WO2014189042A1 - 円すいころ軸受 - Google Patents
円すいころ軸受 Download PDFInfo
- Publication number
- WO2014189042A1 WO2014189042A1 PCT/JP2014/063330 JP2014063330W WO2014189042A1 WO 2014189042 A1 WO2014189042 A1 WO 2014189042A1 JP 2014063330 W JP2014063330 W JP 2014063330W WO 2014189042 A1 WO2014189042 A1 WO 2014189042A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- tapered roller
- cage
- ring
- roller bearing
- tapered
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
- F16C33/4682—Details of individual pockets, e.g. shape or roller retaining means of the end walls, e.g. interaction with the end faces of the 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
- F16C19/36—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 a single row of rollers
- F16C19/364—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 a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
-
- 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
- F16C33/46—Cages for rollers or needles
- F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
- F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
-
- 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
-
- 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
- F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
-
- 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
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/50—Hand tools, workshop equipment or manipulators
- F16C2322/59—Manipulators, e.g. robot arms
Definitions
- the present invention relates to a tapered roller bearing in which an inner ring does not have a large brim.
- Rolling bearings for industrial robots that require a high moment load and high rigidity such as rolling bearings used in industrial robots, must have a large load capacity in the radial direction and a large load capacity in the axial direction, and must be used in a preload state. Is needed.
- a tapered roller bearing is optimal as a rolling bearing type.
- the general tapered roller bearing includes an inner ring 51 having a tapered raceway surface 51 a on the outer peripheral surface, an outer ring 52 having a tapered raceway surface 52 a on the inner peripheral surface, and a raceway of the inner ring 51.
- the retainer 54 is formed by connecting a large-diameter ring portion 55 and a small-diameter ring portion 56 with a plurality of column portions 57, and houses tapered rollers 53 between the column portions 57.
- a large brim 58 and a small brim 59 are integrally formed at the large diameter end of the inner ring 51 and the small diameter end of the inner ring 51 so that the tapered roller 53 and the retainer 54 do not fall off the inner ring 51 (for example, (See FIGS. 8 to 10 of Patent Document 1.)
- Patent Document 1 in the double row tapered roller bearing, when the cages in each row move to the small diameter side of the inner ring, the cages come into contact with each other, and the movement of the cage and the tapered rollers is restricted. By doing so, it has been proposed to increase the load capacity by eliminating the small brim of the inner ring and extending the length of the tapered roller.
- an object of the present invention is to increase the load capacity by eliminating the large brim of the inner ring of the tapered roller bearing.
- a tapered roller bearing includes an inner ring having a tapered raceway surface formed on an outer peripheral surface, an outer ring having a tapered raceway surface formed on an inner peripheral surface, and the inner ring.
- the tapered rollers are housed between the pillars.
- the tapered rollers have a large diameter from the small diameter side. The component force toward the radial side is received by the large-diameter ring portion of the cage.
- the component force from the small diameter side of the tapered roller acting on the cage toward the large diameter side tries to spread the large diameter ring portion of the cage, but the large diameter ring portion of the cage
- the load capacity can be increased.
- the material of the cage is preferably brass, iron-based material subjected to surface treatment or surface modification, polyether ether ketone (PEEK) -based or polyphenylene sulfide (PPS) -based resin.
- PEEK polyether ether ketone
- PPS polyphenylene sulfide
- the angle formed by the contact surface between the large-diameter ring portion of the cage and the tapered roller with the axis of the rotating shaft is 40 to 50 degrees (preferably 45 degrees).
- a lubricating oil groove having both ends opened is provided on the outer peripheral surface and the outer surface of the large-diameter ring portion of the cage, the cross section thereof is increased in order to increase the rigidity of the large-diameter ring portion of the cage. Even if the space for communicating the inside and outside of the tapered roller bearing is reduced by increasing the size, the circulating oil supply to the inside of the tapered roller bearing can be sufficiently performed.
- the tapered roller bearing of the present invention is configured such that, among the forces acting on the tapered roller, the component force from the small diameter side to the large diameter side of the tapered roller is received by the large diameter ring portion of the cage. Therefore, the length of the tapered roller can be extended by eliminating the large collar of the conventional inner ring, and the load capacity can be increased. Moreover, since it is not necessary to process the inner ring with a large collar, the inner ring can be manufactured at a lower cost than the conventional one.
- Vertical sectional view of the tapered roller bearing of the embodiment 1 is a perspective view of the main part of the tapered roller bearing of FIG. Vertical section of a conventional tapered roller bearing
- FIG. 1 shows a state in which the tapered roller bearing 1 of the embodiment is mounted between the housing 2 and the rotating shaft 3.
- the tapered roller bearing 1 includes an inner ring 4 having a tapered raceway surface 4 a on the outer peripheral surface, an outer ring 5 having a tapered raceway surface 5 a on the inner peripheral surface, and a raceway surface 4 a of the inner ring 4 and a raceway surface of the outer ring 5.
- a plurality of tapered rollers 6 incorporated between 5a and 5a, and a cage 7 for holding each tapered roller 6 so as to roll freely.
- the housing 2 has a cylindrical shape arranged on the outer side in the radial direction of the rotary shaft 3, and the outer ring 5 of the tapered roller bearing 1 is fitted into the inner peripheral surface of the end 2b formed with an inner diameter larger than the central portion 2a.
- the inner end surface of the outer ring 5 is in contact with the step surface between the central portion 2a and the end portion 2b.
- the rotating shaft 3 is formed by separately forming a central portion 3a and an end portion 3b having a flange so as to rotate integrally, and an inner ring 4 of the tapered roller bearing 1 is formed on the outer peripheral surface of the end portion 3b.
- the outer end surface of the inner ring 4 is in contact with the inner surface of the flange of the end portion 3b.
- the cage 7 is made of brass and has a large-diameter ring portion 8 and a small-diameter ring portion 9 connected by a plurality of column portions 10.
- the tapered rollers 6 are accommodated between the column portions 10, and the cones are conical.
- a component force from the small diameter side to the large diameter side of the tapered roller 6 is received by the roller receiving surface 8 a of the large diameter ring portion 8. It is like that.
- the cross section of the large-diameter ring portion 8 is formed larger than the conventional one (see FIG. 3).
- the contact surface between the large-diameter ring portion 8 of the cage 7 and the tapered roller 6, that is, the roller receiving surface 8 a of the large-diameter ring portion 8 and the large-diameter side end surface of the tapered roller 6 are the axis of the rotating shaft 3.
- the angle formed (angle ⁇ formed with the straight line X parallel to the axis of the rotary shaft 3 in FIG. 1) is set to be 40 to 50 degrees (preferably 45 degrees).
- the outer circumferential surface of the large-diameter ring portion 8 of the cage 7 has a lubricating oil groove 8b extending in the axial direction and having both ends opened, and the outer surface extending in the radial direction and having both ends thereof. Opened lubricating oil grooves 8c are respectively provided.
- the tapered roller bearing 1 is made of brass as the material of the cage 7 and the cross section of the large diameter ring portion 8 is increased to increase the rigidity of the large diameter ring portion 8.
- the component force from the small diameter side to the large diameter side of the tapered roller 6 is received by the large diameter ring portion 8 of the cage 7, so that the cage 7 Due to the rigidity of the large-diameter ring portion 8, the movement of the tapered roller 6 toward the large-diameter side of the inner ring 4 is restricted, and it is not necessary to provide a large collar on the inner ring 4. Therefore, it is possible to increase the load capacity by extending the length of the tapered roller as compared with the conventional case.
- the angle formed by the contact surface between the large-diameter ring portion 8 of the cage 7 and the tapered roller 6 with the axis of the rotary shaft 3 is about 45 degrees, the force for pushing the cage 7 toward the large-diameter side of the inner ring 4 Further, the ratio of the moving amount of the tapered roller 6 to the inner ring 4 large diameter side with respect to the radial deformation amount of the large diameter ring portion 8 of the cage 7 is moderately suppressed, and the tapered roller 6 moves toward the inner ring 4 large diameter side. The movement can be reliably regulated.
- the entire cage 7 is made of brass having high rigidity, a low friction coefficient, and high wear strength, not only the rigidity of the large-diameter ring portion 8 of the cage 7 is large, but also the large diameter of the cage 7. An increase in rotational torque and wear of both members due to sliding friction generated between the ring portion 8 and the large-diameter side end surface of the tapered roller 6 are also suppressed.
- the material of the cage 7 is not limited to brass, but is preferably a material having characteristics such as high rigidity, low friction coefficient, and high wear strength.
- surface treatment such as DLC, hard chrome plating, phosphate film, etc.
- an iron-based material subjected to surface modification such as shot peening, or a PEEK-based or PPS-based resin can be used.
- the lubricating oil grooves 8b and 8c having both ends opened are provided on the outer peripheral surface and the outer surface of the large-diameter ring portion 8 of the cage 7, the cross-section of the large-diameter ring portion 8 of the cage 7 is smaller than the conventional one. Even if the space for communication between the inside and outside of the tapered roller bearing 1 is small, the circulating oil supply to the inside of the tapered roller bearing 1 can be sufficiently performed.
Abstract
Description
2 ハウジング
3 回転軸
4 内輪
4a 軌道面
5 外輪
5a 軌道面
6 円すいころ
7 保持器
8 大径リング部
8a ころ受け面
8b、8c 潤滑油溝
9 小径リング部
10 柱部
Claims (3)
- 外周面にテーパ状の軌道面が形成された内輪と、内周面にテーパ状の軌道面が形成された外輪と、前記内輪の軌道面と外輪の軌道面との間に組み込まれる複数の円すいころと、前記各円すいころを転動自在に保持する保持器とを備え、前記保持器は、大径リング部と小径リング部とを複数の柱部で連結したもので、その柱部どうしの間に前記円すいころを収納しており、前記内輪および外輪から円すいころに作用する力のうち、前記円すいころの小径側から大径側へ向かう分力を前記保持器の大径リング部で受けるようにした円すいころ軸受。
- 前記保持器の大径リング部と円すいころとの接触面が回転軸の軸心となす角度を、40~50度とした請求項1に記載の円すいころ軸受。
- 前記保持器の大径リング部の外周面と外側面に、両端が開放された潤滑油溝を設けた請求項1または2に記載の円すいころ軸受。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP14801201.6A EP3001054A1 (en) | 2013-05-23 | 2014-05-20 | Conical roller bearing |
US14/891,685 US20160108959A1 (en) | 2013-05-23 | 2014-05-20 | Tapered roller bearing |
CN201480028873.1A CN105229320A (zh) | 2013-05-23 | 2014-05-20 | 圆锥滚子轴承 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013108854A JP2014228074A (ja) | 2013-05-23 | 2013-05-23 | 円すいころ軸受 |
JP2013-108854 | 2013-05-23 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014189042A1 true WO2014189042A1 (ja) | 2014-11-27 |
Family
ID=51933595
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/063330 WO2014189042A1 (ja) | 2013-05-23 | 2014-05-20 | 円すいころ軸受 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20160108959A1 (ja) |
EP (1) | EP3001054A1 (ja) |
JP (1) | JP2014228074A (ja) |
CN (1) | CN105229320A (ja) |
WO (1) | WO2014189042A1 (ja) |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4936998Y1 (ja) * | 1968-10-02 | 1974-10-09 | ||
JP2000130443A (ja) * | 1998-10-26 | 2000-05-12 | Ntn Corp | 円すいころ軸受および円すいころ軸受用保持器 |
JP2010101369A (ja) * | 2008-10-22 | 2010-05-06 | Ntn Corp | 転がり軸受 |
JP4964696B2 (ja) | 2007-07-18 | 2012-07-04 | Ntn株式会社 | 複列円すいころ軸受 |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB191119446A (en) * | 1911-08-31 | 1912-07-04 | Llewellyn De Milford Ellis | Improvements in Roller Bearings. |
US1402071A (en) * | 1920-03-05 | 1922-01-03 | William F Huther | Roller bearing |
US1843293A (en) * | 1928-02-27 | 1932-02-02 | Medved Nicholas | Roller bearing |
US2219031A (en) * | 1937-12-01 | 1940-10-22 | Bantam Bearings Corp | Bearing construction |
US4655619A (en) * | 1981-06-26 | 1987-04-07 | The United States Of America As Represented By The Secretary Of The Army | Tapered roller bearing |
FR2882116B1 (fr) * | 2005-02-11 | 2007-04-27 | Snr Roulements Sa | Palier a roulement conique comprenant une cage de filtration |
DE102009031068A1 (de) * | 2009-06-30 | 2011-01-05 | Aktiebolaget Skf | Lageranordnung und gelagertes Bauteil für ein Differentialgetriebe |
US8998498B2 (en) * | 2009-11-17 | 2015-04-07 | Nsk Ltd. | Tapered roller bearing and manufacturing method for retainer of tapered roller bearing |
DK2434150T4 (en) * | 2010-09-27 | 2016-12-05 | Siemens Ag | Three row roller bearing, especially for a wind turbine |
WO2013051422A1 (ja) * | 2011-10-04 | 2013-04-11 | ナブテスコ株式会社 | 歯車伝動装置 |
US20150323008A1 (en) * | 2012-12-25 | 2015-11-12 | Nsk Ltd. | Tapered roller bearing |
US9243663B2 (en) * | 2013-08-28 | 2016-01-26 | Jtekt Corporation | Rolling bearing and power transmission device including rolling bearing |
JP6442837B2 (ja) * | 2014-03-10 | 2018-12-26 | 株式会社ジェイテクト | 円錐ころ軸受 |
-
2013
- 2013-05-23 JP JP2013108854A patent/JP2014228074A/ja not_active Withdrawn
-
2014
- 2014-05-20 US US14/891,685 patent/US20160108959A1/en not_active Abandoned
- 2014-05-20 EP EP14801201.6A patent/EP3001054A1/en not_active Withdrawn
- 2014-05-20 WO PCT/JP2014/063330 patent/WO2014189042A1/ja active Application Filing
- 2014-05-20 CN CN201480028873.1A patent/CN105229320A/zh active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4936998Y1 (ja) * | 1968-10-02 | 1974-10-09 | ||
JP2000130443A (ja) * | 1998-10-26 | 2000-05-12 | Ntn Corp | 円すいころ軸受および円すいころ軸受用保持器 |
JP4964696B2 (ja) | 2007-07-18 | 2012-07-04 | Ntn株式会社 | 複列円すいころ軸受 |
JP2010101369A (ja) * | 2008-10-22 | 2010-05-06 | Ntn Corp | 転がり軸受 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3001054A4 * |
Also Published As
Publication number | Publication date |
---|---|
CN105229320A (zh) | 2016-01-06 |
EP3001054A4 (en) | 2016-03-30 |
US20160108959A1 (en) | 2016-04-21 |
JP2014228074A (ja) | 2014-12-08 |
EP3001054A1 (en) | 2016-03-30 |
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