss 8 is provided on the large end surface of the bearing inner ring 2 near the hub side. The boss side is a hub side, and the design is convenient for distinguishing the hub side and the motor side of the bearing during bearing installation.
Furthermore, the two rows of the retainers are independent and split, each row of the retainers comprises a strut 7 and gaskets connected to two ends of the strut, one end of the strut 7 is a threaded end, the other end of the strut is a smooth end, and the threaded end of the strut is in threaded connection with the gaskets; the thread turning directions of the threaded ends of the struts on the retainers on the two sides are opposite, and the threads of the threaded ends of the struts are self-locking threads.
Based on the technical scheme, the main shaft bearing structure is a double-row tapered roller bearing. The conventional design of the tapered roller retainer pillar and the gasket applied in the prior art is a forward-screwing screw, but along with the operation of the bearing, the retainer pillar and the gasket on one side of the bearing are in threaded connection and are loosened. The retainer pillar and the washer on one side of the bearing are designed to be in forward-rotation threaded connection, and the retainer pillar and the washer on the other side of the bearing are designed to be in reverse-rotation threaded connection, so that the retainer pillar and the retainer washer are always in a tight fit state due to the autorotation of the rolling elements in the operation process of the bearing, the threaded washer is prevented from being separated from the pillar, the self-locking effect is achieved, and the stability of the bearing is improved. The utility model provides a pillar head adopts outer hexagon nut structure, and the size is the same with the nut size of standard in the design, the pillar installation of being convenient for.
According to the experiment requirement of the spindle motor, the spindle motor can rotate forward and backward for testing. In order to prevent the support and the washer from loosening, the support and the small washer are fixed by threads through glue during assembly. And meanwhile, the two rows of inner rings are fixed by glue.
The specific numerical value of the gap between the strut and the large washer needs to be determined by calculating the sagging amount and the gap between the large washer and the large end of the roller according to the gap between the strut and the roller strut hole. The sag amount of the strut is calculated according to the gap between the roller strut hole and the strut, and then the displacement of the large washer and the large end surface of the roller in the horizontal direction, the vertical direction and the direction is calculated according to the inclination angle of 45 degrees, so that the gap between the strut and the large washer is calculated. The large washer is prevented from touching the large end face of the roller when the strut moves relatively, and meanwhile, the comprehensive consideration is given to the position degree, the processing level and the stress deformation of the strut of the large washer.
Further, the screw thread direction of the screw thread end of the strut near the motor side is right-handed, and the screw thread direction of the screw thread end of the strut near the hub side is left-handed.
In the above-described aspect, since the bearing rotates clockwise when viewed from the hub side to the motor side, the roller rotation of the bearing closer to the hub side tends to be counterclockwise, and the direction in which the frictional force is generated with the strut is counterclockwise, so that the strut tends to move counterclockwise. However, the rollers and the struts in the other row are opposite to each other, that is, the bearings rotate counterclockwise when viewed from the motor side toward the hub side, the rollers rotate clockwise, and the direction of the friction force generated between the rollers and the struts is clockwise, so that the struts rotate more and more tightly clockwise.
Further, the smooth end of the strut is flexibly supported with the washer.
The technical scheme of the invention is that the washers on two sides of the retainer are integrally machined, the welding spots do not exist between the retainer strut and the washers, one end of the retainer strut is in clearance fit with one washer, so that the retainer is in a flexible state, the retainer strut, the inner ring form a self-locking state of flexible connection, the retainer has no weak point caused by welding in the bearing operation process, the strength of the retainer is improved, and the reliability of the bearing is better ensured. Meanwhile, the pillar and the small roller washer are flexibly supported with the large washer in the running process, so that the phenomenon of blocking is avoided.
Further, the gasket comprises a large gasket 5 and a small gasket 6, the large gasket 5 close to the end face of the bearing is provided with a cylindrical through hole and flexibly supported with the smooth end of the support, and the small gasket 6 close to the center of the bearing is provided with a threaded hole and is in threaded connection with the threaded end of the support. The original threaded hole of the large washer 5 is changed into a unthreaded hole. The strut 7 is free to move a little in the axial direction of the strut.
Further, the roller is a hollow roller, and the pillar 7 is screwed from the large washer 5 through the roller 4 to the small washer 6 when assembling.
Further, the roller end face is in contact with the side wall of the bearing inner ring raceway.
Further, the included angle between the large-cone-angle double-row tapered roller bearing strut and the horizontal plane is 45 degrees, namely the included angle of the contact angle minus the roller half angle is 45 degrees.
The above list is only the preferred embodiment of the present invention. It is obvious that the invention is not limited to the above embodiments, but that many variations are possible. All modifications which can be derived or suggested by a person skilled in the art from the disclosure of the present invention are to be considered within the scope of the invention.
Claims (10)
1. Wind-powered electricity generation main shaft is with big bevel angle biserial tapered roller bearing, its characterized in that: the roller cage comprises an inner ring, an outer ring and two rows of rollers, wherein the two rows of rollers are held between the inner ring and the outer ring through two rows of retainers, the two rows of rollers are arranged differently, and the bus convexity of the rolling surface of one row of rollers close to the motor side is larger than the bus convexity of the rolling surface of one row of rollers close to the hub side.
2. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 1, characterized in that: the convexity of the inner ring and outer ring roller paths close to the motor side is larger than that of the inner ring and outer ring roller paths close to the hub side.
3. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 1, characterized in that: the inner ring is of a split structure, and the inner ring on the hub side and the inner ring on the motor side are matched and positioned through a stepped structure; the end face of the roller is in contact with the side wall of the raceway of the bearing inner ring.
4. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 1, characterized in that: and a boss is arranged on the large end surface of the bearing inner ring close to the hub side.
5. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 1, characterized in that: the two rows of the retainers are independent and split, each row of the retainers comprises a support pillar and gaskets connected to two ends of the support pillar, one end of the support pillar is provided with a threaded end, the other end of the support pillar is provided with a smooth end, and the threaded end of the support pillar is connected with the gaskets through threads; the thread turning directions of the threaded ends of the struts on the retainers on the two sides are opposite, and the threads of the threaded ends of the struts are self-locking threads.
6. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 5, characterized in that: the screw thread direction of the screw thread end of the pillar close to the motor side is right-handed, and the screw thread direction of the screw thread end of the pillar close to the hub side is left-handed.
7. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 5, characterized in that: the smooth end of the strut is flexibly supported by the gasket.
8. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 5, characterized in that: the gasket comprises a large gasket and a small gasket, the large gasket close to the end face of the bearing is provided with a cylindrical through hole and flexibly supported with the smooth end of the pillar, and the small gasket close to the center of the bearing is provided with a threaded hole and is in threaded connection with the threaded end of the pillar.
9. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 8, characterized in that: the roller is a hollow roller, and the strut can be screwed into the small washer from the large washer through the roller during assembly.
10. The large-taper-angle double-row tapered roller bearing for the wind power main shaft according to claim 1, characterized in that: the included angle between the large-cone-angle double-row tapered roller bearing support and the horizontal plane is 45 degrees.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011338230.0A CN112253619A (en) | 2020-11-25 | 2020-11-25 | Large-cone-angle double-row tapered roller bearing for wind power main shaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011338230.0A CN112253619A (en) | 2020-11-25 | 2020-11-25 | Large-cone-angle double-row tapered roller bearing for wind power main shaft |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112253619A true CN112253619A (en) | 2021-01-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011338230.0A Pending CN112253619A (en) | 2020-11-25 | 2020-11-25 | Large-cone-angle double-row tapered roller bearing for wind power main shaft |
Country Status (1)
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|---|---|
| CN (1) | CN112253619A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115013442A (en) * | 2022-06-30 | 2022-09-06 | 中国铁建重工集团股份有限公司 | Holding rack |
| CN117057170A (en) * | 2023-10-12 | 2023-11-14 | 齐鲁工业大学(山东省科学院) | Double-row self-aligning roller bearing contact mechanical model based on flexible contact and play |
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| JPH11270553A (en) * | 1998-03-20 | 1999-10-05 | Ntn Corp | Double row tapered roller bearing |
| JP2005147331A (en) * | 2003-11-18 | 2005-06-09 | Ntn Corp | Double row rolling bearing |
| JP2006090346A (en) * | 2004-09-21 | 2006-04-06 | Ntn Corp | Double row automatic aligning roller bearing and main shaft supporting structure of wind power generator |
| CN108194511A (en) * | 2018-03-06 | 2018-06-22 | 洛阳新强联回转支承股份有限公司 | A kind of retainer of double-row conical bearing |
| CN109322911A (en) * | 2018-11-30 | 2019-02-12 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Wind-power electricity generation main shaft biserial abnormity self-aligning roller bearing |
| EP3601819A1 (en) * | 2017-03-31 | 2020-02-05 | ThyssenKrupp Rothe Erde GmbH | Rolling bearing arrangement and wind turbine |
| CN110886770A (en) * | 2019-12-26 | 2020-03-17 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Double-row conical main shaft bearing retainer |
| CN111878507A (en) * | 2020-08-27 | 2020-11-03 | 明阳智慧能源集团股份公司 | Asymmetric double-row tapered roller main bearing of wind turbine generator and design method thereof |
| CN213808477U (en) * | 2020-11-25 | 2021-07-27 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Large-cone-angle double-row tapered roller bearing for wind power main shaft |
-
2020
- 2020-11-25 CN CN202011338230.0A patent/CN112253619A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11270553A (en) * | 1998-03-20 | 1999-10-05 | Ntn Corp | Double row tapered roller bearing |
| JP2005147331A (en) * | 2003-11-18 | 2005-06-09 | Ntn Corp | Double row rolling bearing |
| JP2006090346A (en) * | 2004-09-21 | 2006-04-06 | Ntn Corp | Double row automatic aligning roller bearing and main shaft supporting structure of wind power generator |
| EP3601819A1 (en) * | 2017-03-31 | 2020-02-05 | ThyssenKrupp Rothe Erde GmbH | Rolling bearing arrangement and wind turbine |
| CN108194511A (en) * | 2018-03-06 | 2018-06-22 | 洛阳新强联回转支承股份有限公司 | A kind of retainer of double-row conical bearing |
| CN109322911A (en) * | 2018-11-30 | 2019-02-12 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Wind-power electricity generation main shaft biserial abnormity self-aligning roller bearing |
| CN110886770A (en) * | 2019-12-26 | 2020-03-17 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Double-row conical main shaft bearing retainer |
| CN111878507A (en) * | 2020-08-27 | 2020-11-03 | 明阳智慧能源集团股份公司 | Asymmetric double-row tapered roller main bearing of wind turbine generator and design method thereof |
| CN213808477U (en) * | 2020-11-25 | 2021-07-27 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Large-cone-angle double-row tapered roller bearing for wind power main shaft |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115013442A (en) * | 2022-06-30 | 2022-09-06 | 中国铁建重工集团股份有限公司 | Holding rack |
| CN115013442B (en) * | 2022-06-30 | 2023-10-31 | 中国铁建重工集团股份有限公司 | Retainer |
| CN117057170A (en) * | 2023-10-12 | 2023-11-14 | 齐鲁工业大学(山东省科学院) | Double-row self-aligning roller bearing contact mechanical model based on flexible contact and play |
| CN117057170B (en) * | 2023-10-12 | 2024-01-26 | 齐鲁工业大学(山东省科学院) | Double-row self-aligning roller bearing contact mechanical model based on flexible contact and play |
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