EP0000703B1 - A self-aligning two row thrust roller bearing - Google Patents
A self-aligning two row thrust roller bearing Download PDFInfo
- Publication number
- EP0000703B1 EP0000703B1 EP78100340A EP78100340A EP0000703B1 EP 0000703 B1 EP0000703 B1 EP 0000703B1 EP 78100340 A EP78100340 A EP 78100340A EP 78100340 A EP78100340 A EP 78100340A EP 0000703 B1 EP0000703 B1 EP 0000703B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rollers
- roller
- self
- bearing
- roller bearing
- Prior art date
- 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.)
- Expired
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
- 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
- F16C19/30—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 axial load mainly
-
- 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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
Definitions
- This invention relates to a self-aligning thrust roller bearing incorporating two relatively rotatable elements, each of which being provided with at least one coaxial race track and a number of rollers provided between and in engagement with the race tracks, the angle between the bearing axis and the roller axes exceeding 20°, the race tracks and the rollers being curved in axial section.
- Spherical thrust roller bearings are earlier known. These bearings generally have one row of unsymmetrical rollers, one bearing ring with a spherical race track and one bearing ring with a roller guiding flange.
- Rings having flanges are expensive to manufacture and bearings having such rings have a high starting friction. It is thus desirable to avoid the need of the flange.
- a possible method for avoiding a flange is to use symmetrical rollers.
- a roller is in this respect considered to be symmetrical if it can be divided in two congruent halves with a cross sectional plane half way between the ends of the roller.
- Symmetrical rollers having such a large axial extension and being arranged with such a large angle between the roller axis and the bearing axis as the rollers appearing in spherical thrust bearings are, however, difficult to guide with a desired precision.
- the sliding in the contact points between the roller and the race track will be large, which leads to power losses and a risk for bearing failure due to the generated friction heat.
- the purpose of the present invention is to provide a bearing of the type defined in the preamble, wherein a good roller guiding is obtained without a flange on one of the rings and which has a low friction at start and during operation.
- rollers of the bearing Due to the fact that all rollers of the bearing have the same revolution angular speed about the bearing axis only one cage for the rollers is needed, which saves space and cost.
- a good roller guiding can easily be obtained by the rollers being arranged to contact each other adjacent the inner race ring or by means of a guiding ring at the outer race ring. Both roller rows are subjected to load when the bearing takes up axial load, which guarantees a good guiding of all rollers.
- By using two rollers instead of one roller with a corresponding axial extension it is possible to halve the bearing friction losses, since the relative sliding between the roller and the race track, i.e. the relation between the sliding speed and the rolling speed, is about proportional to the length of the roller.
- the bearing has two rings 1 and 2 each having C0 2 axial race tracks for a number of symmetrical rollers 3,4 provided between the rings, which rollers are arranged in double rows, and the rollers in both rows are preferably identical.
- the roller rows are situated side by side and the axes 5, 6 of the rollers in each roller row are inclined in the same direction relative to the bearing axis 7.
- the race track of the ring 2 has preferably a spherical surface, which means that the ring 1 and the set of rollers with the rollers 3, 4 and roller cage 8 can be freely tilted relative to the ring 2 without causing a too high contact pressure at the contact between the roller and the race track. If only a limited self- alignment is aimed at, it is possible to let the surface of the race track be non-spherical.
- the load capacity of the bearing is of the same size as the load capacity of a one row bearing, the rollers of which are twice as long as the rollers 3 and 4 and has a corresponding contact angle.
- the limited length of the rollers 3, 4 together with the fact that both roller rows are exposed to load means that the guiding of the rollers will not cause any great difficulties.
- rollers of the two rows in a bearing according to the invention always have the same revolution angular speed relative to each other.
- a single cage can thus be used for both roller rows without risking that the rollers of one row will influence the rollers of the other row through the cage.
- the bearing will be more easy to'manufacture and to handle as it incorporates as few separate parts as possible.
- the bearing can be provided with three or more rows of rollers if it is desired to produce an extra large load capacity and a low relative sliding.
- the race tracks can also be arranged on more than two rings.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Description
- This invention relates to a self-aligning thrust roller bearing incorporating two relatively rotatable elements, each of which being provided with at least one coaxial race track and a number of rollers provided between and in engagement with the race tracks, the angle between the bearing axis and the roller axes exceeding 20°, the race tracks and the rollers being curved in axial section.
- Spherical thrust roller bearings are earlier known. These bearings generally have one row of unsymmetrical rollers, one bearing ring with a spherical race track and one bearing ring with a roller guiding flange.
- Rings having flanges are expensive to manufacture and bearings having such rings have a high starting friction. It is thus desirable to avoid the need of the flange. A possible method for avoiding a flange is to use symmetrical rollers. A roller is in this respect considered to be symmetrical if it can be divided in two congruent halves with a cross sectional plane half way between the ends of the roller. Symmetrical rollers having such a large axial extension and being arranged with such a large angle between the roller axis and the bearing axis as the rollers appearing in spherical thrust bearings are, however, difficult to guide with a desired precision. Furthermore, the sliding in the contact points between the roller and the race track will be large, which leads to power losses and a risk for bearing failure due to the generated friction heat.
- The purpose of the present invention is to provide a bearing of the type defined in the preamble, wherein a good roller guiding is obtained without a flange on one of the rings and which has a low friction at start and during operation.
- This is achieved according to the invention thereby that the bearing is given the characteristics defined in the accompanying claim 1.
- Due to the fact that all rollers of the bearing have the same revolution angular speed about the bearing axis only one cage for the rollers is needed, which saves space and cost. A good roller guiding can easily be obtained by the rollers being arranged to contact each other adjacent the inner race ring or by means of a guiding ring at the outer race ring. Both roller rows are subjected to load when the bearing takes up axial load, which guarantees a good guiding of all rollers. By using two rollers instead of one roller with a corresponding axial extension it is possible to halve the bearing friction losses, since the relative sliding between the roller and the race track, i.e. the relation between the sliding speed and the rolling speed, is about proportional to the length of the roller.
- Hereinafter the invention will be further described with reference to the accompanying drawing, which shows an axial section through a bearing according to an embodiment of the invention.
- The bearing has two
rings 1 and 2 each having C02 axial race tracks for a number ofsymmetrical rollers 3,4 provided between the rings, which rollers are arranged in double rows, and the rollers in both rows are preferably identical. The roller rows are situated side by side and the axes 5, 6 of the rollers in each roller row are inclined in the same direction relative to the bearing axis 7. The race track of thering 2 has preferably a spherical surface, which means that the ring 1 and the set of rollers with therollers 3, 4 androller cage 8 can be freely tilted relative to thering 2 without causing a too high contact pressure at the contact between the roller and the race track. If only a limited self- alignment is aimed at, it is possible to let the surface of the race track be non-spherical. - As both roller rows will take up load when the bearing is subjected to axial load the load capacity of the bearing is of the same size as the load capacity of a one row bearing, the rollers of which are twice as long as the
rollers 3 and 4 and has a corresponding contact angle. The limited length of therollers 3, 4 together with the fact that both roller rows are exposed to load means that the guiding of the rollers will not cause any great difficulties. In order to obtain a good roller guiding it is possible to allow the ends of the rollers of rollers in different rows to contact each other adjacent the inner race ring 1 such as shown inpoint 9. Alternatively it is possible to arrange a loose guidingring 10 between the roller rows adjacent the outer race ring. - In all roller bearings having curved race track profiles and correspondingly curved roller profiles a certain sliding will take place at the contact points between the roller race track and the roller, which will cause friction losses. An estimation of how large these losses are in a bearing is the size of the relative sliding in these contact points. The relative sliding is defined as the ratio between the sliding speed and the rolling speed in the contact points. It can be shown that in a bearing having symmetrical rollers and in which a pure rolling takes place in only one rolling contact point the relative sliding is proportonal to the length of the roller. If the available length of the roller is divided on several rollers, such as in the present invention, the relative sliding is reduced and thereby also the friction losses as also the load is divided on several rollers.
- The rollers of the two rows in a bearing according to the invention always have the same revolution angular speed relative to each other. A single cage can thus be used for both roller rows without risking that the rollers of one row will influence the rollers of the other row through the cage. Besides being space saving the use of one single cage means that the bearing will be more easy to'manufacture and to handle as it incorporates as few separate parts as possible.
- Within the scope of the invention it is possible to vary the bearing design within wide ranges. The bearing can be provided with three or more rows of rollers if it is desired to produce an extra large load capacity and a low relative sliding. The race tracks can also be arranged on more than two rings.
Claims (4)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE7709175A SE411064B (en) | 1977-08-15 | 1977-08-15 | DOUBLE SELF-ADJUSTING AXIAL ROLL BEARINGS |
SE7709175 | 1977-08-15 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0000703A1 EP0000703A1 (en) | 1979-02-21 |
EP0000703B1 true EP0000703B1 (en) | 1981-02-04 |
Family
ID=20332003
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP78100340A Expired EP0000703B1 (en) | 1977-08-15 | 1978-07-10 | A self-aligning two row thrust roller bearing |
Country Status (6)
Country | Link |
---|---|
US (1) | US4209210A (en) |
EP (1) | EP0000703B1 (en) |
JP (1) | JPS54112433A (en) |
DE (1) | DE2860391D1 (en) |
IT (2) | IT1111194B (en) |
SE (1) | SE411064B (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4513869A (en) * | 1982-02-11 | 1985-04-30 | Armco, Inc. | Pedestal crane mounting system |
DK0498232T3 (en) * | 1991-02-04 | 1995-07-17 | Pwb Praezis Werkzeug Bau Ag | Tool preset |
WO1992021889A1 (en) * | 1991-06-05 | 1992-12-10 | 'tribos' Zaklad Naukowo Badawczy | Single-row radial rolling bearing |
DE19612589B4 (en) * | 1996-03-29 | 2005-12-22 | Skf Gmbh | storage |
DE102006050940A1 (en) * | 2006-10-28 | 2008-04-30 | Schaeffler Kg | Roller bearing for use in wheel bearing of motor vehicle, has outer ring defining outer path, and inner and outer paths formed and arranged such that ling body axis is bent towards bearing axis under angle of incidence |
CN105987073A (en) * | 2015-02-06 | 2016-10-05 | 舍弗勒技术股份两合公司 | Thrust ball bearing |
CN114483769B (en) * | 2022-01-25 | 2023-11-14 | 中国铁建重工集团股份有限公司 | Novel aligning slewing bearing with high unbalanced load bearing capacity |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1208428A (en) * | 1914-01-09 | 1916-12-12 | Frank Whitney | Roller bearing. |
DE331454C (en) * | 1919-02-27 | 1921-01-07 | Skf Svenska Kullagerfab Ab | Self-adjusting roller bearing |
US1548821A (en) * | 1920-09-23 | 1925-08-11 | Wilhelm B Bronander | Roller bearing |
FR572167A (en) * | 1923-10-23 | 1924-06-02 | Improvements to roller bearings | |
US1645345A (en) * | 1926-12-09 | 1927-10-11 | Okner Bernard | Ball bearing |
US1918677A (en) * | 1931-09-11 | 1933-07-18 | Wingquist Sven Gustaf | Double-row roller bearing |
US2622946A (en) * | 1950-12-12 | 1952-12-23 | Mckissick Products | Retaining means for idler units |
US3004809A (en) * | 1957-12-19 | 1961-10-17 | Skf Svenska Kullagerfab Ab | Thrust roller bearings |
JPS4529922Y1 (en) * | 1966-08-27 | 1970-11-17 | ||
DE1813979B2 (en) * | 1968-12-11 | 1973-11-08 | The Torrington Co., Torrington, Conn. (V.St.A.) | Double row thrust roller bearing |
JPS5761933B2 (en) * | 1972-07-07 | 1982-12-27 | Esu Kee Efu Andeyusutoriaru Toreedeingu Ando Dev Co Bv |
-
1977
- 1977-08-15 SE SE7709175A patent/SE411064B/en not_active IP Right Cessation
-
1978
- 1978-06-05 US US05/912,197 patent/US4209210A/en not_active Expired - Lifetime
- 1978-07-06 IT IT25395/78A patent/IT1111194B/en active
- 1978-07-06 IT IT7822259U patent/IT7822259V0/en unknown
- 1978-07-10 DE DE7878100340T patent/DE2860391D1/en not_active Expired
- 1978-07-10 EP EP78100340A patent/EP0000703B1/en not_active Expired
- 1978-08-09 JP JP9612478A patent/JPS54112433A/en active Granted
Also Published As
Publication number | Publication date |
---|---|
US4209210A (en) | 1980-06-24 |
JPS559571B2 (en) | 1980-03-11 |
JPS54112433A (en) | 1979-09-03 |
IT7822259V0 (en) | 1978-07-06 |
DE2860391D1 (en) | 1981-03-19 |
SE411064B (en) | 1979-11-26 |
IT7825395A0 (en) | 1978-07-06 |
SE7709175L (en) | 1979-02-16 |
EP0000703A1 (en) | 1979-02-21 |
IT1111194B (en) | 1986-01-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0175858B1 (en) | Radial roller bearing | |
US4379706A (en) | Slidable-type constant velocity universal joint | |
US4192154A (en) | Constant velocity universal joint | |
JPS58134222A (en) | One row or four row tapered roller bearing | |
SE8203576L (en) | ROLLER BEARINGS WITH IMPROVED HALLOWERS | |
EP0000703B1 (en) | A self-aligning two row thrust roller bearing | |
JPS55163324A (en) | Constant velocity ball joint | |
US3765733A (en) | Bearing assembly | |
US3556618A (en) | Double race screwdown thrust bearing | |
US4429922A (en) | Antifriction axial guide means | |
US6132097A (en) | Roller bearing with means for giving the rollers a positive skew angle | |
GB1484392A (en) | Expansion bearing assembly for a converter carrying trunnion | |
US1915585A (en) | Roller bearing | |
US3206263A (en) | Cage for antifriction bearings | |
JPH09126233A (en) | Cross roller bearing | |
US6398417B1 (en) | Rolling member | |
US2859076A (en) | Roller bearing | |
EP1104855A1 (en) | Pure rolling bearing | |
JPS5855362B2 (en) | Bidirectional load type ball bearing | |
EP0158206B1 (en) | A ball bearing | |
GB2070154A (en) | Roller Bearings | |
SU619708A1 (en) | Radial thrust ball bearing | |
US1498571A (en) | Self-adjusting roller bearing | |
KR20000053421A (en) | Rolling bearing | |
US2401557A (en) | Bearing construction |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Designated state(s): DE FR GB |
|
17P | Request for examination filed | ||
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Designated state(s): DE FR GB |
|
REF | Corresponds to: |
Ref document number: 2860391 Country of ref document: DE Date of ref document: 19810319 |
|
PLBI | Opposition filed |
Free format text: ORIGINAL CODE: 0009260 |
|
26 | Opposition filed |
Opponent name: FAG KUGELFISCHER GEORG SCHAEFER & CO. Effective date: 19811029 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 19820726 Year of fee payment: 5 |
|
RDAG | Patent revoked |
Free format text: ORIGINAL CODE: 0009271 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: PATENT REVOKED |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 19830713 Year of fee payment: 6 |
|
27W | Patent revoked |
Effective date: 19830428 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee | ||
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |