Bearing arrangement for roller bodies in compacting rollers

An improved roller bearing structure is provided which is particularly applicable for use in vibratory roller compactors. The roller bearing structure includes a first radially outer bearing ring connected to a non-rotating part, a second radially inner bearing ring connected to a rotating part, and rollers engaging the radially inner and outer surfaces of said first and second bearing rings, respectively. Said first and second bearing rings and the rollers located therebetween comprise a roller bearing ring mount. The radially inner surface of the inner bearing ring is provided with an internal gearing for engagement with a drive pinion to provide a driving input to the rotating part to which the inner bearing ring is secured.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
This invention relates generally to improved roller bearing structures and 
more particularly, but not by way of limitation, to roller bearing ring 
mounts for use in vibratory roller compactors. 
2. Description of the Prior Art 
The invention relates to a bearing arrangement for roller bodies in 
compacting rollers, comprising anti-friction bearings. 
Conventionally ball or roller bearings have been used for such bearing 
arrangements, or tapered-roller bearings, if also axial forces have to be 
absorbed. 
Such conventional bearings are mounted with press fit with the cylindrical 
peripheral surface of their outer rings within a corresponding bore of one 
part, and are mounted with the cylindrical inner surface of the inner ring 
on a correspondingly cylindrical outer surface of the outer part. This 
presents manufacturing problems. 
At first, it is necessary to machine the bore and the outer surface with 
high accuracy. Thus the diameter of such bearings is limited for this 
reason alone. 
As, with roller bodies of vibration rollers mounted in the vehicle frame in 
vibration absorbing manner, for example through rubber cushions, tilting 
torques will act on the bearing arrangement on one side of the roller body 
and cannot be taken up by one single bearing having a rather small radius, 
prior art designs (for example U.S. Pat. No. 3,486,427) require two 
axially spaced bearings (elements 10 and 11 of U.S. Pat. No. 3,456,427) on 
an axle provided on the vehicle frame. Thereby the space required axially 
between vehicle frame and the end (roller bottom) (elements 16 of U.S. 
Pat. No. 3,486,427) of the roller body becomes rather large. Therefore 
this end wall which supports and reinforces the cylindrical roller body is 
arranged rather far inwards of the end of the roller body. This impairs 
the rigidity of the roller body, and this, in turn, is particularly 
disadvantageous with vibrating rollers. 
By inserting the outer ring of the bearing into the bore with press fit, 
and by placing the inner ring, also with press fit, on the cylindrical 
outer surface, the play of the bearing is changed in a way hard to 
control. Also this presents problems in particular with vibrating rollers. 
Namely if the play becomes too large, there will be the risk of the 
bearing getting worn. If, however, the play is too small, the bearing may 
run hot. 
Furthermore it is known to mount a disc-shaped part by means of two roller 
bearings on an axle provided on the vehicle frame and to attach a separate 
ring with an internal gear to this disc-shaped part, the disc-shaped part 
being in driving engagement with the roller through rubber cushions (U.S. 
Pat. No. 3,486,427). This internal gear meshes with a drive pinion which 
is provided on the shaft of a hydraulic drive motor. Apart from the 
problems already explained hereinbefore, the axis of rotation in this 
prior art arrangement is defined by the bearings so that the gear ring has 
to be aligned accurately concentric to the axis of rotation thus defined. 
With another prior art design (German patent specification No. 2,107,793) a 
hollow axle is affixed to the vehicle frame. A drive pinion is mounted in 
this hollow axle through two axially spaced ball bearings. The drive 
pinion is coupled with a hydraulic motor arranged coaxial to the hollow 
axle. An annular housing is mounted on the hollow axle through two 
additional ball bearings, this housing being connected to the roller body 
and having an annular aperture in its inner wall. A stationary gear ring, 
which is provided on the outside of the hollow axle, extends into this 
aperture. This gear ring is engaged by a pinion which is mounted in the 
annular housing by means of a shaft through ball bearings. An intermediate 
gear is provided on this shaft outside the annular housing and meshes with 
the drive pinion. The pinion mounted in the housing is driven through the 
drive pinion and the intermediate gear. Thus the former pinion rolls on 
the stationary gear ring and causes the housing and the roller body 
attached thereto to rotate. 
This arrangement is a most complex one. All bearing arrangements comprise 
conventional ball bearings with the problems explained in the beginning. 
So-called "ring mounts" are known for mounting machines, such as excavating 
machines, which are mounted on a chassis for rotation about a vertical 
axis. Such a ring mount is a roller or journal bearing having an inner 
ring and an outer ring, with which the outer ring is not located in a bore 
and the inner ring is not placed on a cylindrical outer surface, but with 
which both rings are affixed flange-like with their end faces to the 
chassis and to the rotatable machine unit by means of axial bolts or the 
like. 
SUMMARY OF THE INVENTION 
An improved roller bearing structure is provided which is particularly 
applicable for use in vibratory roller compactors. The roller bearing 
structure includes a first radially outer bearing ring, a second radially 
inner bearing ring, and rollers engaging the radially inner and outer 
surfaces of said first and second bearing rings, respectively. Said first 
and second bearing rings and the rollers located therebetween comprise a 
roller bearing ring mount. Said roller bearing ring mount differs from 
conventional roller bearing structures in that the radially inner and 
outer bearing races of a conventional bearing structure are attached to an 
outer cylindrical surface and an inner cylindrical bore, respectively, by 
press fitting, whereas the radially inner and outer bearing rings of the 
roller bearing ring mount of the present invention are secured to a 
rotating and a non-rotating part, respectively, of the structure in which 
the bearing is used, by means of a plurality of threaded screws or other 
such connecting means, thereby eliminating the need for precise machining 
of shafts or bores to accommodate conventional press fit bearings. The 
rollers provided between the first and second bearing rings of the present 
invention preferably comprise a crossed roller bearing. This construction 
allows the radially inner surface of the inner bearing ring to be provided 
with an internal gearing for engagement with a drive pinion to provide a 
driving input to the rotating part to which the inner bearing ring is 
secured. 
The roller bearing structure of the present invention is particularly 
applicable to use in a vibratory compacting roller such as may be used for 
rolling and compacting earth or asphalt on a road bed. Such a vibratory 
compacting roller typically includes a pair of spaced roller bearings, 
generally mounted upon a non-rotating part such as a fixed axle of a 
vehicle upon which the roller is mounted, and engaging with their outer 
peripheral surfaces a rotating part, namely the compacting roller which 
may be referred to as a roller body. Any number of configurations can be 
used to mount a compacting roller upon a chasis or vehicle, but all such 
mounting systems can be generalized in that they include a non-rotatable 
part, e.g., the vehicle chasis, and a rotatable part, e.g., the compacting 
roller, which are joined together by means of roller bearings which engage 
said rotatable and non-rotatable parts. 
According to the invention at least one of the roller bearings is an 
anti-friction bearing ring mount, one bearing ring of which is attached to 
a non-rotatable part by means of attachment elements arranged along the 
periphery of said one bearing ring, and the other bearing ring of which is 
attached, by means of attachment elements arranged along the periphery of 
said other bearing ring to a part rotatable with the roller body. 
It has been found that such a bearing arrangement offers considerable 
advantages for compacting rollers, in particular for vibrating rollers. 
The bearings are not inserted with press fit into a bore nor placed on an 
outer surface, whereby the requirement of accurately machining cylindrical 
surfaces is eliminated. 
The assembly and disassembly, also in the case of repairs, is facilitated, 
as no pulling out or off of bearing rings is required. 
There is no risk of press fits wearing. 
As no cylindrical bores in the roller parts for accomodating the bearing 
need to be machined, the diameter of such bores being limited for 
manufacturing reasons, the diameter of the ring mount may be made 
sufficiently large. Thanks to this large diameter of the ring mounts, the 
accuracy with which the contact surfaces are machined plane needs not to 
be too high. 
The following additional advantages are offered with vibrating rollers: 
The inner and outer rings have a well-defined play, which is determined by 
their dimensions only and cannot be changed by the mounting of the 
bearing. Therefore the bearing play may be made so small, in controlled 
manner, that the displacements of the pumps caused by the vibrations can 
be kept small and undue wear caused thereby is avoided. 
With roller bodies held in a vehicle frame in vibration absorbing manner, 
tilting torques have to be taken up. As the diameter of the ring mount can 
be made sufficiently large, the ring amount is in the position to absorb 
the acting tilting torques with rather small forces acting on a long lever 
arm, contrary to conventional roller bearings. Thus the bearing 
arrangement may comprise a single rather flat ring mount on each side 
instead of two axially spaced conventional roller bearings, as in the 
prior art. Thus relatively little space is required axially at the end of 
the roller body. 
No machine parts for accomodating the inner ring of the ring mount are 
required within the ring mount. Thus the space within the ring mount is 
free for the arrangement or passage of drive means, either for the 
propulsion or for driving a vibration generator. 
Preferably the roller bearing of the ring mount is a crossed-roller 
bearing. 
Such a crossed-roller bearing permits axial forces and tilting torques to 
be taken up, while only rolling friction will occur. 
The propulsion may be effected in that one bearing ring of the ring mount 
has a gearing which is in engagement with a drive pinion. 
Thus there will be no problems with regard of the mutual alignment of the 
bearing and the gear ring. 
It is therefore an object of the present invention to provide an improved 
roller bearing structure. 
Another object of the present invention is to provide a roller bearing 
structure for use in vibratory roller compactors which eliminates the need 
for the provision of closely machined bores and outer cylindrical surfaces 
for the mounting of roller bearings therebetween. 
Yet another object of the present invention is the provision of a roller 
bearing ring mount which provides a radially inner gear on the inner 
surface of an inner bearing ring of the roller bearing mount. 
Another object of the present invention is the provision of an economically 
constructed and maintained roller bearing structure. 
And another object of the present invention is the provision of an improved 
vibratory compacting roller having a roller bearing mount with crossed 
bearings engaging a roller body and a vehicle upon which the roller body 
is mounted. 
Other and further objects, features and advantages of the present invention 
will be readily apparent to those skilled in the art upon a reading of the 
description of preferred embodiments which follows when taken in 
conjunction with the accompanying drawings.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION 
An embodiment of the invention will now be described with reference to the 
accompanying drawing, which is a longitudinal sectional view of a roller 
body having a bearing arrangement of the invention. 
Numeral 10 designates the cylinder of the roller body. Roller bottoms or 
end walls 12 and 14 are provided on the cylinder 10. The housing 16 of an 
unbalance vibrator extends between the roller bottoms. An unbalance 
vibrator 18 is mounted in the roller bottoms through roller bearings 20 
and 22. The propulsion drive of the roller body is effected by a 
hydrostatic motor 24 trough a miter gear 26 and a drive pinion 28. This 
drive pinion 28 engages an internal gearing 30 of the inner ring 32 of the 
ring mount 34. This inner ring 32 is screwed flange-like to a cushion 
spider 36, which, in turn, is attached to the roller bottom 12 through 
rubber cushions 38. That is, an axially inner end face or periphery 39 of 
the inner ring 32 is connected to the cushion spider 36, which may also be 
described as a vertical radially extending plate of the roller body, by 
means of a plurality of axial attachment elements or screws 41. The outer 
ring 40 of the ring mount 34 is screwed flange like to first contact plate 
42 affixed to the vehicle frame. That is, an axially outer end face or 
periphery 43 of the outer ring 40 is connected to the first contact plate 
42, which may also be referred to as a radially extending plate of the 
vehicle frame, by a plurality of attachment elements or screws 41. Inner 
ring and outer ring of the ring mount are mounted on each other through a 
cross-roller bearing. 
The inner ring 46 of a second ring mount 48 is screwed to a second contact 
plate 44, which is also attached to the vehicle frame. The outer ring 50 
of the ring mount 48 is screwed flange-like to an intermediate member 52, 
which is attached to the roller bottom 14. The inner ring 46 and the outer 
ring 50 of the ring mount 48 are also mounted on each other through a 
crossed-roller bearing. 
A coupling 54 is arranged within the ring mount 48. A hydrostatic motor 56 
mounted on the contact plate 44 drives the unbalance vibrator 18 through 
this coupling. The contact plate 44, in turn, is connected to the vehicle 
frame through rubber cushions 58. A crossed-roller bearing is a roller 
bearing, in which the axes of the rollers or roller elements 60 form an 
angle, for example of 45.degree., with the axis of the bearing, the axes 
of the rollers being inlined alternatingly towards one or the other side 
with respect to the axis of the bearing. The bearing rings have 
correspondingly conical rolling surfaces for the two sets of rollers. 
The improved roller bearing construction of the present invention is 
particularly suited for use with a vibratory compacting roller apparatus 
of the type having a rotatable part such as the cylinder 10, a 
non-rotatable part such as the vehicle frame which includes the contact 
plates 42 and 44, and an anti-friction bearing mounted therebetween such 
as the bearing ring mount 34 or 48. 
Thus, the improved roller bearing structure of the present invention is 
well adapted to carry out the objects and attain the ends and advantages 
mentioned as well as those inherent therein. While presently preferred 
embodiments of the invention have been described for the purpose of this 
disclosure, numerous changes in the construction and arrangement of parts 
can be made by those skilled in the art, which changes are encompassed 
within the spirit of this invention as defined by the appended claims.