US20140037234A1 - Bearing assembly for oscillation joint - Google Patents
Bearing assembly for oscillation joint Download PDFInfo
- Publication number
- US20140037234A1 US20140037234A1 US13/567,138 US201213567138A US2014037234A1 US 20140037234 A1 US20140037234 A1 US 20140037234A1 US 201213567138 A US201213567138 A US 201213567138A US 2014037234 A1 US2014037234 A1 US 2014037234A1
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- US
- United States
- Prior art keywords
- bearing
- inboard
- outboard
- bearing assembly
- collet
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- 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.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0015—Hubs for driven wheels
- B60B27/0021—Hubs for driven wheels characterised by torque transmission means from drive axle
- B60B27/0026—Hubs for driven wheels characterised by torque transmission means from drive axle of the radial type, e.g. splined key
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- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
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- 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
- F16C2326/20—Land vehicles
Definitions
- the present disclosure is directed to a bearing assembly, and more particularly, to a bearing sleeve having a generally frustoconical shape for use in an oscillation joint.
- Machines such as, for example, motor graders, wheel tractor scrapers, dozers, wheel loaders, and other types of heavy equipment are used to perform terrain leveling tasks. These machines are often operated over uneven terrain, causing individual wheels to be displaced relative to the machine's frame as the machine's wheels track the uneven terrain.
- the tandem assembly is connected to the machine via a single axle with a pair of wheels mounted to a drive housing positioned on each side of the vehicle via a pivoting or oscillation joint.
- the oscillation joint pivotally connects the chassis of the in relation to the outwardly positioned drive housing while enclosing the power relaying components of the drive assembly.
- the oscillation joint is housed within an axle assembly, and is located in proximity to the differential and away from the wheels which makes the oscillation joint prone to higher forces due to the moment arm effect between the wheels and the differential.
- the bearing geometry within the oscillation joint consist of two vertically oriented thrust washers sandwiching a cylindrical ring bearing which is positioned between the portion of the housing enclosing the axle and the drive housing.
- the present disclosure is directed to overcoming one or more of the shortcomings set forth above.
- the present disclosure is directed to a bearing assembly to rotatably support an oscillating hub rotatably connected to a shaft.
- the bearing assembly comprises an inboard bearing defining a first frustoconical ring having a first bearing surface disposed thereon, and an outboard bearing defining a second frustoconical ring having a second bearing surface disposed thereon.
- the bearing assembly is arranged such that the first bearing surface of the first frustoconical ring and the second bearing surface of the second frustoconical ring are positioned relative to one another to form a generally v-shaped bearing interface between the shaft and the hub.
- FIG. 1 is a diagrammatic illustration of an exemplary machine
- FIG. 2 is a perspective view of a drive casing
- FIG. 3 is a top view of the tandem wheel lower drive train of the machine of FIG. 1 ;
- FIG. 4A is a cross section of an exemplary oscillation joint
- FIG. 4B is a cross-section of another exemplary oscillation joint
- FIG. 5A is a side view of an inboard bearing
- FIG. 5B is a side view of an outboard bearing
- FIG. 6 is a sectional perspective view of the exemplary oscillation joint.
- FIG. 7 is a diagram of the forces in the oscillation joint.
- FIG. 1 illustrates machine 10 having a tandem wheel drive 20 which includes forward wheel 22 and rear wheel 24 .
- the wheels are connected to drive shaft 54 which, in turn, connected to drive axle 56 which is rotatably supported within drive casing 30 , and drive casing 30 is in turn mounted to the body chassis 32 .
- the drive casing 30 is a rigid structure that supports rotating rear and front axles 25 , 27 .
- Positioned on inner side 29 of casing 30 is oscillating hub 90 which is rotatably connected to shaft 68 of the axle assembly 28 through oscillation joint 40 .
- the forward wheel 22 is positioned forward of the oscillation joint 40 relative to the machine 10 and the rear wheel 24 is positioned to the rear of the oscillation joint 40 .
- FIG. 1 depicts the right side of the machine 10
- an identical tandem wheel drive 20 would be provided on the left side as well.
- FIG. 3 depicts the lower drive train assembly 50 of the tandem wheel drive 20 .
- the lower drive train assembly 50 includes centrally located differential 52 connected to drive shaft 54 which is in turn driven by a power source, such as an engine (not shown). Extending from each side of the differential 52 are drive axles 56 .
- drive axle 56 has chain drive sprocket 58 affixed to an end of the drive axle 60 .
- Each chain drive sprocket 58 drives a chain loop 62 which in turn drives a wheel sprocket 64 associated with each wheel assembly 66 .
- Rotation of the drive shaft 54 provides power to the differential 52 , which in turn drives the rotation of a drive axle 56 which rotates about a central axis that substantially corresponds to the oscillation joint axis A.
- FIG. 4A depicts a sectional view of an exemplary oscillation joint 40 .
- the oscillation joint 40 includes a shaft portion 68 having a cylindrical outer surface section 70 that surrounds and is centered about oscillation joint axis A.
- the shaft portion 68 has a diameter D 1 of about 225 mm to about 750 mm in the area of the cylindrical outer surface section 70 .
- an oscillating hub 90 Positioned over and surrounding the cylindrical outer surface 70 is an oscillating hub 90 having an inner contact surface 94 .
- the oscillating hub 90 when its inner contact surface 94 is positioned over the outer surface 70 , is rotatable relative to the shaft portion 68 .
- the bearing assembly 100 Positioned between the cylindrical surface 70 and the inner surface 94 of the oscillating hub 90 is a bearing assembly 100 .
- the bearing assembly 100 comprises an inboard bearing 102 on the machine 10 side of the oscillation joint 40 and an outboard bearing 104 on the drive casing 30 side of the oscillation joint 40 .
- the relative positioning of the inboard bearing 102 and the outboard bearing 104 in the bearing assembly 100 is such that a generally v-shaped bearing interface 105 is formed between the shaft 68 and the oscillating hub 90 .
- the inboard bearing 102 is supported on its side facing the shaft portion 68 by an inclined surface 103 that extends between the cylindrical surface 70 and shoulder wall 76 .
- the inclined surface 103 may be a cast portion of the shaft 68 or may be machined into the surface of the shaft.
- the outboard bearing 104 is supported in its side facing the shaft portion by an inclined surface 107 that extends from a mounting plate 160 which will be discussed further herein.
- FIG. 4B depicts a sectional view of an alternative exemplary oscillation joint 40 that is similar to the oscillation joint depicted in FIG. 4A with the exception that the inboard bearing 102 and outboard bearing 104 are supported by inboard collet 140 and outboard collet 150 , respectively, which will be discussed further herein.
- the inboard bearing 102 as depicted in FIGS. 4A , 4 B and 5 A is in the shape of a first frustoconical ring and is provided with a first bearing surface 106 along its outer surface.
- the outboard bearing 104 as depicted in FIGS. 4A , 4 B and 5 B is in the shape of a second frustoconical ring and is provided with a second bearing surface 108 .
- the frustoconical ring of the inboard bearing 102 has an apical end 110 and a base end 112 and the first bearing surface 106 of the inboard bearing 102 is generally disposed between the apical end 110 and base end 112 .
- the aperture 114 at the apical end 110 of the inboard bearing 102 has a diameter D 2 of about 225 mm to about 750 mm.
- the diameter D 2 of the aperture 114 is substantially equal to the diameter D 1 of the cylindrical portion 70 of the shaft 68 .
- the base end 112 of the inboard bearing 102 is generally contained within a plane 116 parallel to a plane 118 containing the apical end 110 .
- the first bearing surface 106 is at an angle ⁇ 1 of about 9 degrees to about 28 degrees relative to the base end 112 .
- the base end 112 of the inboard bearing 102 has an outer diameter D 3 of about 300 mm to about 784 mm.
- the frustoconical ring of the outboard bearing 104 has an apical end 120 and a base end 122 and the second bearing surface 108 of the outboard bearing 104 is generally disposed between the apical and 120 and the base end 122 .
- the aperture 124 at the apical end 120 of the outboard bearing 104 has a diameter D 4 of about 225 mm to about 750 mm.
- the diameter D 4 of the aperture 124 is substantially equal to the diameter D 1 of the cylindrical portion 70 of the shaft 68 .
- the base end 122 of the outboard bearing 104 is generally contained within a plane 126 parallel to a plane 128 containing the apical end 120 .
- the second bearing surface 108 is at an angle ⁇ 2 of about 46 degrees to about 50 degrees relative to the base end 122 .
- the base end 122 of the outboard bearing 104 has an outer diameter D 5 of about 309 mm to about 784 mm.
- the inboard bearing 102 and the outboard bearing 104 may be formed from any known bearing material known in the art.
- the bearing material may be formed from a metal based material such as chrome steel, stainless steel, carbon alloy steel, and the like.
- the bearing material may preferably be made from a non-metallic material.
- Non-metallic bearing materials suitable for the present bearing assembly 100 include ceramic, nylon, plastics, and a phenolic cotton and resin compound.
- the phenolic cotton and resin compound is particularly preferred due to its durability and being relatively inexpensive. Additionally, the phenolic cotton and resin compound has the ability to be thermoformed to a desired shape from a flat sheet stock.
- the resultant shape is a frustoconical ring.
- the specific curvature of the curved strip cut from the flat sheet stock can be modified so as to provide the desired angle in the frustoconical ring.
- the inboard bearing 102 is in the form of a frustoconical ring extending from an apical end 110 to a base end 112 .
- the inboard bearing 102 has a first bearing surface 106 provided on the exterior surface of the frustoconical ring and an interior surface 132 on the side opposite the first bearing surface 106 .
- the thickness of the inner bearing 102 between the first bearing surface 106 and the interior surface 132 is about 3 mm to about 10 mm.
- the outboard bearing 104 is in the form of a frustoconical ring extending from an apical end 120 to a base end 122 .
- the outboard bearing 104 has a second bearing surface 108 provided on the exterior surface of the frustoconical ring and an interior surface 134 on the side opposite the second bearing surface 108 .
- the thickness of the outer bearing 104 between the second bearing surface 108 and the interior surface 134 is about 3 mm to about 10 mm.
- the term “generally v-shaped” as used above can be understood to mean a relative arrangement that is defined by an interface 105 wherein the apical ends 110 , 120 of the inboard and outboard bearings 102 , 104 are immediately adjacent each other and are separated by less than about 1 mm.
- the term may also be understood to mean a relative arrangement where the apical ends 110 , 120 are separated from each other such that there is a flat landing area 130 between the apical ends 110 , 120 .
- the flat landing area 130 coincides with an open area of the cylindrical surface 70 of the shaft 68 not covered by either the inboard 102 or outboard 104 bearings. In such an arrangement where there is a flat landing area 130 , the apical ends 110 , 120 may be separated by a distance of about 4 mm to about 180 mm.
- the inner contact surface 94 of the oscillating hub 90 will have a generally v-shaped profile in cross section that projects into the generally v-shaped bearing assembly 100 .
- the inner contact surface 94 for a particular oscillation joint 40 will have a generally v-shaped profile that corresponds to the generally v-shaped bearing assembly 100 formed on the shaft 68 to provide a tight and cohesive oscillation joint 40 for the machine 10 .
- the bearing assembly 100 further includes an inboard collet 140 for supporting the inboard bearing 102 .
- the inboard collet 140 has a cross-section that is generally in the form of a right triangle.
- the inboard collet has an apical end 142 , a base end 144 , a supporting surface 146 and a cylindrical through bore 148 .
- the base end 144 projects substantially perpendicularly away from the through bore 148 .
- the supporting surface 146 is sized and angled such that it has generally the same size and angled surface of the interior surface 132 of the inboard bearing 102 .
- the supporting surface 146 is at an angle ⁇ 3 of about 9 degrees to about 28 degrees relative to the base end 144 .
- the inboard bearing 102 can be placed onto the inboard collet 140 such that the entire interior surface 132 of the inboard bearing 102 is supported by the supporting face 146 of the inboard collet 140 .
- the through bore 148 of the inboard collet 140 has a diameter D 6 of about 225 mm to about 750 mm.
- the diameter D 6 of the through bore 148 is substantially equal to the diameter D 1 of the cylindrical portion 70 of the shaft 68 .
- the inboard collet 140 may have an axial length of about 5 mm to about 25 mm.
- the base end 144 of the inboard collet 140 which projects perpendicularly away from the through bore 148 , may have an outer diameter D 8 of about 300 mm to about 784 mm.
- the base end 144 is sized to not extend above a supporting shoulder wall 76 provided on the shaft 68 as will be discussed below.
- the bearing assembly 100 further includes an outboard collet 150 for supporting the outboard bearing 104 .
- the outboard collet 150 has a cross-section that is generally in the form of a right triangle.
- the inboard collet has an apical end 152 , a base end 154 , a supporting surface 156 and a cylindrical through bore 158 .
- the base end 154 projects substantially perpendicularly away from the through bore 158 .
- the supporting surface 156 is sized and angled such that it has generally the same size and angled surface of the interior surface 134 of the outboard bearing 104 . As such, the supporting surface 156 is at an angle ⁇ 4 of about 46 degrees to about 50 degrees relative to the base end 154 .
- the outboard bearing 104 can be placed onto the outboard collet 150 such that the entire interior surface 134 of the outboard bearing 104 is supported by the supporting face 156 of the outboard collet 150 .
- the through bore 158 of the outboard collet 150 has a diameter D 7 of about 225 mm to about 750 mm.
- the diameter D 7 of the through bore 158 is substantially equal to the diameter D 1 of the cylindrical portion 70 of the shaft 68 .
- the outboard collet 150 may have an axial length of about 15 mm to about 30 mm.
- the base end 154 of the outboard collet 150 which projects perpendicularly away from the base end 154 , may have an outer diameter D 9 of about 309 mm to about 784 mm.
- the bearing assembly may further be provided with an annular mounting plate 160 sized to interact with an end face 74 of the shaft and to hold the bearing assembly 100 in place.
- the mounting plate 160 may be fixedly held in place by a fastening device 162 such as a bolt or screw.
- the mounting plate 160 has an through hole 164 with a diameter D 10 less than the diameter D 1 of the cylindrical face and an outer diameter D 11 sized substantially similar to the outer diameter D 9 of the outer collet base end 154 .
- the inboard bearing 102 is supported on its interior surface 132 by inclined surface 103 .
- Inclined surface 103 has a similarly angled and shaped supporting surface 196 to the supporting surface 146 of inboard collet 140 described above.
- the inclined surface 103 is a unitary piece with the shaft 68 .
- the angled face of the inclined surface 103 extends from the cylindrical surface 70 shoulder wall 76 of the shaft and is angled to support the interior surface 132 of the inboard bearing 102 .
- the outer collet 150 and the mounting plate 160 may be formed from a single piece to form a retaining collet 198 .
- This combined piece serves the function of both the outer collet 150 and mounting plate 160 as described above and provides an inclined surface 107 .
- Inclined surface 107 has a similarly angled and shaped supporting surface 197 to the supporting surface 156 of outboard collet 150 described above.
- the oscillation joint 40 allows independent rotation of the drive casing 30 about the oscillation joint axis A.
- the rotation about the oscillation joint 40 allows the machine 10 to operate more smoothly over rough terrain. For example, when the machine 10 is moving in a forward direction and the right side forward wheel 22 as depicted in FIG. 1 encounters an obstacle, such as a rock, the forward wheel would move upwardly and cause a counterclockwise rotation of the drive casing 30 about the oscillation joint axis A.
- the axle of the forward wheel 23 , oscillation joint axis A, and the axle of the rear wheel 25 remain in a straight line L with the front wheel elevated relative to the rear wheel 24 .
- the drive casing 30 rotates clockwise about the oscillation joint axis A until the line L is again substantially horizontal (or parallel with the ground).
- the rear wheel 24 would, in a manner similar to the forward wheel 22 , move upwardly and cause a clockwise rotation of the drive casing 30 about the oscillation joint axis A.
- the axle of the forward wheel 23 , oscillation joint axis A, and the axle of the rear wheel remain in a straight line L with the rear wheel 24 elevated relative to the forward wheel 22 .
- the drive casing rotates counterclockwise about the oscillation joint axis A until the line L is substantially horizontal.
- the rotation of the oscillation joint 40 when the wheel 22 , 24 are passing over obstacles also allows more accurate terrain leveling operation.
- FIG. 6 depicts a section of a portion of the oscillation joint 40 .
- the drive axle 56 passes through a shaft portion 68 of the oscillation joint 40 .
- the shaft 68 has a cylindrical outer surface 70 that surrounds and is centered about oscillation joint axis A.
- the cylindrical outer surface has a first end 72 proximal to the differential 52 and a second end distal to the differential have an end face 74 projecting perpendicular and radially inwardly from the cylindrical outer surface 70 .
- FIG. 1 depicted in FIG.
- a shoulder wall 76 having a height of about 15 to about 40 mm between the cylindrical surface 70 and a top edge 78 .
- the shoulder substantially extends around the circumference of the inner housing 68 and has a diameter greater than that of the cylindrical outer surface 70 .
- inclined surface 103 extends from the first end of the cylindrical surface to the location of the shoulder 76 .
- the inner housing 69 which includes shaft 68 and shoulder wall 76 , additionally includes a flange surface 80 for fixedly connecting the inner housing 69 to the differential 52 .
- the flange surface 80 may be connected to the differential 52 using bolts, screws, welding, or any other known method of fixedly attaching pieces together. By fixedly attached, it is intended that the inner housing and the differential do not rotate relative to one another.
- the inner housing may also be provided with a second cylindrical surface 82 extending from the shoulder top edge 78 to the flange 80 joining the structures.
- the oscillating hub 90 has a generally v-shaped inner contact surface 94 that corresponds to the generally v-shaped bearing assembly 100 about with the oscillating joint 40 rotates.
- the inner contact surface 94 surrounds the shaft 68 and contacts at least the inboard bearing 102 and the outboard bearing 104 .
- the oscillating hub 90 is also provided with an outer flange 170 positioned at the outboard side 172 of the oscillating hub 90 .
- the outer flange 170 is provided so that the oscillating hub 90 can be fixedly connected to the drive casing 30 .
- the oscillating hub 90 may be connected to the drive casing using a fastening device 174 such as bolts, screws, or any other known method of fixedly attaching pieces together.
- the generally v-shaped arrangement of the bearing assembly 100 provides an even wear profile in the oscillation joint 40 .
- an extended life wear profile is provided as compared to a similar oscillation joint using a thrust washer and thrust ring arrangement.
- the oscillation joint In addition to handling the standard vertical forces that are experienced within the joint, the oscillation joint also handles horizontal forces that would be experienced in a side impact to a wheel. Basically, the impact force is transmitted to the sloping v-shaped portion of the oscillation joint bearing and due to its shape, any wear to the bearing does not result in “play” or a “wear-gap” at the bearings.
- the axial positioning of the oscillation joint bearing assembly 100 on the shaft 68 can be achieved through the use of shims (not shown).
- the shims are formed from thin metallic washers sized to fit over the cylindrical portion 70 of the shaft 68 . If required, the shims may be placed between either the shoulder wall 76 and the base end 144 of the inboard collet 140 , between the annular mounting plate 160 and the base end 154 of the outboard collet 150 , or both.
- the angle ⁇ 1 for the first bearing surface 106 is perpendicular to the force couple 190 resisting the tipping moment. This angle is parallel to a line through the contact point on the inboard bearing 102 and outboard bearing 104 .
- the angle ⁇ 2 for the second bearing surface 108 is perpendicular to the angle of the vector sum of the reaction force due to the force couple 190 resisting the tipping moment and the vertical load 192 which is reacted to by the outboard bearing 104 (see FIG. 7 ).
- the optimal angle of the inboard bearing 102 and the outboard bearing 104 as calculated may vary by plus or minus 5 degrees based on the rim and tire selection for a particular machine. Variables for calculating the optimal angles or a variety of machines having an oscillation joint are contained in Table 1.
- Ratio of force couple reaction magnitude to tire force vertical load joint center to tire center axial/distance between contact points
- the disclosed oscillation joint and bearing assembly may be an inexpensive, effective solution for reducing bearing wear in the oscillation joint of a machine.
Abstract
A bearing assembly for an oscillation joint on a machine having a tandem wheel drive. The bearing assembly rotatably supports an oscillating hub rotatably connected to a shaft. The bearing assembly includes a frustoconical inboard bearing having a first bearing surface and a frustoconical outboard bearing having a second bearing surface disposed thereon positioned such that the first and second bearing surfaces form a generally v-shaped bearing interface between the shaft and the hub.
Description
- The present disclosure is directed to a bearing assembly, and more particularly, to a bearing sleeve having a generally frustoconical shape for use in an oscillation joint.
- Machines such as, for example, motor graders, wheel tractor scrapers, dozers, wheel loaders, and other types of heavy equipment are used to perform terrain leveling tasks. These machines are often operated over uneven terrain, causing individual wheels to be displaced relative to the machine's frame as the machine's wheels track the uneven terrain. In machines with a tandem wheel drive assembly, the tandem assembly is connected to the machine via a single axle with a pair of wheels mounted to a drive housing positioned on each side of the vehicle via a pivoting or oscillation joint. The oscillation joint pivotally connects the chassis of the in relation to the outwardly positioned drive housing while enclosing the power relaying components of the drive assembly. With a known conventional suspension incorporating pivoting or oscillation joints, the machine's wheels track the terrain and the suspension is structured to manage downward as well as shear forces imparted on the wheels during machine operation. An example of a machine incorporating an oscillation joint is described in U.S. Pat. No. 7,959,169 issued to Gentry et al.
- In particular, the oscillation joint is housed within an axle assembly, and is located in proximity to the differential and away from the wheels which makes the oscillation joint prone to higher forces due to the moment arm effect between the wheels and the differential. Traditionally, the bearing geometry within the oscillation joint consist of two vertically oriented thrust washers sandwiching a cylindrical ring bearing which is positioned between the portion of the housing enclosing the axle and the drive housing. As the oscillation joint wears, the thrust rings' respective clearances increase resulting in increased side-to-side movement and, as a result, premature wear ensues.
- Maintenance of the traditional oscillation joint typically requires adding shims to one or both of the thrust washers to take up the gap caused by wear of the thrust washers. This causes added expense and machine downtime. Moreover, the ring bearing may wear at a different rate than the pair of thrust washers resulting in additional maintenance events and the replacement of unevenly worn components. Additionally, the individual thrust washers may experience different degrees of wear. Such uneven wear often results in early replacement of the bearing combination within the oscillation joint. Moreover, using axial shims only addresses the axial forces that are experienced within the joint and does not allow for radial gap adjustment. A typical method of providing for both radial and axial gap adjustment in a rotating application is to utilize opposing tapered roller bearings or crossed roller bearings. However, known tapered roller bearings have predetermined angularity between the roller bearings and the axial direction of the oscillation joint. Custom made units of tapered roller bearings and crossed roller bearings are expensive and often impractical for large diameter bearing applications.
- The present disclosure is directed to overcoming one or more of the shortcomings set forth above.
- In an exemplary embodiment, the present disclosure is directed to a bearing assembly to rotatably support an oscillating hub rotatably connected to a shaft. The bearing assembly comprises an inboard bearing defining a first frustoconical ring having a first bearing surface disposed thereon, and an outboard bearing defining a second frustoconical ring having a second bearing surface disposed thereon. The bearing assembly is arranged such that the first bearing surface of the first frustoconical ring and the second bearing surface of the second frustoconical ring are positioned relative to one another to form a generally v-shaped bearing interface between the shaft and the hub.
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FIG. 1 is a diagrammatic illustration of an exemplary machine; -
FIG. 2 is a perspective view of a drive casing; -
FIG. 3 is a top view of the tandem wheel lower drive train of the machine ofFIG. 1 ; -
FIG. 4A is a cross section of an exemplary oscillation joint; -
FIG. 4B is a cross-section of another exemplary oscillation joint; -
FIG. 5A is a side view of an inboard bearing; -
FIG. 5B is a side view of an outboard bearing; -
FIG. 6 is a sectional perspective view of the exemplary oscillation joint; and -
FIG. 7 is a diagram of the forces in the oscillation joint. -
FIG. 1 illustratesmachine 10 having atandem wheel drive 20 which includesforward wheel 22 andrear wheel 24. The wheels are connected to driveshaft 54 which, in turn, connected to driveaxle 56 which is rotatably supported withindrive casing 30, anddrive casing 30 is in turn mounted to thebody chassis 32. Thedrive casing 30, as best seen inFIG. 2 , is a rigid structure that supports rotating rear andfront axles inner side 29 ofcasing 30 is oscillatinghub 90 which is rotatably connected toshaft 68 of theaxle assembly 28 throughoscillation joint 40. Theforward wheel 22 is positioned forward of theoscillation joint 40 relative to themachine 10 and therear wheel 24 is positioned to the rear of theoscillation joint 40. WhileFIG. 1 depicts the right side of themachine 10, an identicaltandem wheel drive 20 would be provided on the left side as well. -
FIG. 3 depicts the lowerdrive train assembly 50 of thetandem wheel drive 20. The lowerdrive train assembly 50 includes centrally located differential 52 connected todrive shaft 54 which is in turn driven by a power source, such as an engine (not shown). Extending from each side of thedifferential 52 are driveaxles 56. In an exemplary embodiment, driveaxle 56 has chain drive sprocket 58 affixed to an end of thedrive axle 60. Each chain drive sprocket 58 drives achain loop 62 which in turn drives awheel sprocket 64 associated with eachwheel assembly 66. Rotation of thedrive shaft 54 provides power to thedifferential 52, which in turn drives the rotation of adrive axle 56 which rotates about a central axis that substantially corresponds to the oscillation joint axis A. -
FIG. 4A depicts a sectional view of anexemplary oscillation joint 40. Theoscillation joint 40 includes ashaft portion 68 having a cylindricalouter surface section 70 that surrounds and is centered about oscillation joint axis A. In one embodiment, theshaft portion 68 has a diameter D1 of about 225 mm to about 750 mm in the area of the cylindricalouter surface section 70. Positioned over and surrounding the cylindricalouter surface 70 is an oscillatinghub 90 having aninner contact surface 94. The oscillatinghub 90, when itsinner contact surface 94 is positioned over theouter surface 70, is rotatable relative to theshaft portion 68. - Positioned between the
cylindrical surface 70 and theinner surface 94 of the oscillatinghub 90 is abearing assembly 100. In an exemplary embodiment, thebearing assembly 100 comprises an inboard bearing 102 on themachine 10 side of theoscillation joint 40 and an outboard bearing 104 on thedrive casing 30 side of theoscillation joint 40. The relative positioning of the inboard bearing 102 and the outboard bearing 104 in thebearing assembly 100 is such that a generally v-shaped bearing interface 105 is formed between theshaft 68 and the oscillatinghub 90. - In the exemplary embodiment depicted in
FIG. 4A , the inboard bearing 102 is supported on its side facing theshaft portion 68 by an inclined surface 103 that extends between thecylindrical surface 70 andshoulder wall 76. The inclined surface 103 may be a cast portion of theshaft 68 or may be machined into the surface of the shaft. Theoutboard bearing 104 is supported in its side facing the shaft portion by an inclined surface 107 that extends from a mountingplate 160 which will be discussed further herein. -
FIG. 4B depicts a sectional view of an alternative exemplary oscillation joint 40 that is similar to the oscillation joint depicted inFIG. 4A with the exception that theinboard bearing 102 andoutboard bearing 104 are supported byinboard collet 140 andoutboard collet 150, respectively, which will be discussed further herein. - The
inboard bearing 102 as depicted inFIGS. 4A , 4B and 5A is in the shape of a first frustoconical ring and is provided with afirst bearing surface 106 along its outer surface. Similarly, theoutboard bearing 104 as depicted inFIGS. 4A , 4B and 5B, is in the shape of a second frustoconical ring and is provided with asecond bearing surface 108. - The frustoconical ring of the
inboard bearing 102 has anapical end 110 and abase end 112 and thefirst bearing surface 106 of theinboard bearing 102 is generally disposed between theapical end 110 andbase end 112. Theaperture 114 at theapical end 110 of theinboard bearing 102 has a diameter D2 of about 225 mm to about 750 mm. The diameter D2 of theaperture 114 is substantially equal to the diameter D1 of thecylindrical portion 70 of theshaft 68. - The
base end 112 of theinboard bearing 102 is generally contained within aplane 116 parallel to aplane 118 containing theapical end 110. In an exemplary embodiment, thefirst bearing surface 106 is at an angle ⊖1 of about 9 degrees to about 28 degrees relative to thebase end 112. - In an exemplary embodiment, the
base end 112 of theinboard bearing 102 has an outer diameter D3 of about 300 mm to about 784 mm. - The frustoconical ring of the
outboard bearing 104 has anapical end 120 and abase end 122 and thesecond bearing surface 108 of theoutboard bearing 104 is generally disposed between the apical and 120 and thebase end 122. Theaperture 124 at theapical end 120 of theoutboard bearing 104 has a diameter D4 of about 225 mm to about 750 mm. The diameter D4 of theaperture 124 is substantially equal to the diameter D1 of thecylindrical portion 70 of theshaft 68. - The
base end 122 of theoutboard bearing 104 is generally contained within aplane 126 parallel to aplane 128 containing theapical end 120. In an exemplary embodiment, thesecond bearing surface 108 is at an angle ⊖2 of about 46 degrees to about 50 degrees relative to thebase end 122. - In an exemplary embodiment, the
base end 122 of theoutboard bearing 104 has an outer diameter D5 of about 309 mm to about 784 mm. - The
inboard bearing 102 and theoutboard bearing 104 may be formed from any known bearing material known in the art. For example, the bearing material may be formed from a metal based material such as chrome steel, stainless steel, carbon alloy steel, and the like. The bearing material may preferably be made from a non-metallic material. Non-metallic bearing materials suitable for thepresent bearing assembly 100 include ceramic, nylon, plastics, and a phenolic cotton and resin compound. The phenolic cotton and resin compound is particularly preferred due to its durability and being relatively inexpensive. Additionally, the phenolic cotton and resin compound has the ability to be thermoformed to a desired shape from a flat sheet stock. When a curved strip of the phenolic cotton and resin compound is passed through a set of heat rollers, the resultant shape is a frustoconical ring. The specific curvature of the curved strip cut from the flat sheet stock can be modified so as to provide the desired angle in the frustoconical ring. - The
inboard bearing 102, as described above, is in the form of a frustoconical ring extending from anapical end 110 to abase end 112. Theinboard bearing 102 has afirst bearing surface 106 provided on the exterior surface of the frustoconical ring and aninterior surface 132 on the side opposite thefirst bearing surface 106. The thickness of theinner bearing 102 between thefirst bearing surface 106 and theinterior surface 132 is about 3 mm to about 10 mm. - Similarly, the
outboard bearing 104, is in the form of a frustoconical ring extending from anapical end 120 to abase end 122. Theoutboard bearing 104 has asecond bearing surface 108 provided on the exterior surface of the frustoconical ring and aninterior surface 134 on the side opposite thesecond bearing surface 108. The thickness of theouter bearing 104 between thesecond bearing surface 108 and theinterior surface 134 is about 3 mm to about 10 mm. - The term “generally v-shaped” as used above can be understood to mean a relative arrangement that is defined by an
interface 105 wherein the apical ends 110, 120 of the inboard andoutboard bearings flat landing area 130 between the apical ends 110, 120. Theflat landing area 130 coincides with an open area of thecylindrical surface 70 of theshaft 68 not covered by either the inboard 102 or outboard 104 bearings. In such an arrangement where there is aflat landing area 130, the apical ends 110, 120 may be separated by a distance of about 4 mm to about 180 mm. - Similarly, the
inner contact surface 94 of theoscillating hub 90 will have a generally v-shaped profile in cross section that projects into the generally v-shapedbearing assembly 100. Theinner contact surface 94 for a particular oscillation joint 40 will have a generally v-shaped profile that corresponds to the generally v-shapedbearing assembly 100 formed on theshaft 68 to provide a tight and cohesive oscillation joint 40 for themachine 10. - In an exemplary embodiment as depicted in
FIG. 4B , the bearingassembly 100, further includes aninboard collet 140 for supporting theinboard bearing 102. Theinboard collet 140 has a cross-section that is generally in the form of a right triangle. The inboard collet has anapical end 142, abase end 144, a supportingsurface 146 and a cylindrical throughbore 148. Thebase end 144 projects substantially perpendicularly away from the throughbore 148. The supportingsurface 146 is sized and angled such that it has generally the same size and angled surface of theinterior surface 132 of theinboard bearing 102. As such, the supportingsurface 146 is at an angle ⊖3 of about 9 degrees to about 28 degrees relative to thebase end 144. Theinboard bearing 102 can be placed onto theinboard collet 140 such that the entireinterior surface 132 of theinboard bearing 102 is supported by the supportingface 146 of theinboard collet 140. - The through
bore 148 of theinboard collet 140 has a diameter D6 of about 225 mm to about 750 mm. The diameter D6 of the throughbore 148 is substantially equal to the diameter D1 of thecylindrical portion 70 of theshaft 68. By the diameter D1 of the throughbore 148 being matched to the diameter D1 of thecylindrical portion 70 of theshaft 68, a tight, non-rotating fit is provided between theinboard collet 140 and thecylindrical portion 70. Theinboard collet 140 may have an axial length of about 5 mm to about 25 mm. Further, thebase end 144 of theinboard collet 140, which projects perpendicularly away from the throughbore 148, may have an outer diameter D8 of about 300 mm to about 784 mm. Thebase end 144 is sized to not extend above a supportingshoulder wall 76 provided on theshaft 68 as will be discussed below. - In an exemplary embodiment, the bearing
assembly 100, further includes anoutboard collet 150 for supporting theoutboard bearing 104. Theoutboard collet 150 has a cross-section that is generally in the form of a right triangle. The inboard collet has anapical end 152, abase end 154, a supportingsurface 156 and a cylindrical throughbore 158. Thebase end 154 projects substantially perpendicularly away from the throughbore 158. The supportingsurface 156 is sized and angled such that it has generally the same size and angled surface of theinterior surface 134 of theoutboard bearing 104. As such, the supportingsurface 156 is at an angle ⊖4 of about 46 degrees to about 50 degrees relative to thebase end 154. Theoutboard bearing 104 can be placed onto theoutboard collet 150 such that the entireinterior surface 134 of theoutboard bearing 104 is supported by the supportingface 156 of theoutboard collet 150. - The through
bore 158 of theoutboard collet 150 has a diameter D7 of about 225 mm to about 750 mm. The diameter D7 of the throughbore 158 is substantially equal to the diameter D1 of thecylindrical portion 70 of theshaft 68. By the diameter D7 of the throughbore 158 being matched to the diameter D1 of thecylindrical portion 70 of theshaft 68, a tight, non-rotating fit is provided between theoutboard collet 150 and thecylindrical portion 70. Theoutboard collet 150 may have an axial length of about 15 mm to about 30 mm. Further, thebase end 154 of theoutboard collet 150, which projects perpendicularly away from thebase end 154, may have an outer diameter D9 of about 309 mm to about 784 mm. - The bearing assembly may further be provided with an
annular mounting plate 160 sized to interact with anend face 74 of the shaft and to hold the bearingassembly 100 in place. The mountingplate 160 may be fixedly held in place by afastening device 162 such as a bolt or screw. The mountingplate 160 has an throughhole 164 with a diameter D10 less than the diameter D1 of the cylindrical face and an outer diameter D11 sized substantially similar to the outer diameter D9 of the outercollet base end 154. - In another exemplary embodiment as depicted in
FIG. 4A , theinboard bearing 102 is supported on itsinterior surface 132 by inclined surface 103. Inclined surface 103 has a similarly angled and shaped supportingsurface 196 to the supportingsurface 146 ofinboard collet 140 described above. However, rather than providing a separateinboard collet 140, in this embodiment, the inclined surface 103 is a unitary piece with theshaft 68. The angled face of the inclined surface 103 extends from thecylindrical surface 70shoulder wall 76 of the shaft and is angled to support theinterior surface 132 of theinboard bearing 102. - In an exemplary embodiment, the
outer collet 150 and the mountingplate 160 may be formed from a single piece to form a retainingcollet 198. This combined piece serves the function of both theouter collet 150 and mountingplate 160 as described above and provides an inclined surface 107. Inclined surface 107 has a similarly angled and shaped supportingsurface 197 to the supportingsurface 156 ofoutboard collet 150 described above. - As described above, the oscillation joint 40 allows independent rotation of the
drive casing 30 about the oscillation joint axis A. The rotation about the oscillation joint 40 allows themachine 10 to operate more smoothly over rough terrain. For example, when themachine 10 is moving in a forward direction and the right side forward wheel 22 as depicted inFIG. 1 encounters an obstacle, such as a rock, the forward wheel would move upwardly and cause a counterclockwise rotation of thedrive casing 30 about the oscillation joint axis A. When theforward wheel 22 is on the rock, the axle of the forward wheel 23, oscillation joint axis A, and the axle of therear wheel 25 remain in a straight line L with the front wheel elevated relative to therear wheel 24. As theforward wheel 22 passes over and drops back down from the rock, thedrive casing 30 rotates clockwise about the oscillation joint axis A until the line L is again substantially horizontal (or parallel with the ground). When therear wheel 24 then encounters the rock, therear wheel 24 would, in a manner similar to theforward wheel 22, move upwardly and cause a clockwise rotation of thedrive casing 30 about the oscillation joint axis A. When therear wheel 24 is on the rock, the axle of the forward wheel 23, oscillation joint axis A, and the axle of the rear wheel remain in a straight line L with therear wheel 24 elevated relative to theforward wheel 22. As therear wheel 24 passes over and drops down from the rock, the drive casing rotates counterclockwise about the oscillation joint axis A until the line L is substantially horizontal. The rotation of the oscillation joint 40 when thewheel -
FIG. 6 depicts a section of a portion of theoscillation joint 40. In an exemplary embodiment, thedrive axle 56, passes through ashaft portion 68 of theoscillation joint 40. As described above, theshaft 68 has a cylindricalouter surface 70 that surrounds and is centered about oscillation joint axis A. The cylindrical outer surface has afirst end 72 proximal to the differential 52 and a second end distal to the differential have anend face 74 projecting perpendicular and radially inwardly from the cylindricalouter surface 70. In the embodiment depicted inFIG. 4B and described above, extending perpendicular and radially outward from thecylindrical surface 70 from thefirst end 72 is ashoulder wall 76 having a height of about 15 to about 40 mm between thecylindrical surface 70 and atop edge 78. The shoulder substantially extends around the circumference of theinner housing 68 and has a diameter greater than that of the cylindricalouter surface 70. In the embodiment depicted inFIG. 4A and described above, inclined surface 103 extends from the first end of the cylindrical surface to the location of theshoulder 76. Theinner housing 69, which includesshaft 68 andshoulder wall 76, additionally includes aflange surface 80 for fixedly connecting theinner housing 69 to the differential 52. Theflange surface 80 may be connected to the differential 52 using bolts, screws, welding, or any other known method of fixedly attaching pieces together. By fixedly attached, it is intended that the inner housing and the differential do not rotate relative to one another. The inner housing may also be provided with a secondcylindrical surface 82 extending from the shouldertop edge 78 to theflange 80 joining the structures. - The oscillating
hub 90, as described above, has a generally v-shapedinner contact surface 94 that corresponds to the generally v-shapedbearing assembly 100 about with the oscillating joint 40 rotates. Theinner contact surface 94 surrounds theshaft 68 and contacts at least theinboard bearing 102 and theoutboard bearing 104. The oscillatinghub 90 is also provided with anouter flange 170 positioned at theoutboard side 172 of theoscillating hub 90. Theouter flange 170 is provided so that the oscillatinghub 90 can be fixedly connected to thedrive casing 30. The oscillatinghub 90 may be connected to the drive casing using afastening device 174 such as bolts, screws, or any other known method of fixedly attaching pieces together. - The generally v-shaped arrangement of the bearing
assembly 100 provides an even wear profile in theoscillation joint 40. By providing theinboard bearing 102 andoutboard bearing 104 at angles tailored to the dimensions of the oscillation joint and to the forces experienced within the joint, an extended life wear profile is provided as compared to a similar oscillation joint using a thrust washer and thrust ring arrangement. In addition to handling the standard vertical forces that are experienced within the joint, the oscillation joint also handles horizontal forces that would be experienced in a side impact to a wheel. Basically, the impact force is transmitted to the sloping v-shaped portion of the oscillation joint bearing and due to its shape, any wear to the bearing does not result in “play” or a “wear-gap” at the bearings. - Additionally, the axial positioning of the oscillation
joint bearing assembly 100 on theshaft 68, as well as adjustment of axial gaps, can be achieved through the use of shims (not shown). The shims are formed from thin metallic washers sized to fit over thecylindrical portion 70 of theshaft 68. If required, the shims may be placed between either theshoulder wall 76 and thebase end 144 of theinboard collet 140, between theannular mounting plate 160 and thebase end 154 of theoutboard collet 150, or both. - For the
inboard bearing 102, the angle ⊖1 for thefirst bearing surface 106 is perpendicular to theforce couple 190 resisting the tipping moment. This angle is parallel to a line through the contact point on theinboard bearing 102 andoutboard bearing 104. For theoutboard bearing 104, the angle ⊖2 for thesecond bearing surface 108 is perpendicular to the angle of the vector sum of the reaction force due to theforce couple 190 resisting the tipping moment and thevertical load 192 which is reacted to by the outboard bearing 104 (seeFIG. 7 ). The optimal angle of theinboard bearing 102 and theoutboard bearing 104 as calculated may vary by plus or minus 5 degrees based on the rim and tire selection for a particular machine. Variables for calculating the optimal angles or a variety of machines having an oscillation joint are contained in Table 1. - The results for determining the optimal angles based on the below calculation for determining the optimal angle are contained in Table 2.
- Distance between contact points=(inboard bearing outer diameter/2+outboard bearing outer diameter/2)2+((Outboard Bearing Axial)2)0.5
- Angle off of vertical (radians)=as in (axial distance between outer edges of sleeve bearings/distance between contact points)
- Inboard Bearing Optimal Angle off of vertical (degrees)=angle off of vertical (radians)×180/π.
- Ratio of force couple reaction magnitude to tire force vertical load=joint center to tire center axial/distance between contact points
- Vertical component of ratio=sin(angle off of vertical)×joint center to tire center axial/distance between contact points
- Horizontal component of ratio=cos(angle off of vertical)×x joint center to tire center axial/distance between contact points
- Vertical sum=1+vertical component of ratio
- Angle of resultant vector from vertical (radians)=a tan(horizontal component of ratio/vertical sum)
- Angle of resultant vector from vertical (degrees)=Angle of resultant vector from vertical (radians)×180/π.
- Outboard bearing optimal angle off of vertical=90−Angle of resultant vector from vertical (degrees)
- The results for determining the optimal angles based on the above formulas are contained in Table 2. The results are summarized in Table 3
-
TABLE 1 Machine Units 1 2 3 4 5 6 7 8 9 10 11 Axial Dimensions Inboard mm 0 0 0 0 0 0 0 0 0 0 0 Bearing Axial Outboard mm 159 159 159 159 159.2 159.2 160.2 160.2 160 176 128 Bearing Axial Joint Center mm 572.8 572.8 572.8 572.8 601 601 601.5 601.5 689.3 688 929 to Tire Center Axial Radial Dimensions Inboard mm 300 300 300 300 300 303 300 300 402 447 784 Bearing Outer Diameter Outboard mm 309 309 309 309 309 309 309 309 405 450 784 Bearing Outer Diameter -
TABLE 2 Calculations Machine Units 1 2 3 4 5 6 7 8 9 10 11 Distance mm 344 344 344 344 344 345 344 344 434 481 794 between contact points Angle off rad 0.48113 0.48113 0.48113 0.48113 0.48165 0.47963 0.48422 0.48422 0.37744 0.37431 0.16184 of vertical Inboard deg 27.5667 27.5667 27.5667 27.5667 27.5963 27.4809 27.7438 27.7438 21.6259 21.4464 9.2726 bearing optimal angle off of vertical Ratio of ratio 1.667 1.667 1.667 1.667 1.7488 1.7420 1.74788 1.74788 1.5877 1.4293 1.1695 force couple reaction magnitude to tire force vertical load Vertical 0.7715 0.7715 0.7715 0.7715 0.7101 0.8039 0.8137 0.8137 0.5852 0.5226 0.1884 Com- ponent of Ratio Horizontal 1.4779 1.4779 1.4779 1.4779 1.5498 1.5455 1.5469 1.5469 1.4759 1.3303 1.5418 Com- ponent of Ratio Vertical 1.7715 1.7715 1.7715 1.7715 1.8101 1.8039 1.8137 1.8137 1.5852 1.5230 1.8884 Sum rad 0.6953 0.6953 0.6953 0.6953 0.7081 0.7084 0.7062 0.7062 0.7497 0.7181 0.7708 Angle of resultant vector from vertical Angle of deg 39.83657 39.83657 39.83657 39.83657 40.57051 40.58855 40.46192 40.46192 42.9574 41.1444 44.16226 resultant vector from vertical Outboard deg 50.16343 50.16343 50.16343 50.16343 49.42949 49.41145 49.53808 49.53808 47.0426 48.8556 45.83774 bearing optimal angle off of vertical -
TABLE 3 Results Summary Machine unit 1 2 3 4 5 6 7 8 9 10 11 Optimal deg 28 28 28 28 28 27 28 28 22 21 9 inboard bearing angle Optimal deg 50 50 50 50 49 49 50 50 47 49 46 outboard bearing angle - The disclosed oscillation joint and bearing assembly may be an inexpensive, effective solution for reducing bearing wear in the oscillation joint of a machine.
- It will be apparent to those skilled in the art that various modifications and variations may be made to the disclosed oscillation joint and bearing assembly. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the disclosed oscillation joint and bearing assembly. It is intended that the specification be considered as exemplary only, with a true scope being indicated by the following claims and their equivalents.
Claims (18)
1. A bearing assembly to rotatably support an oscillating hub rotatably connected to a shaft, the bearing assembly comprising:
an inboard bearing defining a first frustoconical ring having a first bearing surface disposed thereon, and
an outboard bearing defining a second frustoconical ring having a second bearing surface disposed thereon,
wherein said first bearing surface of said first frustoconical ring and said second bearing surface of said second frustoconical ring being positioned relative to one another to form a generally v-shaped bearing interface between said shaft and said hub, wherein the bearing assembly further comprises an outboard collet comprising an apical end, a base end, and a supporting face, the supporting face of the outboard collet supporting the outboard bearing on an interior surface opposite the second bearing surface, and wherein the bearing assembly further comprises a mounting plate configured for mounting to an end face of the shaft and for retaining the outboard collet in the bearing assembly.
2. The bearing assembly of claim 1 , wherein the first bearing surface is disposed between a base end and an apical end of the inboard bearing, the apical end having an aperture with a diameter of 225 mm to 750 mm.
3. The bearing assembly of claim 2 , wherein the first bearing surface is at an angle of 9 degrees to 28 degrees relative to the base end of the inboard bearing.
4. The bearing assembly of claim 1 , wherein the second bearing surface is disposed between a base end and an apical end of the outboard bearing, the apical end having an aperture with a diameter of 225 mm to 750 mm.
5. The bearing assembly of claim 4 , wherein the second bearing surface at an angle of 46 to 50 degrees relative to the base end of the outboard bearing.
6. The bearing assembly of claim 1 , wherein the inboard bearing and outboard bearing have a substantially uniform thickness of 3 mm to 10 mm.
7. The bearing assembly of claim 1 , wherein the inboard bearing has a base end having an outboard diameter of 300 mm to 784 mm.
8. The bearing assembly of claim 1 , wherein the outboard bearing has a base end having an outer diameter of 309 mm to 784 mm.
9. The bearing assembly of claim 1 , wherein the inboard bearing and the outboard bearing are formed from a non-metallic material.
10. The bearing assembly of claim 9 , wherein the non-metallic material is a phenolic cotton and resin compound.
11. The bearing assembly of claim 1 , wherein the bearing assembly further comprises an inboard inclined surface extending from an inboard side of the shaft comprising a supporting face, the supporting face of the inboard inclined surface supporting the inboard bearing on an interior surface opposite the first bearing surface.
12. The bearing assembly of claim 11 , wherein the inboard inclined surface supporting surface is at an angle of degrees to 28 degrees relative a line perpendicular with the central axis of the shaft.
13. (canceled)
14. The bearing assembly of claim 13 , wherein the outboard collet comprises a cylindrical through bore having a diameter of 225 mm to 750 mm, the base end projects perpendicular to the through bore, and the base end has an outer diameter of 309 mm to 784 mm.
15. The bearing assembly of claim 13 , wherein the outboard collet supporting surface is at an angle of 46 degrees to 50 degrees relative to the base end of the outboard collet.
16.
17. The bearing assembly of claim 1 , wherein the mounting plate and the outboard collet are a single piece.
18. The bearing assembly of claim 1 , wherein the bearing assembly further comprises a inboard collet comprising an apical end, a base end, and a supporting face, the supporting face of the inboard collet supporting the inboard bearing on an interior surface opposite the first bearing surface, wherein the inboard collet comprises a cylindrical through bore having a diameter of 225 mm to 750 mm, the base end projects perpendicular to the through bore, and the base end has an outer diameter of 300 mm to 784 mm, and wherein the inboard collet supporting surface is at an angle of 9 degrees to 28 degrees relative to the base end of the inboard collet.
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US11084340B2 (en) * | 2017-08-01 | 2021-08-10 | Caterpillar Sarl | Hitch assembly for articulated machines |
EP4212746A1 (en) * | 2022-01-13 | 2023-07-19 | Artisan Vehicle Systems Inc. | An oscillation bearing arrangement of a mobile mining machine and a mobile mining machine |
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CN104956102A (en) | 2012-12-25 | 2015-09-30 | 日本精工株式会社 | Tapered roller bearing |
CN105143697A (en) * | 2013-04-04 | 2015-12-09 | 日本精工株式会社 | Tapered roller bearing-use resin made cage and tapered roller bearing provided with such cage |
US9540099B2 (en) * | 2014-08-15 | 2017-01-10 | Goodrich Corporation | Compliant lower bearing with tapered outer diameter |
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US386051A (en) | 1888-07-10 | Leather coil for washers | ||
US3578828A (en) * | 1969-02-18 | 1971-05-18 | Kaman Aerospace Corp | Split-race bearing construction |
US4936634A (en) | 1988-08-25 | 1990-06-26 | Deere & Company | Removable wheel tread adjusting device |
JPH06300042A (en) * | 1993-04-13 | 1994-10-25 | Nippon Seiko Kk | Static pressure gas bearing |
SE519042C2 (en) | 1998-04-22 | 2002-12-23 | Winkvistbolagen Smidesprodukte | Clamping sleeve for absorbing axial forces in a mechanical joint, use of clamping sleeve and method for axially fixing drives stored on a shaft with such clamping sleeve |
US6609765B2 (en) | 2001-06-26 | 2003-08-26 | Deere & Company | Adjustable wheel and axle assembly for a work vehicle |
US7959169B2 (en) | 2008-03-31 | 2011-06-14 | Caterpilar Inc. | Chain driven independent suspension having an oscillation joint |
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US11084340B2 (en) * | 2017-08-01 | 2021-08-10 | Caterpillar Sarl | Hitch assembly for articulated machines |
EP4212746A1 (en) * | 2022-01-13 | 2023-07-19 | Artisan Vehicle Systems Inc. | An oscillation bearing arrangement of a mobile mining machine and a mobile mining machine |
WO2023135566A1 (en) * | 2022-01-13 | 2023-07-20 | Artisan Vehicle Systems, Inc | A mobile mining machine comprising an oscillation bearing arrangement |
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