GB1568579A - Creation of Inventions and Patents with Artificial Intelligence

GB1568579A – Taper roller bearings
– Google Patents

GB1568579A – Taper roller bearings
– Google Patents
Taper roller bearings

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Publication number
GB1568579A

GB1568579A
GB20047/77A
GB2004777A
GB1568579A
GB 1568579 A
GB1568579 A
GB 1568579A
GB 20047/77 A
GB20047/77 A
GB 20047/77A
GB 2004777 A
GB2004777 A
GB 2004777A
GB 1568579 A
GB1568579 A
GB 1568579A
Authority
GB
United Kingdom
Prior art keywords
bearing
roller
raceway
taper
axis
Prior art date
1976-05-13
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

Application number
GB20047/77A
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.)

SKF Industrial Trading and Development Co BV

Original Assignee
SKF Industrial Trading and Development Co BV
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.)
1976-05-13
Filing date
1977-05-12
Publication date
1980-06-04

1977-05-12
Application filed by SKF Industrial Trading and Development Co BV
filed
Critical
SKF Industrial Trading and Development Co BV

1980-06-04
Publication of GB1568579A
publication
Critical
patent/GB1568579A/en

Status
Expired
legal-status
Critical
Current

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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

F16C19/34—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

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

F16C19/225—Details of the ribs supporting the end 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

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

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

F16C2240/00—Specified values or numerical ranges of parameters; Relations between them

F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap

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

F16C2240/00—Specified values or numerical ranges of parameters; Relations between them

F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap

F16C2240/50—Crowning, e.g. crowning height or crowning radius

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

Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION

Y02T10/00—Road transport of goods or passengers

Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies

Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction

Description

PATENT SPECIFICATION
( 11) 1 568 579 ( 21) Application Np 20047/77 ( 31) Convention Application No.
( 22) Filed 12 May 1977 i 030 ( 32) Filed 13 May 1976 in ( 33) United States of America (US) ( 44) Complete Specification published 4 June 1980 ( 51) INT CL 3 F 16 C 19/36 ( 52) Index at acceptance F 2 A 5 C 8 5 CR D 36 ( 54) TAPER ROLLER BEARINGS ( 1) We, SKF INDUSTRIAL TRADING & DEVELOPMENT COMPANY B V, a Dutch company, of P O Box 50, Nieuwegein, the Netherlands do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:-
The present invention relates to tapered roller bearings.
Tapered roller bearings comprise an inner race ring or inner member or cone, an outer race ring or outer member or cup, and a plurality of frusto-conical rolling elements located therebetween thus facilitating relative rotation of the members about a bearing axis normal to the plane or path of relative movement of the members The inner member has a raceway surface which is tapered at a predetermined angle with respect to the bearing axis, and the outer member has a raceway surface which is tapered to another greater predetermined angle with respect to the bearing axis Conventionally, these bearings are designed so that, when subjected to the loads they are designed to carry, the taper angles have apexes with a common locus on the bearing axis, and the rotational axis of each rolling element also intersects the bearing axis at the aforementioned locus By virtue of this structure, pure rolling contact is assumed to exist between the rolling elements and the raceways of the inner and outer members when the bearing operates under load.
In the conventional tapered roller bearing, the rolling elements are contained in the annular space between the members by means of one or more flanges which engage one, or the other, or both of the opposite end faces of the rolling elements During operation of the bearing, the flange bears against an end face of the rolling element and, as a consequence, generates friction therebetween This friction tends to cause each rolling element to skew about an axis which is normal to its own rolling axis and which intersects the bearing axis.
When so skewed, each rolling element has an axially-directed component of sliding 50 motion to the inner and outer members.
In the conventional bearing, the axially directed sliding component and concomitant friction forces are usually codirectional with the axial loads applied to the respec 55 tive inner and outer members, so that the rolling elements are said to be skewed in a negative angular direction.
It has been determined that when a roller bearing operates with its rolling elements 60 disposed at negative skew angles, the bearing has higher friction and lower life than if it were to operate with the elements disposed at positive skew angles wherein components of the friction forces between the elements 65 and the members acting on the members counteract components of axial loads carried by those members.
According to the invention a taper roller bearing comprises an inner race ring, an 70 outer race ring and a plurality of taper rollers arranged to roll on the raceways of the race rings, such that when the bearing is in use and an external load is applied, the apex of the taper angle of each taper rol 75 ler is offset from the bearing axis and the axis of each taper roller is at a positive skew angle so that the axial component of friction on one of the raceways arising between the taper rollers and that raceway 80 opposes the axial component of the external load on that raceway.
When the apex of the taper angle of one of the taper rollers, the axis of that taper roller and the points of equal speed of that 85 taper roller and the raceways are projected onto and orthogonally with respect to a plane passing through that taper roller and in which plane lies the bearing axis, the projection of the apex may lie in a zone 90 00 W)o ( 19) -i% 2 pi DO 9.j -I’ l’f’4 ú 4 4 44 Ii CI A 4 f U I 1 ‘ I t I 9 ‘ I r :
1 1 1 1 z 1 1 1 ; F r – 1 I 1 2 ‘ V t’1 11 I:’ It’? 41 4:41, 4 I :1 III 4 4 ‘ f pf( 44; 4 I 142 ‘ Ik P 21 144 ‘4144141 ii I ‘ 2)) 44 2)42 -” 44 f ( U Pr’l, 14 pj, ”4 2 1 I 2.
ItUt:?ll I:4 4 j 4334 .
4 tv – P F 1 z ,f I 4 U.
I 1.’ 4 iii 4 $, 1 568 579 113.
The accelerating and retarding action on the roller 113 on opposite sides of its median M creates a moment on the roller 113 about the median M to skew the roller 113 counterclockwise The engagement of the roller 113 with the outer raceway 112 a, however, has an effect on the roller 113 which is opposite the effect produced by the inner raceway lila on the roller 113 That is, between the outer raceway 112 a and the roller 113, the zones of acceleration and deceleration are reversed, with the zone of acceleration being located to the right of the median M and the zone of deceleration being located to the left of the median M.
To cause the roller 113 to assume a positive skew angle, the inner member skew moment is made to predominate over the outer skew moment This is ensured by providing the inner raceway 11 la with a very shallow recess groove or relief llb located underneath and between the ends of the roller 113 adjacent its median M along the raceway so that the roller 113 engages the inner raceway on each side of the relief llb with greater contact pressure than adjacent its median M As an example, the relief is preferably of a depth equal to about one-half the elastic deformation of the contact, or in the region of about 0 00025 times the mean roller diameter The outer raceway 112 a, on the other hand, is provided with a pair of relieved surfaces 112 c and 112 d spaced outwardly of the median M thus providing a raised portion between the ends of the roller 113 so that the roller 113 engages the outer raceway 112 adjacent its median M while being spaced from (or engaging with a lower contact pressure) the raceway 112 adjacent its ends By virtue of this structure, the magnitude of the inner moment is made greater than the oppositely directed outer moment to skew the roller 113 as illustrated in Fig 4 It is noted that the reliefs 11 lb, 112 c and 112 d are greatly exaggerated for purposes of illustration.
In order to demonstrate how the present invention affects positioning of the rollers at positive skew angles during operation of the bearing under load, and with particular reference to Figs 3 and 4, the reader should view the roller 113 as stationary and the inner and outer members 111 and 112 rotating relative to one another in opposite directions in the manner shown with the inner member moving toward the reader and the outer member moving away from the reader Under these conditions, the speed of the inner raceway surface lila at the small (left) end of the roller 113 is higher than that of the roller surface 113 at that location Consequently, the tangential component fi, of the friction f, on the roller 113 has the same direction as the direction of movement of the inner ring; that is, toward the reader At the large end of the roller, the tangential component f,1 of the friction force is oppositely directed, since the peripheral speed of the roller 113 at that 70 location is greater than the peripheral speed of the inner raceway lila at the same location This results in a force couple or moment from the inner ring 111 on the roller 113 which tends to skew the roller 75 113 in the direction shown in Fig 4.
At the outer ring 112 there is a skewing moment in the opposite direction This is because the speed of the outer raceway 112 a adjacent the small end of the roller 113 is 80 higher than the speed of the surface of the roller 113 at that point Consequently, the tangential component f 3 t of the friction force fss on the roller 113 has the same direction as the direction of movement of the outer 85 ring; that is, away from the viewer At the large end of the roller 113, the tangential component f 3 t of the friction force f,2 is oppositely directed, since the roller surface speed is greater than the peripheral speed 90 of the outer raceway 112 The skewing moment of the outer ring 112 on the roller 113, is however, smaller than the inner ring 111 because the distance between the friction force components f,,t f,3 t is smaller than 95 the distance between the force components f.11, f,t as a consequence of the particular geometry of the raceway profiles The net result is that the inner ring moment dominates and skews the roller in the desired direction 100 illustrated.
When the roller 113 is skewed in the direction illustrated in Fig 4, the surface of the roller engaged with the inner raceway 1 la must slide axially rightward relative to the 105 raceway 1 la in order for the roller 113 to travel in the annular space between the members The roller 113 must slide axially in the opposite direction with respect to the outer raceway 112 a Because of this slid 110 ing, leftward friction forces fs,, f, develop on the underside of the roller 113, and rightward reaction friction forces f,,, f,2 develop on the inner raceway 11 la The friction forces fas f, have axial components fsa, 115 fle which act axially rightward on the inner member 111 to counteract the leftward axial component PIA of the external load P,.
In the same way, the rightward axial load component P 2, of the external load P, is 120 counteracted at the outer member 112 by the leftward axial component fs,, of the friction force fi, Thus, when the rolling axis A 2 of the roller 113 is not coplanar with the bearing axis Al, and these force condi 125 tions occur, the roller 113 is defined as being disposed at a positive skew angle and the aforementioned desirable consequences occur.
Because of the tapered shape of the rol 130 1 568 579 ling element, the right-hand end face of the rolling element always engages the flange or rib 114 with a force R,, which creates a reaction force Rrb, and the friction forces fa, fb are developed therebetween However, the magnitude of the friction forces are significantly reduced, because some of the flange to rolling element contact load is carried by the friction forces between the raceways and the rolling elements due to the positive skew This may be best understood by reference to Figs 9 a and 9 b, wherein the various forces acting in bearings operating with rollers under positive, negative and zero skew conditions are illustrated schematically.
For ease of presentation, an equilibrium force polygon is drawn for each rolling element Illustrating forces which would exist when the bearing configurations depicted in Figs 1, 3 and 5 are subjected to an axial load of Pl, per roller The broken line triangles in each figure represent the force polygons when the rollers are unskewed i e.
zero angle of skew The solid line polygons in each figure represent the force polygons when the rollers are skewed, either positively or negatively The relative magnitudes of the rib reaction forces Rrb in each figure should be noted.
In the case of the prior art bearing design (Figs 1 and 2), it has been established that the bearing normally operates with each rolling element disposed at a negative skew angle The effect of the resulting lateral friction or skid forces, fl and fir on the force equilibrium is shown in the uppermost figure, Fig 9 a, wherein these friction forces cause both the outer raceway and inner raceway normal forces No and N 1 respectively 4 o and the rib force Rrb to be greater with a negatively-skewed roller than with an unskewed roller Thus, a bearing operating in such a negatively-skewed mode has higher friction losses and poorer fatigue life than predicted on a basis of force magnitudes when skew is ignored Note in particular that the rib force Rb is increased, thus causing an increase in the roller skewing moment.
In a bearing designed according to the embodiment illustrated in Figs 3 and 4, the roller has a positive skew, and the resulting force polygon is illustrated in Fig 9 b It will be noted that the outer raceway and inner raceway normal forces N O and NI respectively and the rib reaction force R, are all less than they would be if the roller were unskewed Note, however, that the degree of apex displacement illustrated in Fig.
6 O 3 has been greatly exaggerated for ease of illustration Thus the corresponding polygon in Fig 9 b appears much broader based than the one in Fig 9 a However, the relative difference in magnitude of the rib reaction force Rrb is thus also exaggerated However, the tendency, in this embodiment, is to cause a slight increase in the magnitude of the rib force Rrb in the process of securing frictional skew moments with which to overcome the friction moment associated with 70 the rib force.
By way of example, a bearing constructed in accordance with Figs 3 and 4 would have an apex L, spaced radially outward of the bearing axis A, a distance of at least 0 005 75 times the mean diameter of the inner raceway It is noted, however, that because of the skew angle of the rolling element 113, the apex L, is located towards the reader out of the plane of the section of Fig 3 80 Another embodiment of the present invention is illustrated in Figs 5 and 6 The tapered roller bearing 210 illustrated therein comprises an inner member 211, an outer member 212, and a series of rolling ele 85 ments, such as the roller 213, mounted between the inner and outer members The bearing 210 has a bearing axis A, which is disposed normal to the path of relative movement of the rolling elements 213 be 90 tween the inner and outer members, and the rolling element 213 has a rotational axis A 2.
Fig 5 is also a projection onto end orthogonally with respect to a plane in 95 which lies the bearing axis A, and which passes through the tapered rolling element 113 Lines 216 and 217 lie in this plane and extend from the intersection L, of the projection of the roller axis A 2 with bearing 100 axis A, to the projection of the points of equal speed between taper rolling element 213 and the raceways 211 a and 212 a The lines 216 a and 217 a are the lines of taper of the rolling element 213 and the projection of 105 the apex L of the taper angle xl lies outside the zone defined by the lines 216 and 217.
Apex LU is offset radially from the bearing axis A, and the projection of the apex LI lies on the opposite side of the bearing axis 110 A, to the taper rolling element 213.
Line 216 a intersects the bearing axis A, at L, and subtends an angle a, and line 217 a intersects the bearing axis Al at L, and subtends an angle 72 Lines 216 and 217 subtend 115 an angle of 7, which is greater than angle The apex L: in this embodiment is located at a point out of the plane away from the reader whereas, in the embodiment of Fig 120 ures 3 and 4, the apex L is located at a point out of the plane towards the reader.
The theoretical lines of constant speed 216 and 217, which have the projection of their apex L, on the bearing axis A-, intersect 125 the lines 216 a and 217 a at the roller median M; however, because the projection of the apex L is located beyond the bearing axis A,, the locations of relative sliding motion between the roller 213 and the raceways 130 1 568 579 211 a and 212 q are the reverse of the locations in the embodiment of Figs 3 and 4.
For instance, between the inner raceway 211 a and the bottom of the roller 213, the zone of roller acceleration is located to the right of the roller median M and the zone of deceleration is located to the left thereof As a result, the skew moments from the outer and inner raceways change sign.
In this embodiment, to obtain positive skew, the skew moment provided by the outer member 212 must pre-dominate over the inner member 211 To this end, the outer raceway 212 a is provided with a central recess relief or shallow groove 212 b along the raceway, and the inner raceway 211 is provided with relieved surfaces 211 i and 211 d, located on opposite sides of the roller median M thus forming a raised portion along the raceways Thus, the roller 213 contacts the inner raceway 211 a adjacent the roller median M with higher contact pressure than it contacts the outer raceway 212 a The roller 213 engages the outer raceway 212 a on each side of the relief 212 b with greater contact pressure than adjacent its median M By virtue of this structure, the axial components Pl and P,& of the external loads Pl and P 2 on the inner and outer members respectively, are counteracted by axial components f,, and fs,, of friction force fs 2 and f,,, f, between the roller 213 and the raceways 21 la and 212 a in much the same manner as described in the embodiment of Figs 3 and 4 It is noted that the reliefs 21 Ic, 21 ld and 212 b are greatly exaggerated for purposes of illustration.
The advantages of the bearing design may be best understood by reference to the force polygon Fig 9 c As seen therein, the geometrical relations in this embodiment result in a polygon having a narrower base, indicating a reduction in the rib reaction force Rrb Also, there is a reduction in the outer raceway and inner raceway normal contact forces N, and N, respectively The extent of geometrical modifications needed for roller skew control is minimized with this design, since the reduction in the rib reaction force Rr, reduces the need for corrective skew moments to be applied to the roller.
Figures 7 and 8 illustrate further embodiments of the present invention These embodiments have certain geometric relations which are similar to those of the embodiments of Figs 3 and 4 and 5 and 6, respectively In the Fig 7 embodiment, the bearing 310 has an inner member 311, an outer member 312, and a roller 313 The projection of the apex L 2 of the frustoconical roller 313 is located off the bearing axis A, on the same side of the roller.
The apexes L, and L, of lines 316 a and 317 a on which lie raceways 311 a and 312 a, respectively, are located at approximately differing points on the bearing axis A, so that geometrical line contact is maintained between-the raceways and the roller In this instance, the apex L, of the outer raceway surface 312 a is located closer to the bear 70 ing than the apex L, of the inner raceway surface 311 a The desired roller skew is obtained by making the inner raceway surface 311 a rougher than the outer raceway surface 312 a Note that the projection of the 75 apex L is located inside the zone defined by the lines of equal speed 316 and 317.
In the Fig 8 embodiment, the bearing 410 has an inner member 411 and an outer member 412 and is designed with the pro 80 jection of the apex L, of the frusto-conical roller 413 located off the bearing axis A, a predetermined distance on the other side to the roller 413 The apexes L, and L, of lines 416 q and 417 a the two raceways 85 411 a and 412 a, respectively are located at two spaced points on the bearing axis so that geometrical line contact is maintained between the raceways and the roller In this embodiment, the apex L, of the outer race 90 way surface 412 a is located further from the bearing that the apex L, of the inner raceway surface 411 a The desired roller skew is obtained by making the outer raceway 412 a rougher than the inner raceway 411 a 95 Note that the projection of the apex L 2 is located outside the zone defined by the lines of equal speed 416 and 417.
Other embodiments of the present invention are illlustrated in Figs 10 to 13 In 100 these embodiments, one raceway is cylindrical and the other is tapered For instance, in the embodiment of Figs 10 and 11 the outer raceway is cylindrical and the inner raceway is tapered In the embodiment of 105 Figs 12 and 13, the outer raceway is tapered and the inner raceway is cylindrical.
Referring now to the embodiment illustrated in Figs 10 and 11, the desired roller skew is effected by causing the roller skew 110 ing moment produced by the outer cylindrical raceway to predominate over the roller skewing moment produced by the inner conical raceway In this bearing 510, the lines of equal peripheral speed 516 and 517 115 drawn through the roller median M intersect the bearing axis A, at the apex L, at which location the projection of the rotational axis A of the rolling element 513 also intersects the bearing axis A, The lines of 120 generation 516 a and 517 a of the inner and outer raceways 511 a and 512 a, respectively, intersect one another and the projection of the rolling element axis A 2 at another location L, which is inside the zone defined by 125 the equal speed lines 516 and 517 when the bearing is under load In this embodiment, it is noted that the path of relative motion of the inner and outer members 511 and 512 is between the apexes L, and L, 130 1 568 579 During operation of the bearing under load the portion of the roller 513 to the left of the median M at the inner raceway 511 a is accelerated by the inner raceway 511 a.
With the inner and outer members 511 and 512 moving in the directions indicated, the portion of the roller 513 to the right of the median M is retarded by the inner raceway 511 a This acceleration and retarding lo action produces a moment tending to skew the roller 513 counterclockwise looking downward in Fig 11 The zones of acceleration and retardation of the roller 513 are reversed with respect to the outer raceway 512 a, and the resulting moment generated by the outer raceway tends to skew the roller 513 clockwise In this embodiment, however, the moment produced by the outer raceway 512 a is greater than the moment produced by the inner raceway 511 a because of the shallow central recess, groove or relief 512 b provided in the outer raceway 512 a adjacent the roller median M and the raised portion formed by the pair of reliefs 511 c and 511 d in the inner raceway adjacent the ends of the roller 513 As in the previous embodiments, these reliefs are greatly exaggerated for purposes of illustration only.
The inner raceway 511 a engages the roller with a greater pressure adjacent the roller median M than the outer raceway at the same location, and the outer raceway engages the roller outboard of the median with a greater pressure than the inner raceway at the same location As a result, the roller 513 assumes the skew angle B (Fig.
11) When so skewed, friction forces f,3 and f., develop on the roller 513 and outer raceway 512 a, and friction forces f,, and f, develop on the roller 513 and inner raceway 51 la, respectively When the axial components of the friction forces f 2 and f,4 on the inner and outer raceways 51 la and 512 a, respectively, are directed as indicated in Fig.
10, i e, in directions counter to the directions of the axial load components P 2 and P,, of external load P 2 and P, and the roller axis A 2 is not coplanar with the bearing axis A,, the roller 513 is positively skewed As noted heretofore, when the roller is skewed positively, the bearing 510 operates with lower overall friction and a longer service life than does a similarly loaded bearing with a negatively skewed roller.
In the bearing 610 illustrated in Figs 12 and 13, the desired roller skew is achieved by causing the roller skewing moment produced by the outer raceway to predominate over the roller skewing moment produced by the inner raceway In this embodiment, the equal speed lines 616 and 617 intersect the bearing axis A, at an apex X The lines of generation 616 a and 617 a of the inner and outer raceways 611 a and 612 a, respectively, intersect one another at point L, when the bearing is under load The projection of the point 12 is located inside the zone defined between the equal speed lines 616 and 617 and is located on the projection of the rotational axis A, of the roller 613 In 70 this embodiment, the point L, is located between the point L 1 and the inner and outer members 611 and 612, as constrasted with the embodiment of Figs 10 and 11 wherein the points L, and L, are located on oppo 75 site sides of the bearing 510 Also, it is noted that the inner raceway 611 a is provided with a raised portion formed by surface reliefs 611 ic and 611 d outboard of the roller median M, and the outer raceway 612 a 80 is provided with a shallow recess relief or groove 612 b adjacent the roller median M.
These raceway surface reliefs, which are greatly exaggerated for purposes of illustration, cooperate with the roller 613 to cause 85 it to skew positively into the angle B indicated in Fig 13 when the inner and outer bearing members 611 and 612 rotate relative to one another in the directions indicated in Fig 12 and the bearing is under 90 load As in the other embodiments, the axial components of the friction forces f,2, and f,4 counteract axial components Pt A and P 2, of the external loads Pl and P 2, respectively to provide the advantages of positive skew 95

Claims (13)

WHAT WE CLAIM IS:-

1 A taper roller bearing comprising an inner race ring, an outer race ring and a 100 plurality of taper rollers arranged to roll on the raceways of the race rings, such that when the bearing is in use and an external load is applied, the apex of the taper angle of each taper roller is offset from the bear 105 ing axis and the axis of each taper roller is at a positive skew angle so that the axial component of friction on one of the raceways arising between the taper rollers and that raceway opposes the axial component 11 o of the external load on that raceway.

2 A bearing as claimed in claim 1 wherein when the apex of the taper angle of one of the taper rollers, the axis of that taper roller and the points of equal speed I 15 of that taper and the raceways are projected onto and orthogonally with respect to a plane passing through that taper roller and in which plane lies the bearing axis, the projection of the apex lies in a zone de 120 fined by the two lines lying in the plane and extending from the intersection of the projection of the roller axis with the bearing axis and passing through the projection of the points of equal speed 125

3 A bearing as claimed in claim 2 wherein the surface of the inner raceway has a higher coefficient of friction than the surface of the outer raceway.

4 A bearing as claimed in claim 2 or 130 1 568 579 claim 3 wherein the inner raceway has a recess extending along the raceway and lying between the ends of each taper roller.

A bearing as claimed in any of claims 2 to 4 wherein the outer raceway has a raised portion extending along the raceway and lying between the ends of each taper roller.

6 A bearing as claimed in any of the preceding claims wherein one of the raceways is tapered and the other is cylindrical.

7 A bearing as claimed in claim 1 wherein, when the apex of the taper angle of one of the taper rollers, the axis of that taper roller and the points of equal speed of that taper roller and the raceways are projected onto and orthogonally with respect to a plane passing through that taper roller and in which plane lies the bearing axis, the projection of the apex lies outside a zone defined by two lines lying in the plane and extending from the intersection of the projection of the roller axis with the bearing axis and passing through the projection of the points of equal speed.

8 A bearing as claimed in claim 7 wherein the surface of the outer raceway has a higher coefficient of friction than the surface of the inner raceway.

9 A bearing as claimed in claim 7 or 30 claim 8 wherein the outer raceway has a recess extending along the raceway and lying between the ends of each taper roller.

A bearing as claimed in any of claims 7 to 9 wherein the inner raceway 35 has a raised portion extending along the raceway and lying between the ends of each taper roller.

11 A bearing as claimed in any of the preceding claims wherein the apex of 40 the taper angle of each roller is spaced radially of the bearing axis a distance of at least 0 005 times the mean diameter of the inner raceway.

12 A taper roller bearing substantially 45 as hereinbefore described with reference to and as shown in Figs 3, 4 and 9 b or with reference to and as shown in Figs 5, 6 and 9 c or with reference to and as shown in Fig.
7, or with reference to and as shown in Fig 50 8, or with reference to and as shown in Figs.
and 11 or with reference to and as shown in Figs 12 and

13.
BOULT, WADVE & TENNANT Chartered Patent Agents 34 Cursitor Street, London, EC 4 A 1 PQ Printed for Her Majesty’s Stationery Office by The Tweeddale Press Ltd, Berwick-upon-Tweed, 1980.
Published at the Patent Office, 25 Southampton Buildings, London, WC 2 A l AY, from which copies may be obtained.
a

GB20047/77A
1976-05-13
1977-05-12
Taper roller bearings

Expired

GB1568579A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

US05/686,030

US4065191A
(en)

1976-05-13
1976-05-13
Roller skew control for tapered roller bearings

Publications (1)

Publication Number
Publication Date

GB1568579A
true

GB1568579A
(en)

1980-06-04

Family
ID=24754616
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB20047/77A
Expired

GB1568579A
(en)

1976-05-13
1977-05-12
Taper roller bearings

Country Status (6)

Country
Link

US
(1)

US4065191A
(en)

JP
(3)

JPS52151441A
(en)

DE
(1)

DE2720887A1
(en)

FR
(1)

FR2351305A1
(en)

GB
(1)

GB1568579A
(en)

IT
(1)

IT1125743B
(en)

Families Citing this family (29)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

SE410992B
(en)

1978-04-11
1979-11-19
Skf Ab

ROLLING STOCK

US4557613A
(en)

1978-09-01
1985-12-10
Skf Industries, Inc.
Spherical roller bearing having reciprocal crowning for skew control

JPS6123521U
(en)

1984-07-19
1986-02-12
光洋精工株式会社

roller bearing

KR940010978B1
(en)

1988-08-12
1994-11-21
갈소니꾸 가부시끼가이샤
Multi-flow type heat exchanger

JPH03113U
(en)

1989-05-22
1991-01-07

JP2562615Y2
(en)

1991-12-05
1998-02-16
日本精工株式会社

Tapered roller bearing

JP3359501B2
(en)

1995-07-24
2002-12-24
日本精工株式会社

Tapered roller bearing for pinion shaft support of differential gear

EP0756095B1
(en)

1995-07-24
1999-11-24
Nsk Ltd
Conical roller bearing for supporting a pinion shaft of a differential gear

US6328477B1
(en)

1998-11-27
2001-12-11
Ntn Corporation
Tapered roller bearings and gear shaft support devices

JP2003130059A
(en)

2001-10-19
2003-05-08
Koyo Seiko Co Ltd
Tapered roller bearing

JP4007260B2
(en)

2003-06-09
2007-11-14
株式会社ジェイテクト

Tapered roller bearing

EP1471271A3
(en)

2003-04-25
2005-11-30
Koyo Seiko Co., Ltd.
Tapered roller bearing and final reduction gear

DE102004055227A1
(en)

2004-11-17
2006-05-18
Fag Kugelfischer Ag & Co. Ohg

Tapered roller bearings

JP4592444B2
(en)

2005-02-25
2010-12-01
Ｎｔｎ株式会社

Tapered roller bearing

DE102006052043A1
(en)

2006-11-04
2008-05-08
Ab Skf

Raceway element and tapered roller bearing with the raceway element

DE102006052045A1
(en)

2006-11-04
2008-05-08
Ab Skf

Tapered roller bearing

DE102008021884A1
(en)

2008-05-02
2009-11-05
Schaeffler Kg

Tapered roller bearing and shaft bearing for at least one tapered roller bearing

DE102010011462A1
(en)

2010-03-15
2011-09-15
Schaeffler Technologies Gmbh & Co. Kg

Tapered roller bearing with profiled raceway

DE102010030648A1
(en)

2010-06-29
2011-12-29
Bayerische Motoren Werke Aktiengesellschaft
Taper roller bearing for use in e.g. wheel bearing of passenger car, has inner ring comprising ring outer side functioning bearing surface, where portion of surface of rolling element is provided with low-friction coating

RU2446323C1
(en)

2010-10-05
2012-03-27
Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования “Алтайский государственный технический университет им. И.И. Ползунова” (АлтГТУ)
Single-row spherical roller bearing

DE102012217505A1
(en)

2012-09-27
2012-12-06
Schaeffler Technologies AG & Co. KG
Bearing arrangement for gear transmission, has tapered roller bearing associated to shaft, where conical rolling elements are inserted in rolling element cage, and bearing outer ring is guided at conical outer track

DE102012217506B4
(en)

2012-09-27
2014-07-10
Schaeffler Technologies Gmbh & Co. Kg

Bearing arrangement for a transmission

EP4063677B1
(en)

2012-12-25
2023-06-14
NSK Ltd.
Tapered roller bearing

EP2982878B1
(en)

2013-04-04
2018-08-08
NSK Ltd.
Resin cage for tapered roller bearing and tapered roller bearing including the resin cage

EP3332137B1
(en)

2015-08-04
2019-06-26
Schaeffler Technologies AG & Co. KG
Angular contact roller bearing and method and device for the assembly thereof

DE102017113933A1
(en)

2017-06-23
2018-12-27
Schaeffler Technologies AG & Co. KG

Tapered roller bearing with corrected tread

JP6875971B2
(en)

2017-09-28
2021-05-26
Ntn株式会社

Cage for tapered roller bearings and tapered roller bearings

JP6804093B2
(en)

2017-12-20
2020-12-23
西部自動機器株式会社

Tapered roller moving method and tapered roller moving device

DE102019007309A1
(en)

2018-11-23
2020-05-28
Sew-Eurodrive Gmbh & Co Kg

Bearing system with one bearing and gearbox with one bearing system

Family Cites Families (2)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

SE365852B
(en)

1972-07-07
1974-04-01
Skf Ind Trading & Dev

JPS5761933B2
(en)

1972-07-07
1982-12-27
Esu Kee Efu Andeyusutoriaru Toreedeingu Ando Dev Co Bv

1976

1976-05-13
US
US05/686,030
patent/US4065191A/en
not_active
Expired – Lifetime

1977

1977-05-09
IT
IT23318/77A
patent/IT1125743B/en
active

1977-05-10
DE
DE19772720887
patent/DE2720887A1/en
not_active
Ceased

1977-05-11
FR
FR7714423A
patent/FR2351305A1/en
active
Granted

1977-05-12
GB
GB20047/77A
patent/GB1568579A/en
not_active
Expired

1977-05-13
JP
JP5445377A
patent/JPS52151441A/en
active
Granted

1986

1986-10-07
JP
JP61237274A
patent/JPS62110016A/en
active
Granted

1986-10-07
JP
JP61237275A
patent/JPS62110017A/en
active
Granted

Also Published As

Publication number
Publication date

FR2351305A1
(en)

1977-12-09

JPS6211203B2
(en)

1987-03-11

IT1125743B
(en)

1986-05-14

JPS62110017A
(en)

1987-05-21

JPS635608B2
(en)

1988-02-04

JPS52151441A
(en)

1977-12-15

US4065191A
(en)

1977-12-27

JPS62110016A
(en)

1987-05-21

JPS635609B2
(en)

1988-02-04

FR2351305B1
(en)

1982-01-29

DE2720887A1
(en)

1977-12-01

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