US20170321745A1 - Roller bearing assembly - Google Patents
Roller bearing assembly Download PDFInfo
- Publication number
- US20170321745A1 US20170321745A1 US15/522,942 US201415522942A US2017321745A1 US 20170321745 A1 US20170321745 A1 US 20170321745A1 US 201415522942 A US201415522942 A US 201415522942A US 2017321745 A1 US2017321745 A1 US 2017321745A1
- Authority
- US
- United States
- Prior art keywords
- roller
- bearing assembly
- raceway
- straight
- tapered
- 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.)
- Abandoned
Links
- 238000005096 rolling process Methods 0.000 claims abstract description 8
- 230000000712 assembly Effects 0.000 description 6
- 238000000429 assembly Methods 0.000 description 6
- 238000012986 modification Methods 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000007935 neutral effect Effects 0.000 description 2
- 238000004901 spalling Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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
-
- 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
- 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
- F16C19/361—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 cylindrical 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
-
- 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
-
- 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
- F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
-
- 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
- F16C33/64—Special methods of manufacture
-
- 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
-
- 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
- F16C2240/70—Diameters; Radii
- F16C2240/80—Pitch circle diameters [PCD]
- F16C2240/82—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD
- F16C2240/84—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD with full complement of balls or rollers, i.e. sum of clearances less than diameter of one rolling element
-
- 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
Definitions
- the present invention relates generally to roller bearing assemblies. More particularly, the present invention relates to a roller bearing assembly including straight rollers that can be utilized for applications in which tapered roller bearing assemblies are often used.
- roller bearing assemblies that can handle both axial and radial loads.
- roller bearing assemblies used in these applications include a plurality of tapered rollers disposed between a pair of inner and outer raceways, each of which is correspondingly angled, or tapered and meeting at an apex, with regard to a longitudinal center axis of the corresponding bearing assembly to allow for pure rolling.
- these assemblies are commonly referred to as tapered roller bearing assemblies.
- Tapered rollers are larger at one end as opposed to the other, and include a body that extends therebetween and is formed by a frustoconical outer surface.
- the outer surface of a tapered roller's body may be profiled in various applications. As would be expected, such tapered rollers can be difficult and time consuming to manufacture and, therefore, also expensive to manufacture.
- bearing assembly 10 such as the one shown in FIG. 9 , that utilizes a plurality of straight rollers 20 , that are relatively easy to manufacture as compared to tapered rollers, and rotatably received in a roller retainer 17 between a tapered inner cup 12 and a tapered outer cup 14 of the bearing assembly.
- inner cup 12 and outer cup 14 define an inner raceway 16 and outer raceway 18 , respectively, both of which are defined by frustoconical surfaces.
- FIG. 10A a portion of frustoconical outer raceway 18 is shown with a corresponding straight roller 20 when bearing assembly 10 is in the “at rest” position.
- each straight roller 20 When the bearing assembly is “at rest,” meaning there is no relative rotation between its tapered inner cup 12 and tapered outer cup 14 , each straight roller 20 may be in contact with both frustoconical inner raceway 16 and frustoconical outer raceway 18 along the entire length of the roller, as a longitudinal center axis 24 of each straight roller 20 intersects a longitudinal center axis 24 of the bearing assembly.
- each straight roller 20 will begin to rotate about its pivot axis 26 ( FIG. 9 ) that is both transverse to its longitudinal center axis 24 and extends outwardly from its midpoint to intersect longitudinal center axis 22 of the bearing assembly.
- This rotational motion about pivot axis 26 is driven by the tangential speeds of the roller's surfaces relative to their radial position on the inner and outer cups 12 and 14 , as best seen in FIGS. 10B and 9 .
- the full extent to which each straight roller 20 may rotate about its pivot axis 26 is limited by the dimensions of its corresponding retainer roller pocket 23 .
- each straight roller 20 rotates about its corresponding pivot axis 26 is due to the fact that its first end face 21 does not have as far to travel along outer raceway 18 as does its second end face 23 .
- second end face 23 would have to roll along “fast path” 17 of raceway faster than first end face 21 rolls along “slow path” 19 since fast path 17 is a larger circular path than is slow path 19 .
- “Neutral path” 21 represents the path that the midpoint of each straight roller 20 travels along outer raceway 18 .
- the present invention recognizes and addresses considerations of prior art constructions and methods.
- a roller bearing assembly in accordance with the present disclosure, includes a tapered inner cup defining an inner raceway, an tapered outer cup defining an outer raceway, the outer raceway having a convex profile, the convex profile being defined by an intersection of the outer raceway and a central plane in which a longitudinal center axis of the roller bearing assembly lies, and a plurality of straight rollers disposed between the tapered inner cup and the tapered outer cup so that each straight roller is in rolling contact with the inner raceway and the outer raceway, each straight roller having a first end face, a second end face and a cylindrical body extending therebetween.
- a roller bearing assembly in accordance with the present disclosure, includes an inner cup defining a tapered inner raceway, an outer cup defining a tapered outer raceway, the tapered outer raceway having a convex profile, the convex profile being defined by an intersection of the outer tapered raceway and a central plane in which a longitudinal center axis of the roller bearing assembly lies, a roller retainer having an inner perimeter, an outer perimeter and a frustoconically shaped body extending therebetween, the body defining a plurality of roller pockets, and a plurality of straight rollers disposed between the tapered inner cup and the tapered outer cup, each straight roller being disposed in a corresponding roller pocket of the roller retainer so that each straight roller is in rolling contact with the inner tapered raceway and the outer tapered raceway, each straight roller having a first end face, a second end face and a cylindrical body extending therebetween.
- FIG. 1 is a cross-sectional view of a roller bearing assembly in accordance with an embodiment of the present disclosure
- FIG. 2A is a partial top view of an outer cup and straight roller of the roller bearing assembly shown in FIG. 1 , wherein the straight roller is at rest;
- FIG. 2B is a partial top view of an outer cup and straight roller of the roller bearing assembly shown in FIG. 1 , wherein the straight roller is in motion;
- FIG. 3 is a partial view of the roller retainer and a corresponding straight roller of the roller bearing assembly shown in FIG. 1 ;
- FIG. 4 is a partial cross-sectional view of the roller bearing assembly shown in FIG. 2A , taken along line 4 - 4 ;
- FIG. 5 is a partial, cross-sectional view of the roller bearing assembly shown in FIG. 2B , taken along lines 5 - 5 ;
- FIG. 6 is an enlarged view of the indicated portion of the cross-sectional view of the roller bearing assembly shown in FIG. 1 ;
- FIG. 7 is a partial cross-sectional view of a second embodiment of a roller bearing assembly in accordance with the present disclosure, wherein the straight roller is at rest;
- FIG. 8 is a partial cross-sectional view of the second embodiment of a roller bearing assembly shown in FIG. 7 with the present disclosure, wherein the straight roller is in motion;
- FIG. 9 is a cross-sectional view of a prior art roller bearing assembly
- FIG. 10A is a partial top view of an outer cup and a straight roller of the prior art roller bearing assembly shown in FIG. 9 , wherein the straight roller is at rest;
- FIG. 10B is a partial top view of an outer cup and a straight roller of the prior art roller bearing assembly shown in FIG. 9 , wherein the straight roller is in motion;
- FIG. 11 is a partial view of the roller retainer and a corresponding straight roller of the prior art roller bearing assembly shown in FIG. 9 ;
- FIG. 12 is a partial cross-sectional view of the prior art roller bearing assembly shown in FIG. 10B , taken along line 12 - 12 .
- an embodiment of a roller bearing assembly 100 in accordance with the present disclosure includes a tapered inner cup 110 , a tapered outer cup 130 , a roller retainer 170 disposed therebetween that defines a plurality of roller pockets 178 , and a plurality of straight rollers 150 , each straight roller being rotatably received in a corresponding roller pocket 178 .
- Roller retainer 170 and straight rollers 150 are rotatably received between inner cup 110 and outer cup 130 such that each straight roller 150 is rotatably received between, and in rolling contact with, an inner raceway 118 and an outer raceway 138 defined by inner cup 110 and outer cup 130 , respectively.
- inner cup 110 and outer cup 130 are constructed using drawn cup technology, in alternate embodiments the inner cup and the outer cup may be precision ground cups. Additionally, as shown in FIG. 1 , an inner collar 180 defining a central shaft bore 182 is disposed radially inwardly of inner cup 110 and an outer collar 184 is disposed radially outwardly of outer cup 130 , to facilitate installation of bearing assembly.
- roller retainer 170 includes an annular first end member 172 , an annular second end member 174 , and a plurality of elongated central members 176 extending therebetween, thereby forming the plurality of roller pockets 178 .
- second end member 174 has a greater diameter than first end member 172
- central members 176 extend between first end member 172 and second end member 174 in a frustoconical fashion.
- a straight roller 150 is rotatably received in a corresponding roller pocket 178 , each straight roller 150 including a first end face 152 , a second end face 154 , and a cylindrical body extending therebetween.
- roller pockets 178 of roller retainer 170 are selected to limit the extent to which each corresponding straight roller 150 is allowed to rotate about its corresponding pivot axis 160 ( FIG. 1 ), as inner cup 110 and outer cup 130 rotate relative to each other, as discussed in greater detail below. Note, the dimensions of roller pocket 178 as shown in FIG. 3 are exaggerated, as is the extent to which straight roller 150 is able to rotate therein, for illustrative purposes only.
- inner cup 110 includes an annular inner flange 112 , and annular outer flange 114 , and a frustoconically shaped body 116 extending therebetween.
- the frustoconically shaped inner surface of body 116 is adjacent inner collar 180
- the frustoconically shaped outer surface of body 116 defines inner raceway 118 of roller bearing assembly 100 .
- outer cup 130 includes an annular inner flange 132 , an annular outer flange 134 , and a frustoconically shaped body 136 extending therebetween.
- the frustoconically shaped outer surface of body 136 is adjacent outer collar 184 .
- outer raceway 138 of bearing assembly 100 which is defined by the inner surface of the outer cup's body 136 , is not defined by frustoconical surface. Rather, outer raceway 138 defines a convex profile, as defined by the intersection of a plane of symmetry of rolling bearing assembly 100 , that being any plane in which a longitudinal center axis 101 of the bearing assembly lies, with outer raceway 138 of outer cup 130 . As such, as shown in FIGS.
- straight roller 150 when straight roller 150 is in the “at rest” position, that being when there is no relative motion between inner cup 110 and outer cup 130 and a longitudinal center axis 158 of straight roller 150 intersects longitudinal center axis 101 of roller bearing assembly 100 , straight roller 150 is in contact with inner raceway 118 along its entire length. However, due to the convex profile of outer raceway 138 , straight roller 150 is only in contact with outer raceway along a portion of its full length, that being a middle portion.
- each straight roller 150 will begin to rotate about its pivot axis 160 ( FIG. 1 ) that is both transverse to its longitudinal center axis 158 and extends outwardly from its midpoint to intersect longitudinal center axis 101 of the bearing assembly.
- This rotational motion about pivot axis 160 is best seen in FIGS. 2B and 5 .
- the full extent to which each straight roller 150 may rotate about its pivot axis 160 is limited by the dimensions of its corresponding roller pocket 178 , as shown in FIG. 3 .
- each straight roller 150 is due to the fact that its first end face 152 does not have as far to travel along outer raceway 138 as does its second end face 154 .
- second end face 154 would have to roll along “fast path” 142 of raceway faster than first end face 152 rolled along “slow path” 144 since fast path 142 is a larger circular path than is slow path 144 .
- “Neutral path” 146 represents the path that the midpoint of each straight roller 20 travels along outer raceway 138 .
- each straight roller 150 of the disclosed roller bearing assembly 100 maintains contact with outer raceway 138 as the straight roller rotates about its pivot axis 160
- the middle portion of each straight roller 20 in the prior art bearing assembly loses contact with outer raceway 18 , resulting in the end loading of the rollers.
- each straight roller 150 is in contact with outer raceway 138 than when the straight rollers are in the at rest position shown in FIGS. 2A and 4 . Therefore, the convex outer raceway 138 of the disclosed bearing assembly 100 leads to reduced end loading of straight rollers and, therefore, reduced spalling.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Manufacturing & Machinery (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
- The present invention relates generally to roller bearing assemblies. More particularly, the present invention relates to a roller bearing assembly including straight rollers that can be utilized for applications in which tapered roller bearing assemblies are often used.
- Various applications require roller bearing assemblies that can handle both axial and radial loads. Typically, roller bearing assemblies used in these applications include a plurality of tapered rollers disposed between a pair of inner and outer raceways, each of which is correspondingly angled, or tapered and meeting at an apex, with regard to a longitudinal center axis of the corresponding bearing assembly to allow for pure rolling. As such, these assemblies are commonly referred to as tapered roller bearing assemblies. Tapered rollers are larger at one end as opposed to the other, and include a body that extends therebetween and is formed by a frustoconical outer surface. As well, the outer surface of a tapered roller's body may be profiled in various applications. As would be expected, such tapered rollers can be difficult and time consuming to manufacture and, therefore, also expensive to manufacture.
- As such, it would be desirable to utilize a
bearing assembly 10, such as the one shown inFIG. 9 , that utilizes a plurality ofstraight rollers 20, that are relatively easy to manufacture as compared to tapered rollers, and rotatably received in aroller retainer 17 between a taperedinner cup 12 and a taperedouter cup 14 of the bearing assembly. As noted,inner cup 12 andouter cup 14 define aninner raceway 16 andouter raceway 18, respectively, both of which are defined by frustoconical surfaces. Referring additionally toFIG. 10A , a portion of frustoconicalouter raceway 18 is shown with a correspondingstraight roller 20 when bearingassembly 10 is in the “at rest” position. When the bearing assembly is “at rest,” meaning there is no relative rotation between its taperedinner cup 12 and taperedouter cup 14, eachstraight roller 20 may be in contact with both frustoconicalinner raceway 16 and frustoconicalouter raceway 18 along the entire length of the roller, as alongitudinal center axis 24 of eachstraight roller 20 intersects alongitudinal center axis 24 of the bearing assembly. - Note, however, as relative rotation occurs between
inner cup 12 andouter cup 14, eachstraight roller 20 will begin to rotate about its pivot axis 26 (FIG. 9 ) that is both transverse to itslongitudinal center axis 24 and extends outwardly from its midpoint to intersectlongitudinal center axis 22 of the bearing assembly. This rotational motion aboutpivot axis 26 is driven by the tangential speeds of the roller's surfaces relative to their radial position on the inner andouter cups FIGS. 10B and 9 . Note, the full extent to which eachstraight roller 20 may rotate about itspivot axis 26 is limited by the dimensions of its correspondingretainer roller pocket 23. Rotation of eachstraight roller 20 about itscorresponding pivot axis 26 is due to the fact that itsfirst end face 21 does not have as far to travel alongouter raceway 18 as does itssecond end face 23. For example, as shown inFIG. 10B , forstraight roller 20 not to rotate about itspivot axis 26,second end face 23 would have to roll along “fast path” 17 of raceway faster thanfirst end face 21 rolls along “slow path” 19 sincefast path 17 is a larger circular path than isslow path 19. Of course, this is not possible as all portions ofstraight roller 20 roll simultaneously. “Neutral path” 21 represents the path that the midpoint of eachstraight roller 20 travels alongouter raceway 18. - Referring now to
FIGS. 10B and 12 , the rotation ofstraight roller 12 about itspivot axis 26 causes frustoconicalouter raceway 20 to now function as though it has a concave profile with respect tolongitudinal center axis 24 of the straight roller. This concave profile is a hyperbolic conic section as defined by the plane running throughlongitudinal center axis 24 of the rotatedstraight rollers 20 and the points where first and second end faces 21 and 23 of the rollers contactouter raceway 18. As shown, this configuration leads to undesirable end loading ofstraight rollers 20 and, therefore, undesirable stress profiles for the straight rollers. Such end loading can lead to spalling and, ultimately, bearing failure within an unacceptable timeframe. - The present invention recognizes and addresses considerations of prior art constructions and methods.
- One embodiment of a roller bearing assembly, in accordance with the present disclosure, includes a tapered inner cup defining an inner raceway, an tapered outer cup defining an outer raceway, the outer raceway having a convex profile, the convex profile being defined by an intersection of the outer raceway and a central plane in which a longitudinal center axis of the roller bearing assembly lies, and a plurality of straight rollers disposed between the tapered inner cup and the tapered outer cup so that each straight roller is in rolling contact with the inner raceway and the outer raceway, each straight roller having a first end face, a second end face and a cylindrical body extending therebetween.
- Another embodiment of a roller bearing assembly, in accordance with the present disclosure, includes an inner cup defining a tapered inner raceway, an outer cup defining a tapered outer raceway, the tapered outer raceway having a convex profile, the convex profile being defined by an intersection of the outer tapered raceway and a central plane in which a longitudinal center axis of the roller bearing assembly lies, a roller retainer having an inner perimeter, an outer perimeter and a frustoconically shaped body extending therebetween, the body defining a plurality of roller pockets, and a plurality of straight rollers disposed between the tapered inner cup and the tapered outer cup, each straight roller being disposed in a corresponding roller pocket of the roller retainer so that each straight roller is in rolling contact with the inner tapered raceway and the outer tapered raceway, each straight roller having a first end face, a second end face and a cylindrical body extending therebetween.
- The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate one or more embodiments of the invention and, together with the description, serve to explain the principles of the invention.
- A full and enabling disclosure of the present invention, including the best mode thereof, directed to one of ordinary skill in the art, is set forth in the specification, which makes reference to the appended drawings, in which:
-
FIG. 1 is a cross-sectional view of a roller bearing assembly in accordance with an embodiment of the present disclosure; -
FIG. 2A is a partial top view of an outer cup and straight roller of the roller bearing assembly shown inFIG. 1 , wherein the straight roller is at rest; -
FIG. 2B is a partial top view of an outer cup and straight roller of the roller bearing assembly shown inFIG. 1 , wherein the straight roller is in motion; -
FIG. 3 is a partial view of the roller retainer and a corresponding straight roller of the roller bearing assembly shown inFIG. 1 ; -
FIG. 4 is a partial cross-sectional view of the roller bearing assembly shown inFIG. 2A , taken along line 4-4; -
FIG. 5 is a partial, cross-sectional view of the roller bearing assembly shown inFIG. 2B , taken along lines 5-5; -
FIG. 6 is an enlarged view of the indicated portion of the cross-sectional view of the roller bearing assembly shown inFIG. 1 ; -
FIG. 7 is a partial cross-sectional view of a second embodiment of a roller bearing assembly in accordance with the present disclosure, wherein the straight roller is at rest; -
FIG. 8 is a partial cross-sectional view of the second embodiment of a roller bearing assembly shown inFIG. 7 with the present disclosure, wherein the straight roller is in motion; -
FIG. 9 is a cross-sectional view of a prior art roller bearing assembly; -
FIG. 10A is a partial top view of an outer cup and a straight roller of the prior art roller bearing assembly shown inFIG. 9 , wherein the straight roller is at rest; -
FIG. 10B is a partial top view of an outer cup and a straight roller of the prior art roller bearing assembly shown inFIG. 9 , wherein the straight roller is in motion; -
FIG. 11 is a partial view of the roller retainer and a corresponding straight roller of the prior art roller bearing assembly shown inFIG. 9 ; and -
FIG. 12 is a partial cross-sectional view of the prior art roller bearing assembly shown inFIG. 10B , taken along line 12-12. - Repeat use of reference characters in the present specification and drawings is intended to represent same or analogous features or elements of the invention according to the disclosure.
- Reference will now be made in detail to presently preferred embodiments of the invention, one or more examples of which are illustrated in the accompanying drawings. Each example is provided by way of explanation, not limitation, of the invention. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in the present invention without departing from the scope and spirit thereof. For instance, features illustrated or described as part of one embodiment may be used on another embodiment to yield a still further embodiment. Thus, it is intended that the present invention covers such modifications and variations as come within the scope of the appended claims and their equivalents.
- Referring now to the figures, as shown in
FIGS. 1 and 6 , an embodiment of a roller bearingassembly 100 in accordance with the present disclosure includes a taperedinner cup 110, a taperedouter cup 130, aroller retainer 170 disposed therebetween that defines a plurality ofroller pockets 178, and a plurality ofstraight rollers 150, each straight roller being rotatably received in acorresponding roller pocket 178.Roller retainer 170 andstraight rollers 150 are rotatably received betweeninner cup 110 andouter cup 130 such that eachstraight roller 150 is rotatably received between, and in rolling contact with, aninner raceway 118 and anouter raceway 138 defined byinner cup 110 andouter cup 130, respectively. Note, althoughinner cup 110 andouter cup 130, as shown, are constructed using drawn cup technology, in alternate embodiments the inner cup and the outer cup may be precision ground cups. Additionally, as shown inFIG. 1 , aninner collar 180 defining a central shaft bore 182 is disposed radially inwardly ofinner cup 110 and anouter collar 184 is disposed radially outwardly ofouter cup 130, to facilitate installation of bearing assembly. - Referring now to
FIG. 3 , in the embodiment shown,roller retainer 170 includes an annularfirst end member 172, an annularsecond end member 174, and a plurality of elongatedcentral members 176 extending therebetween, thereby forming the plurality of roller pockets 178. Referring additionally toFIG. 1 , in thatsecond end member 174 has a greater diameter thanfirst end member 172,central members 176 extend betweenfirst end member 172 andsecond end member 174 in a frustoconical fashion. Astraight roller 150 is rotatably received in acorresponding roller pocket 178, eachstraight roller 150 including afirst end face 152, asecond end face 154, and a cylindrical body extending therebetween. The dimensions of roller pockets 178 ofroller retainer 170 are selected to limit the extent to which each correspondingstraight roller 150 is allowed to rotate about its corresponding pivot axis 160 (FIG. 1 ), asinner cup 110 andouter cup 130 rotate relative to each other, as discussed in greater detail below. Note, the dimensions ofroller pocket 178 as shown inFIG. 3 are exaggerated, as is the extent to whichstraight roller 150 is able to rotate therein, for illustrative purposes only. - As best seen in
FIG. 6 ,inner cup 110 includes an annularinner flange 112, and annularouter flange 114, and a frustoconically shapedbody 116 extending therebetween. The frustoconically shaped inner surface ofbody 116 is adjacentinner collar 180, whereas the frustoconically shaped outer surface ofbody 116 definesinner raceway 118 ofroller bearing assembly 100. Similarly,outer cup 130 includes an annularinner flange 132, an annularouter flange 134, and a frustoconically shapedbody 136 extending therebetween. As well, the frustoconically shaped outer surface ofbody 136 is adjacentouter collar 184. Note, however,outer raceway 138 of bearingassembly 100, which is defined by the inner surface of the outer cup'sbody 136, is not defined by frustoconical surface. Rather,outer raceway 138 defines a convex profile, as defined by the intersection of a plane of symmetry of rollingbearing assembly 100, that being any plane in which alongitudinal center axis 101 of the bearing assembly lies, withouter raceway 138 ofouter cup 130. As such, as shown inFIGS. 2A and 4 , whenstraight roller 150 is in the “at rest” position, that being when there is no relative motion betweeninner cup 110 andouter cup 130 and alongitudinal center axis 158 ofstraight roller 150 intersectslongitudinal center axis 101 ofroller bearing assembly 100,straight roller 150 is in contact withinner raceway 118 along its entire length. However, due to the convex profile ofouter raceway 138,straight roller 150 is only in contact with outer raceway along a portion of its full length, that being a middle portion. - However, as relative rotation occurs between
inner cup 110 andouter cup 130, eachstraight roller 150 will begin to rotate about its pivot axis 160 (FIG. 1 ) that is both transverse to itslongitudinal center axis 158 and extends outwardly from its midpoint to intersectlongitudinal center axis 101 of the bearing assembly. This rotational motion aboutpivot axis 160 is best seen inFIGS. 2B and 5 . Note, the full extent to which eachstraight roller 150 may rotate about itspivot axis 160 is limited by the dimensions of itscorresponding roller pocket 178, as shown inFIG. 3 . As previously noted, the rotation of eachstraight roller 150 about itscorresponding pivot axis 160 is due to the fact that itsfirst end face 152 does not have as far to travel alongouter raceway 138 as does itssecond end face 154. For example, as shown inFIG. 2B , forstraight roller 150 not to rotate about itspivot axis 160,second end face 154 would have to roll along “fast path” 142 of raceway faster thanfirst end face 152 rolled along “slow path” 144 sincefast path 142 is a larger circular path than isslow path 144. Of course, this is not possible as all portions ofstraight roller 20 roll simultaneously. “Neutral path” 146 represents the path that the midpoint of eachstraight roller 20 travels alongouter raceway 138. - Referring now to
FIGS. 2B and 5 , unlike the previously discussed priorart bearing assembly 10 shown inFIGS. 9 through 12 , the rotation of eachstraight roller 150 about itspivot axis 160 causes convexouter raceway 130 to now function as though it has a straight profile with respect tolongitudinal center axis 158 of the straight roller. Specifically, the middle portion of eachstraight roller 150 of the disclosedroller bearing assembly 100 maintains contact withouter raceway 138 as the straight roller rotates about itspivot axis 160, whereas the middle portion of eachstraight roller 20 in the prior art bearing assembly loses contact withouter raceway 18, resulting in the end loading of the rollers. As such, as the rotation of the disclosedstraight rollers 150 causes their end portions to come into contact withouter raceway 138, an even greater portion of eachstraight roller 150 is in contact withouter raceway 138 than when the straight rollers are in the at rest position shown inFIGS. 2A and 4 . Therefore, the convexouter raceway 138 of the disclosedbearing assembly 100 leads to reduced end loading of straight rollers and, therefore, reduced spalling. - While one or more preferred embodiments of the invention are described above, it should be appreciated by those skilled in the art that various modifications and variations can be made in the present invention without departing from the scope and spirit thereof. It is intended that the present invention cover such modifications and variations as come within the scope and spirit of the appended claims and their equivalents.
Claims (12)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US2014/063659 WO2016072963A1 (en) | 2014-11-03 | 2014-11-03 | Roller bearing assembly |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2014/063659 A-371-Of-International WO2016072963A1 (en) | 2014-11-03 | 2014-11-03 | Roller bearing assembly |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/933,530 Continuation US11885373B2 (en) | 2014-11-03 | 2020-07-20 | Roller bearing assembly |
Publications (1)
Publication Number | Publication Date |
---|---|
US20170321745A1 true US20170321745A1 (en) | 2017-11-09 |
Family
ID=51905423
Family Applications (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/522,942 Abandoned US20170321745A1 (en) | 2014-11-03 | 2014-11-03 | Roller bearing assembly |
US16/933,530 Active US11885373B2 (en) | 2014-11-03 | 2020-07-20 | Roller bearing assembly |
US18/535,723 Pending US20240133425A1 (en) | 2014-11-03 | 2023-12-11 | Roller bearing assembly |
Family Applications After (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/933,530 Active US11885373B2 (en) | 2014-11-03 | 2020-07-20 | Roller bearing assembly |
US18/535,723 Pending US20240133425A1 (en) | 2014-11-03 | 2023-12-11 | Roller bearing assembly |
Country Status (6)
Country | Link |
---|---|
US (3) | US20170321745A1 (en) |
EP (1) | EP3215751B1 (en) |
JP (1) | JP6793128B2 (en) |
KR (1) | KR20170066490A (en) |
CN (1) | CN107076200B (en) |
WO (1) | WO2016072963A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11885373B2 (en) | 2014-11-03 | 2024-01-30 | Jtekt Bearings North America Llc | Roller bearing assembly |
Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH117835A (en) * | 1925-07-04 | 1926-12-01 | Hugo Drotschmann | Roller bearings. |
US2859076A (en) * | 1955-09-27 | 1958-11-04 | Edwin T Lorig | Roller bearing |
US3572860A (en) * | 1969-06-19 | 1971-03-30 | Gen Motors Corp | Modified cylindrical roller bearing |
US3740108A (en) * | 1971-11-15 | 1973-06-19 | Skf Ind Trading & Dev | Cylindrical roller bearing |
US4403813A (en) * | 1981-10-14 | 1983-09-13 | The United States Of America As Represented By The Secretary Of The Air Force | Roller bearing cage design |
US5005988A (en) * | 1990-03-28 | 1991-04-09 | Thomson Industries, Inc. | Linear motion bearing |
CA2093648A1 (en) * | 1991-08-09 | 1993-02-10 | Nobuo Takata | Antifriction roller bearing |
US5902022A (en) * | 1996-06-28 | 1999-05-11 | The Torrington Company | Controlled contact stress roller bearing |
US6315458B1 (en) * | 1998-06-19 | 2001-11-13 | Nsk Ltd. | Roller bearing |
US6767135B2 (en) * | 2001-09-19 | 2004-07-27 | Nippon Thompson Co., Ltd. | Roller bearing cage |
US6832971B2 (en) * | 2002-02-18 | 2004-12-21 | Nissan Motor Co., Ltd. | Toroidal continuously variable transmission |
DE102005058149A1 (en) * | 2005-12-06 | 2007-07-05 | Schaeffler Kg | Tapered roller bearings with curved raceways |
US20140270616A1 (en) * | 2011-08-11 | 2014-09-18 | Ntn Corporation | Tapered roller bearing and mounting structure thereof |
US20160160914A1 (en) * | 2013-07-19 | 2016-06-09 | The Timken Company | Relief contour for a roller bearing |
US20160245335A1 (en) * | 2014-04-08 | 2016-08-25 | Nrb Bearings Ltd. | An Improved Roller Bearing with Enhanced Stress Bearing Capacity |
US9447821B2 (en) * | 2011-12-13 | 2016-09-20 | Koyo Bearings North America, LLC | Bearing outer race |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR397201A (en) | 1908-12-08 | 1909-05-03 | Gustave Jules Tresca | Automotive car hub |
FR479207A (en) * | 1914-07-16 | 1916-03-01 | Skf Svenska Kullagerfab Ab | Roller bearings improvements |
FR517696A (en) * | 1919-06-28 | 1921-05-10 | Nordiska Kullager Ab | Improvements to anti-friction roller bearings |
FR897201A (en) * | 1942-04-13 | 1945-03-15 | Adjustable roller bearing | |
CH348580A (en) * | 1956-12-28 | 1960-08-31 | Pitner Alfred | Method of manufacturing a needle bearing ring and ring obtained by this process |
JP2857220B2 (en) * | 1990-04-23 | 1999-02-17 | テイエチケー株式会社 | Rolling roller bearing |
DE4114374C2 (en) | 1991-05-02 | 2003-06-05 | Hauni Werke Koerber & Co Kg | Method and device for wrapping a strand of the tobacco processing industry |
US5322374A (en) * | 1991-08-09 | 1994-06-21 | Nobuo Takata | Antifriction roller bearing |
US6354745B1 (en) * | 1999-09-16 | 2002-03-12 | The Timken Company | Fully self-aligning roller bearing |
JP2001173665A (en) * | 1999-12-20 | 2001-06-26 | Nsk Ltd | Roller bearing |
JP2008240965A (en) * | 2007-03-28 | 2008-10-09 | Jtekt Corp | Drawn-cup roller bearing |
CN101649860B (en) * | 2009-09-07 | 2011-12-28 | 浙江兆丰机电股份有限公司 | Tapered roller drive wheel hub bearing unit |
US20120082407A1 (en) * | 2010-10-01 | 2012-04-05 | Amsted Rail Company, Inc. | Railway car bearing seal spacer assembly |
US20170321745A1 (en) | 2014-11-03 | 2017-11-09 | Koyo Bearings North America Llc | Roller bearing assembly |
-
2014
- 2014-11-03 US US15/522,942 patent/US20170321745A1/en not_active Abandoned
- 2014-11-03 KR KR1020177011498A patent/KR20170066490A/en not_active IP Right Cessation
- 2014-11-03 WO PCT/US2014/063659 patent/WO2016072963A1/en active Application Filing
- 2014-11-03 JP JP2017543704A patent/JP6793128B2/en active Active
- 2014-11-03 EP EP14799942.9A patent/EP3215751B1/en active Active
- 2014-11-03 CN CN201480083148.4A patent/CN107076200B/en active Active
-
2020
- 2020-07-20 US US16/933,530 patent/US11885373B2/en active Active
-
2023
- 2023-12-11 US US18/535,723 patent/US20240133425A1/en active Pending
Patent Citations (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH117835A (en) * | 1925-07-04 | 1926-12-01 | Hugo Drotschmann | Roller bearings. |
US2859076A (en) * | 1955-09-27 | 1958-11-04 | Edwin T Lorig | Roller bearing |
US3572860A (en) * | 1969-06-19 | 1971-03-30 | Gen Motors Corp | Modified cylindrical roller bearing |
US3740108A (en) * | 1971-11-15 | 1973-06-19 | Skf Ind Trading & Dev | Cylindrical roller bearing |
US4403813A (en) * | 1981-10-14 | 1983-09-13 | The United States Of America As Represented By The Secretary Of The Air Force | Roller bearing cage design |
US5005988A (en) * | 1990-03-28 | 1991-04-09 | Thomson Industries, Inc. | Linear motion bearing |
CA2093648A1 (en) * | 1991-08-09 | 1993-02-10 | Nobuo Takata | Antifriction roller bearing |
US5902022A (en) * | 1996-06-28 | 1999-05-11 | The Torrington Company | Controlled contact stress roller bearing |
US6315458B1 (en) * | 1998-06-19 | 2001-11-13 | Nsk Ltd. | Roller bearing |
US6767135B2 (en) * | 2001-09-19 | 2004-07-27 | Nippon Thompson Co., Ltd. | Roller bearing cage |
US6832971B2 (en) * | 2002-02-18 | 2004-12-21 | Nissan Motor Co., Ltd. | Toroidal continuously variable transmission |
DE102005058149A1 (en) * | 2005-12-06 | 2007-07-05 | Schaeffler Kg | Tapered roller bearings with curved raceways |
US20140270616A1 (en) * | 2011-08-11 | 2014-09-18 | Ntn Corporation | Tapered roller bearing and mounting structure thereof |
US9447821B2 (en) * | 2011-12-13 | 2016-09-20 | Koyo Bearings North America, LLC | Bearing outer race |
US20160160914A1 (en) * | 2013-07-19 | 2016-06-09 | The Timken Company | Relief contour for a roller bearing |
US9777767B2 (en) * | 2013-07-19 | 2017-10-03 | The Timken Company | Relief contour for a roller bearing |
US20160245335A1 (en) * | 2014-04-08 | 2016-08-25 | Nrb Bearings Ltd. | An Improved Roller Bearing with Enhanced Stress Bearing Capacity |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11885373B2 (en) | 2014-11-03 | 2024-01-30 | Jtekt Bearings North America Llc | Roller bearing assembly |
Also Published As
Publication number | Publication date |
---|---|
WO2016072963A1 (en) | 2016-05-12 |
US11885373B2 (en) | 2024-01-30 |
US20200347878A1 (en) | 2020-11-05 |
JP6793128B2 (en) | 2020-12-02 |
JP2017534037A (en) | 2017-11-16 |
EP3215751B1 (en) | 2021-04-28 |
CN107076200A (en) | 2017-08-18 |
EP3215751A1 (en) | 2017-09-13 |
US20240133425A1 (en) | 2024-04-25 |
KR20170066490A (en) | 2017-06-14 |
CN107076200B (en) | 2023-02-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20240133425A1 (en) | Roller bearing assembly | |
US9683605B2 (en) | Tapered roller bearing | |
US10054164B2 (en) | Rolling bearing | |
US20120251025A1 (en) | Angular contact ball bearing, in particular a spindle bearing, having improved cage guidance | |
JP2019044975A (en) | Tapered roller bearing | |
CN111164318B (en) | Thrust bearing retainer with shortened flange | |
US20130202239A1 (en) | Turning bearing with loading hole for introduction of separator with roller | |
US20090154860A1 (en) | Tapered roller bearing | |
JP2012202453A (en) | Self-aligning roller bearing | |
US20170102032A1 (en) | Low friction ball bearing cage design with optimized contact surface | |
US9133879B2 (en) | Turning bearing with rollers between outer ring and inner ring | |
CN107044481A (en) | Roller bearing | |
US9909620B2 (en) | Radial roller cage with centerline guidance | |
KR101864611B1 (en) | Ball bearing | |
CN110439923A (en) | A kind of three column combination bearings | |
JP2015230023A (en) | Double-row cylindrical roller bearing | |
US8529137B2 (en) | Radial bearing cage with contact feature | |
JP2019173918A (en) | Four-point contact ball bearing and cage for ball bearing using the same | |
KR101352166B1 (en) | A low torque bearing | |
JP2013053716A (en) | Self-aligning roller bearing and turning wheel support structure | |
US20170058948A1 (en) | Tapered roller bearing with reduced friction | |
JP2008133851A (en) | Roller bearing | |
JP2018184999A (en) | Tapered roller bearing | |
JP2017150560A (en) | Constant velocity joint | |
KR20160101882A (en) | A plastic cage for taper roller bearing |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: KOYO BEARINGS NORTH AMERICA LLC, OHIO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:ABRAHAMSON, SCOTT;REEL/FRAME:042176/0650 Effective date: 20150116 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STCV | Information on status: appeal procedure |
Free format text: NOTICE OF APPEAL FILED |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |
|
AS | Assignment |
Owner name: JTEKT BEARINGS NORTH AMERICA LLC, SOUTH CAROLINA Free format text: CHANGE OF NAME;ASSIGNOR:KOYO BEARINGS NORTH AMERICA LLC;REEL/FRAME:066641/0564 Effective date: 20230401 |