WO2007078616A2 - Roulement à rouleaux coniques et procédé de fabrication - Google Patents

Roulement à rouleaux coniques et procédé de fabrication Download PDF

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Publication number
WO2007078616A2
WO2007078616A2 PCT/US2006/046984 US2006046984W WO2007078616A2 WO 2007078616 A2 WO2007078616 A2 WO 2007078616A2 US 2006046984 W US2006046984 W US 2006046984W WO 2007078616 A2 WO2007078616 A2 WO 2007078616A2
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WO
WIPO (PCT)
Prior art keywords
tapered
tapered bearing
ring
inner ring
assembly
Prior art date
Application number
PCT/US2006/046984
Other languages
English (en)
Other versions
WO2007078616A3 (fr
Inventor
Daniel R. Mclarty
John S. Hayward
Thomas R. Bober
Original Assignee
Timken Us Corporation
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.)
Filing date
Publication date
Application filed by Timken Us Corporation filed Critical Timken Us Corporation
Publication of WO2007078616A2 publication Critical patent/WO2007078616A2/fr
Publication of WO2007078616A3 publication Critical patent/WO2007078616A3/fr

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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
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
    • 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
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • 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
    • F16C33/588—Races of sheet metal
    • 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
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Definitions

  • the present invention relates to tapered bearings and a method for manufacturing tapered bearings.
  • Tapered bearings are known in the art, and include four main components, the inner ring, outer ring, rolling elements and the rolling element retainer or cage. Tapered bearings are distinguished from other designs by the rolling elements having a tapered profile rather than being straight cylinders and the raceways having a slope. These geometries allow the bearing to accommodate thrust loads.
  • tapered bearings are manufactured using a method of machining the inner and outer rings.
  • the present invention provides an improved method of manufacturing tapered bearing rings in which complex and expensive machining operations to create the tapered raceway surfaces are eliminated.
  • the invention also includes various applications for the bearings made with the improved method of the invention.
  • the invention provides a tapered bearing configured to rotatably support a shaft within a housing.
  • the tapered bearing includes a plurality of rolling elements, an inner ring including a tapered raceway, an outer ring including a tapered raceway, and an insert coupled to the shaft.
  • the inner ring conforms to a surface of the insert when: the tapered bearing is loaded and the outer ring conforms to a surface of the housing when the tapered bearing is loaded.
  • the invention provides a tapered bearing assembly that includes a shaft, a housing, a plurality of rolling elements, an insert coupled to the shaft, an inner ring including a tapered raceway, and an outer ring including a tapered raceway.
  • the inner ring conforms to a surface of the insert when the tapered bearing assembly is loaded and the outer ring conforms to a surface of the housing when the tapered bearing assembly is loaded.
  • the invention provides a wheel hub assembly that includes a housing, a hub, a shaft coupled to the hub, and a tapered bearing assembly configured to rotatably support the hub within the housing.
  • the tapered bearing includes a plurality of rolling elements, an inner ring including a tapered raceway, and an outer ring including a tapered raceway. The inner ring conforms to the hub when the wheel hub assembly is loaded and the outer ring conforms to the housing when the wheel hub assembly is loaded.
  • the invention provides a spindle assembly that includes a housing, a shaft, and a tapered bearing assembly configured to rotatably support the shaft within the housing.
  • the tapered bearing includes a plurality of rolling elements, an inner ring including a tapered raceway, and an outer ring including a tapered raceway. The inner ring conforms to the shaft when the spindle assembly is loaded and the outer ring conforms to the housing when the spindle assembly is loaded.
  • the invention provides a method of manufacturing a tapered bearing that includes an inner ring and an outer ring.
  • the method includes providing a die cavity configured to receive a forming die, providing a substantially circular ring, and placing the ring within the die cavity.
  • the method further includes pressing the forming die into the ring to form an element, removing the element from the die cavity, and separating the element into the inner ring and the outer ring.
  • the invention provides a method of manufacturing a tapered bearing including an inner ring and an outer ring.
  • the method includes providing a blank, stamping the blank to form an element, and separating the element into the inner ring and the outer ring of the tapered bearing such that each ring defines a respective tapered raceway of the tapered bearing.
  • Fig. 1 is a section view of one embodiment of a tapered bearing with cylindrical rolling elements embodying the present invention.
  • Fig. 2 is an enlarged partial section view of the tapered bearing of Fig. 1.
  • Figs. 3A-3G illustrate a method of manufacturing the tapered bearing of Fig. 1.
  • Fig. 4 is a section view of an alternative embodiment of a tapered bearing with tapered rolling elements.
  • Figs. 5A-5D illustrate a method of manufacturing the tapered bearing of Fig. 4.
  • Fig. 6 is an enlarged partial section view of an alternative embodiment of the tapered bearing of Fig. 4.
  • Fig. 7 is an enlarged partial section view of yet another alternative embodiment of the tapered bearing of Fig. 4.
  • Fig. 8 is yet another alternative embodiment of the tapered bearing of Fig. 4.
  • Fig. 9 is yet another alternative embodiment of the tapered bearing of Fig. 4.
  • Fig. 10 is an exploded view of a wheel hub illustrating one application of the tapered bearing of Fig. 4.
  • Fig. 11 is a section view of the wheel hub of Fig. 10.
  • Fig. 12 is a section view of an alternative embodiment of the wheel hub of Fig. 10
  • Fig. 13 is a perspective view of yet another application of the tapered bearing of Fig. 4.
  • the illustrated tapered bearing 20 includes an outer ring 22, an inner ring 24, a cage 26, and rolling elements 28.
  • the cage 26 could be eliminated.
  • the outer ring 22 includes a tapered outer raceway 30, the taper generally defining a cup angle a.
  • the outer raceway 30 supports the rolling elements 28 and provides a path on which the rolling elements 28 traverse.
  • the outer raceway 30 may include a crowned surface profile, the purpose of which will be discussed below.
  • the outer ring 22 further includes an outer surface 32 that is generally cylindrically shaped and generally concentric around a shaft centerline 34.
  • the outer surface 32 is typically received and supported by a housing 36.
  • the outer ring 22 can be formed from steel, including low carbon steel, or any other suitable material.
  • the inner ring 24 includes a tapered inner raceway 38, the taper generally defining a cone angle ⁇ .
  • the inner raceway 38 supports the rolling elements 28 and provides a path on which the rolling elements 28 traverse. Similar to the outer raceway 30, the inner raceway 38 may also include a crowned surface profile.
  • the inner raceway 38, the outer raceway 30, or both, can have the crowned profile. Providing at least one crowned profile on a raceway helps prevent edge loading of the rolling elements 28 if the cone angle ⁇ and the cup angle a differ a small amount.
  • the inner ring 24 further includes an inner surface 40.
  • the inner surface 40 is generally cylindrically shaped and generally concentric around the shaft centerline 34.
  • a shaft 42 is positioned through a bore 44 defined by the inner surface 40 of the tapered bearing 20.
  • the inner ring 24 includes a first flange 46 and a second flange 48 that prevent the rolling elements 28 and the cage 26 from sliding off of the inner raceway 38 axially while the tapered bearing 20 is in operation.
  • the inner ring 24 can be formed from steel, including low carbon steel, or any other suitable material.
  • the cage 26 retains and positions the rolling elements 28.
  • Each rolling element 28 is placed in a pocket (not shown) that maintains a substantially equal distance between the rolling elements 28.
  • the number of pockets is equal to the number of rolling elements 28. Any number of rolling elements 28 or pockets can be used, depending on the application of the tapered bearing 20.
  • the rolling elements 28 roll along the inner raceway 38 and outer raceway 30. While the illustrated tapered bearing 20 of Fig. 1 is shown with cylindrical rolling elements 28, it should be understood that tapered rolling elements can also be employed, in which case flanges 48 will absorb the resultant thrust on rollers 28.
  • Figs. 3A — 3G display one method of manufacturing the tapered bearing 20 illustrated in Fig. 1.
  • the method includes forming a ring 50 by a wrap and weld method (see Fig. 3A).
  • the ring 50 is preferably formed from low carbon steel since the low carbon content will allow for a weld of high integrity and avoid excess hardening in the weld.
  • any suitable material can be utilized for forming the ring 50, such as plain steel or aluminum.
  • a washer stamped from strip stock can be utilized.
  • the method of forming the ring 50 may additionally include de-flashing the weld. This is simplified by the use of the low carbon material since the weld should be relatively soft. In addition, due to the later forming step utilized, the weld tends to remain at the outermost areas of the ring 50, not in what will eventually be the inner raceway 38 and the outer raceway 30. Thus, de-flashing the weld is less critical than would otherwise be the case. Critical areas of the weld can, if desired, undergo an optional double disk grind operation to supplement the de-flashing process.
  • the inner ring 24 and the outer ring 22 of the tapered bearing 20 illustrated in Fig. 1 are formed by setting the ring 50 within a die cavity 52 and pressing a forming die 54 into the ring 50 within the die cavity 52.
  • the die cavity 52 includes an inside wall 56 and an outside wall 58.
  • the inside wall 56 is configured to form the inner surface 40 of the future inner ring 24 and the outside wall 58 is configured to form the outer surface 32 of the future outer ring 22 of the tapered bearing 20 illustrated in Fig. 1.
  • the forming die 54 includes a projection 64 with an inside surface 66 and an outside surface 68.
  • the inside surface 66 is configured to form the inner raceway 38 and the outside surface 68 is configured to form the outer raceway 30 of the tapered bearing 20 when the forming die 54 is pressed into the die cavity 52.
  • the forming die 54 further includes a tip 70 that is configured to form the second flange 48 of the inner ring 24.
  • the press quench step includes a post die 74 and a raceway die 76.
  • the segments of the raceway die 76 are allowed to float in the radial direction while the post die 74 maintains a desired inner bore diameter and inner bore roundness of the inner ring 24.
  • the raceway die 76 will force the raceways into shape in relation to the bore 44 such that the cup angle a and cone angle ⁇ are substantially the same.
  • the element 72 is separated to create the inner ring 24 and the outer ring 22.
  • the rings should separate well due to the small area being sheared and the brittleness of the material in the shear area. It should be understood that the element 72 can be separated before it is carburized, however keeping the element 72 as a single piece greatly facilitates the press quench step of Fig. 3D. Additionally, the separated inner and outer rings 24, 22 may be tumbled after separation. [0036] To assemble the tapered bearing 20, the rolling elements 28 are set within the pockets of the cage 26 and placed upon the inner raceway 38 of the inner ring 24. The outer ring 22 is placed such that the outer raceway 30 captures the rolling elements 28 as illustrated in Fig. 3F.
  • the first flange 46 is formed by hot curling before placing the outer ring 22 over the inner ring 24 (see Fig, 3G).
  • the first flange 46 can be cold formed before heat treatment if a suitable cage design that snaps or forms over the rolling elements 28 is employed.
  • Fig. 4 illustrates a second embodiment of a tapered bearing 120 of the present invention manufactured using a similar method to that previously presented.
  • the tapered roller bearing 120 includes an outer ring 122, an inner ring 124, a cage 126, and tapered rolling elements 128.
  • the outer ring 122 is supported in a housing 136 and the inner ring 124 is supported on a shaft 142.
  • the inner ring 124 has a generally thin and constant cross-sectional thickness.
  • the inner ring 124 includes a tapered inner raceway 138, the taper generally defining a cone angle/?'.
  • the shaft 142 assists in defining the cone angle ⁇ '.
  • the shaft 142 includes a machined taper portion 178 with an angle equal to, or nearly equal to that of the cone angle ⁇ '.
  • the outer ring 122 of the second embodiment also has a generally thin and constant cross-sectional thickness similar to that of the inner ring 124.
  • the outer ring 122 includes an outer raceway 13.0 and an outer surface 132.
  • the outer raceway 130 includes a taper generally defining a cup angle d.
  • the outer surface 132 is supported by the housing 136.
  • the housing 136 includes.a tapered portion 180 that assists in defining the cup angle ol. The angle of the tapered portion 180 is equal to or nearly equal to that of the cup angle d.
  • Tapered rolling elements 128 roll along the inner raceway 138 and the outer raceway 130, positioned by the cage 126,
  • the rolling elements can be defined by one of several variations in cross-section. While the illustrated tapered bearing 120 of Fig. 4 is shown with tapered rolling elements 128, it should be understood that cylindrical rolling elements can also be employed.
  • Figs. 5 A — 5D illustrate one method of manufacturing the tapered bearing 120 of Fig. 4. This method is somewhat similar to the method employed in manufacturing the tapered bearing 20 of Fig. 1. Therefore, only the general differences will be discussed.
  • One method of manufacturing the tapered bearing of Fig. 4 includes creating a blank 182 from generally thin (e.g. 0.010 to about 0.125 inches) sheet metal stock or strip stock (see Fig. 5A).
  • the blank 182 can be made from any suitable material, such as, steel, including low carbon steel, or aluminum.
  • the blank 182 is stamped into a formed element 172 using conventional stamping machinery.
  • Fig. 5B illustrates the formed element 172 that will eventually be separated to create the inner and outer rings 124, 122 of the tapered bearing 120.
  • an optional partial shear 184 can be performed at the future separation point of the element 172 (see Fig. 5C).
  • the partial shear 184 increases the rigidity of the element 172, and as a result, decreases deformation of the element 172 during an optional heat treatment similar to the heat treatment method employed in the first embodiment and as described above.
  • the formed element 172 is separated into the inner ring 124 and the outer ring 122.
  • the partial shear 184 makes the separation of the element 172 easier by reducing the shear area remaining after the element 172 has been hardened during heat treatment.
  • Fig. 5D illustrates the inner and outer ring 124, 122 after separation.
  • the tapered bearing 120 of Fig. 4 is assembled in a substantially similar method to the tapered bearing 20 of Fig. 1.
  • the rolling elements 128 are set within the pockets of the cage 126 and placed upon the inner raceway 138 of the inner ring 124.
  • the outer ring 122 is placed such that the outer raceway 130 captures the rolling elements 128 as illustrated in Fig. 4.
  • the inner and outer rings 124, 122 are each stamped from a separate blank.
  • the inner ring 124 is stamped from a first blank and the outer ring 122 is stamped from a second blank.
  • the first and second blanks can be generally thin (e.g. 0.010 to about 0.125 inches) sheet metal stock or strip stock made from any suitable material, such as steel, including low carbon steel, or aluminum.
  • the inner raceway 138 or outer raceway 130 may include a crown 186 (see Figs. 6 and 7).
  • the raceway of the inner ring 124, the outer ring 122, or both, may be crowned. Providing at least one crowned raceway helps prevent edge loading of the rolling elements 128 if the cone angle ⁇ ' and the cup angle d differ a small amount.
  • the method of forming the tapered bearing 120 presented above, and illustrated in Figs. 5 A - 5D allows the crowned profile of the inner and outer rings 124, 122 to differ if desired.
  • Fig. 6 illustrates one method of forming the crowned inner raceway 138.
  • the crown can be formed by machining a profile in a portion 186 of the shaft 142. Due to the thin cross-sectional thickness of the inner ring 124, the inner ring 124 will conform to the profile of the crown on the shaft 142 when loaded.
  • Fig. 7 illustrates an alternative method of forming the crown.
  • the crown is formed with the use of a raceway seat insert 188.
  • the insert 188 which includes a crowned profile 189, is coupled to the shaft 142.
  • the shaft 142 includes two portions of different diameters that form a shoulder 190.
  • the insert 188 is coupled to the shaft 142, adjacent to the shoulder 190. Again, due to the thin cross-sectional thickness of the inner ring 124, the inner ring 124 will conform to the crowned profile 189 of the insert 188 when loaded.
  • the rolling elements 128 may also include a crown.
  • the crown of the rolling elements 128 minimizes concentrated edge loading on the rolling element 128 which leads to premature failure of the rolling elements 128.
  • the tapered bearing 120 can be modified to include an optional seal 192 (see Fig. 8) or seal 193 and integral flinger ring 194 (see Fig. 9).
  • Fig. 8 illustrates the seal 192 disposed between the inner ring 124' and outer ring 122'.
  • the seal 192 is configured to prevent debris from entering the bearing 120'.
  • the seal 192 provides improved seal and bearing life due to the seal lips riding on hardened steel rather than soft steel which is common with cartridge type seal assemblies.
  • Fig. 9 illustrates a modified tapered bearing 120" with the seal 193 and an integral flinger ring 194.
  • the flinger ring 194 is formed integrally with the inner ring 124" during the stamping process presented above.
  • the flinger ring 194 is also configured to prevent debris from entering the bearing 120". It should be understood that the integral flinger ring 194 can also be formed integrally with the outer ring 122".
  • Fig. 10 is an exploded view of one application of tapered bearings 202 and 204 substantially similar to the tapered bearings 120, 120', and 120" of Figs. 4-9.
  • two tapered bearings 202, 204 are used in a wheel hub assembly 200.
  • the wheel hub assembly 200 is configured for use in an all terrain vehicle, however it should be understood that the wheel hub assembly 200 can be configured for use in any vehicle.
  • the wheel hub assembly 200 includes the first bearing 202, the second bearing 204, a tapered seat insert 206, a hub 208, a brake disk 210 and a knuckle 212.
  • the knuckle 212 includes two supports 214 configured to couple the knuckle 212 to a vehicle.
  • the knuckle 212 may also include a speed sensor 216 which interacts with a tone wheel 218 to determine the speed of the vehicle.
  • the knuckle 212 also includes a bore 219. The bore
  • the hub 208 includes a collar 220 with a rolled over end portion 222.
  • the inner surface of the collar includes an internal spline 224.
  • the spline 224 couples the hub 208 to a shaft (not shown) of the vehicle, such that rotation of the shaft will rotate the hub 208.
  • the rolled over end portion 222 of the collar 220 provides a shoulder which prevents the second bearing 204, the seat insert 206, the first bearing 202, and the hub 208 from moving substantially in the axially direction with respect to the knuckle 212.
  • the hub 208 also includes a plurality of apertures 226 extending through the hub 208. Each of the apertures 226 receives a stud 228.
  • the hub 208 may also include a plurality of axially extended flanges 231.
  • the flanges 231 each include a bore 229 extending through a raised end portion of the flanges 231.
  • the bores 229 receive a fastener (not shown) to couple the brake disk 210 to the hub 208.
  • Fig. 11 illustrates the assembled wheel hub 200.
  • the brake disk 210 interacts with a braking system of the vehicle to slow the rotation of the hub 208. ' If the brake disk 210 requires replacement, it can be removed from the hub 208.
  • the fasteners are removed from the bores 229 and the brake disk 210 is rotated relative to the hub 208.
  • the brake disk 210 is rotated until lobes 233 of the brake disk 210 clear the flanges 231 so that the brake disk 210 can be slid axially and removed.
  • the first and second bearings 202, 204 include an inner ring 232, an outer ring 234, a cage 236, tapered rolling elements 238, and a seal 240.
  • the first and second bearings 202, 204 are substantially similar to the tapered bearings 120, 120', 120" illustrated in Fig. 4-9 and are formed using a method substantially similar to the stamping method presented above and illustrated in Fig. 5.
  • the first and second bearings 202, 204 allow relative rotational motion of the hub 208 with respect to the knuckle 212.
  • the knuckle 212 is held in a substantially fixed rotational position while the hub 208 is rotated by the vehicle shaft.
  • the first bearing 202 is disposed on the collar 220 of the hub 208 such that the inner ring 232 is supported by the collar 220.
  • the first bearing 202 is mounted on a tapered portion 221 of the collar 220.
  • the collar 220 can include a crown surface profile to which the inner ring 232 will conform to when loaded. Alternatively, a raceway seat insert could be used to provide the crown.
  • the second bearing 204 is also disposed on the collar 220 of the hub 208.
  • the tapered seat insert 206 supports the inner ring 232 of the second bearing 204.
  • the seat insert 206 supports and provides a taper to inner ring 232 of the second bearing 204, whereas the inner ring 232 of the first bearing 202 is supported by the tapered portion 221 of the hub 208.
  • the seat insert 206 may include a crowned surface profile. It should be understood that the knuckle 212 may also include a crowned surface profile to which the outer rings 234 of the first and second bearings 202, 204 will conform when loaded.
  • Fig. 12 is an alternative embodiment of the wheel hub 200 of Fig. 11. Fig.
  • wheel hub 300 that is substantially similar to the wheel hub 200 of Fig. 11.
  • wheel hub 300 includes a threaded seat insert 346.
  • the threaded seat insert 346 replaces the rolled over end portion 222 and the seat insert 206 of the wheel hub 200 illustrated in Fig. 11.
  • the wheel hub 300 includes a first bearing 302, a second bearing 304, a hub 308, a brake disk 310 and a knuckle 312.
  • the wheel hub 300 includes a hub 308 with a collar 320.
  • the collar 320 includes a threaded portion 348 disposed an exterior surface of the collar 320.
  • the threaded portion 348 is configured to couple the threaded seat insert 346 to the collar 320.
  • the seat insert 346 provides a tapered portion 321 that supports an inner ring 332 of the second bearing 304.
  • the tapered portion 321 can include a crowned surface profile to which the inner ring 332 will conform when loaded.
  • the seat insert 346 also includes a shoulder 322 that prevents substantial axial movement of the second bearing 304, the first bearing 302 and the hub 308 with respect to the knuckle 312.
  • the threaded seat insert 346 allows for easy access to the first and second bearings 302, 304 for service and maintenance of the wheel hub 300. If the first bearing 302 or the second bearing 304 is in need of replacement or maintenance, the threaded seat insert 346 can easily be removed from the collar 320 by rotating the threaded seat insert 346 with respect to the hub 308. With the seat insert 346 removed, the second bearing 304 can be axially slid off of the collar 320. Next, to access the first bearing 302, the hub 308 can be slid axially while the knuckle 312 remains relatively fixed. When the hub 308 is removed from the bore of the knuckle 312, the first bearing 302 can be slid axially off of the collar 320. The wheel hub 300 can be reassembled by following the above steps in substantially reverse order.
  • Fig. 13 illustrates yet another application of tapered bearings 402, 404 that are substantially similar to the tapered bearings 120, 120', and 120" of Figs. 4-9.
  • a spindle assembly 400 includes a housing 408, a shaft 453, a first bearing 402, and a second bearing 404.
  • the spindle assembly 400 is configured to be used in a lawnmower to transmit rotational motion from a drive member to a blade assembly. It should be understood that the spindle assembly 400 can also be used in other suitable applications to transmit rotational motion.
  • the shaft 453 includes a first end 454 and a second end 455.
  • a pulley (not shown) is coupled to the first end 454.
  • the pulley can be rotated by a belt driven by a drive member. Alternatively, they pulley can be replaced with a gear or any suitable component to transfer rotational motion to the shaft 453.
  • a blade assembly (not shown) is coupled to the second end 455 of the shaft 453. The blade assembly is configured such that rotation of the shaft 453 will rotate one or more blades of the blade assembly.
  • the housing 408 includes a flange 456.
  • the flange 456 and fasteners (not shown) couple the housing 408 to the lawnmower such that the housing 408 remains in a relatively fixed position with respect to the lawnmower. Therefore, when the pulley rotates the shaft 453, the shaft 453 and the blade assembly will rotate with respect to the housing 408.
  • the first and second bearings 402, 404 support the shaft 453 within the housing 408.
  • the first and second bearings 402, 404 are formed using a method substantially similar to the stamping method described above and illustrated in Figs. 5A - 5D, and are substantially similar to the bearings 120, 120', 120", 202, 204, 302, and 304 previously described above.
  • the illustrated spindle assembly 400 also includes a ring 457 staked to the shaft 453.
  • the ring 457 is staked in a groove or grooves of the shaft 453 which are underneath the ring 457 as shown in Fig. 13.
  • the ring 457 presses against an end plate 459 to preload the first and second bearings 402, 404.
  • Providing the preload to the bearing assembly allows for greater bearing stiffness and running accuracy.
  • the ring 457 can easily be removed from the shaft 453 to allow for access to the first and second bearings 402, 404.

Abstract

L'invention concerne un roulement à rouleaux coniques configuré pour supporter un arbre dans un carter en lui permettant de tourner. Le roulement à rouleaux coniques comprend une pluralité d'éléments roulants, une bague intérieure comprenant un chemin de roulement tronconique, une bague extérieure comprenant un chemin de roulement tronconique et un insert accouplé à l'arbre. La bague intérieure s'adapte à une surface de l'insert quand le roulement à rouleaux coniques est en charge et la bague extérieure s'adapte à une surface du carter quand le roulement à rouleaux coniques est en charge.
PCT/US2006/046984 2005-12-22 2006-12-11 Roulement à rouleaux coniques et procédé de fabrication WO2007078616A2 (fr)

Applications Claiming Priority (2)

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US75302605P 2005-12-22 2005-12-22
US60/753,026 2005-12-22

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WO2007078616A3 WO2007078616A3 (fr) 2007-10-18

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PCT/US2006/047858 WO2007075386A2 (fr) 2005-12-22 2006-12-15 Extremite de roue a chemins de roulement emboutis

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DE102007053693A1 (de) * 2007-11-10 2009-05-20 Ab Skf Kegelrollenlageranordnung
CN110425228A (zh) * 2019-09-05 2019-11-08 嘉兴欧治汽车技术有限公司 设滚边的轮毂轴承总成及轴承装配方法

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WO2009064729A2 (fr) * 2007-11-12 2009-05-22 The Timken Company Chemin de roulement extérieur composite de moyeu de roue, et son procédé de fabrication
DE102010026544A1 (de) * 2010-07-08 2012-01-12 Daimler Ag Wälzlager
ITTO20111131A1 (it) * 2011-12-12 2013-06-13 Skf Ab Gruppo cuscinetto-mozzo per la ruota di un veicolo a motore
EP2639465A1 (fr) * 2012-03-16 2013-09-18 Peer Bearing S.r.l. Procédé d'assemblage de roulement à billes pour applications à faible bruit et ensemble de roulement à billes conçu spécifiquement pour la mise en ýuvre de ce procédé
WO2014057303A1 (fr) * 2012-10-10 2014-04-17 Aktiebolaget Skf Palier à roulement comprenant un logement ayant deux parties et procédé permettant de fabriquer et d'installer un tel palier
ITTO20130027A1 (it) * 2013-01-11 2014-07-12 Skf Ab Unità mozzo di peso leggero con anelli di cuscinetto integrati, e procedimenti per la sua fabbricazione
US10300740B2 (en) 2014-07-30 2019-05-28 Honeywell International Inc. Wheel hub bearing bore
DE102017200338A1 (de) 2017-01-11 2017-04-27 Audi Ag Radlager für ein Kraftfahrzeug
GB2572940A (en) * 2018-02-27 2019-10-23 Cooper Roller Bearings Company Ltd Double row spherical roller bearing
CN111594084A (zh) * 2020-05-21 2020-08-28 中国铁建重工集团股份有限公司 球铰接轴承和取芯钻机

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US3262743A (en) * 1963-12-24 1966-07-26 Timken Roller Bearing Co Sealing device for a roller bearing
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DE102007053693B4 (de) * 2007-11-10 2016-03-10 Ab Skf Kegelrollenlageranordnung
CN110425228A (zh) * 2019-09-05 2019-11-08 嘉兴欧治汽车技术有限公司 设滚边的轮毂轴承总成及轴承装配方法

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Publication number Publication date
WO2007078616A3 (fr) 2007-10-18
WO2007075386A3 (fr) 2007-11-08
WO2007075386A2 (fr) 2007-07-05

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