WO1997016959A1

WO1997016959A1 - Round baler having double bearing supported tailgate roller

Info

Publication number: WO1997016959A1
Application number: PCT/US1996/016380
Authority: WO
Inventors: John Dale Anderson; Ferol S. Fell; Craig Pecenka; Howard Ratzlaff
Original assignee: Hay and Forage Industries
Current assignee: Hay and Forage Industries
Priority date: 1995-11-09
Filing date: 1996-10-15
Publication date: 1997-05-15
Anticipated expiration: 1998-05-09
Also published as: AU7443196A

Abstract

A round baler (10) uses double bearing assemblies to journal each end of its bale supporting roll (148) where continuous exposure to the harmful effects of trash, dirt and moisture is at a high level. Each set of double bearings has an outboard bearing (120) that remains exposed to the elements at that location, as well as a second, back-up bearing (118) safely tucked away from the elements in a protected, inboard position. The outboard bearing (120) serves not only as a means for journaling the roll (148), but also as a means for shielding and protecting the inboard bearing (118) against contamination.

Description

ROUND BALER HAVING DOUBLE BEARING SUPPORTED TAILGATE ROLLER

Background ofthe Invention

1. Field ofthe Invention

The present invention relates generally to round balers and, more particularly, to a special bearing arrangement for the bale support roll of a round baler to reduce the risk of fires caused by undetected contamination, failure, and overheating of current bearing assemblies for such rolls.

2. Discussion of Prior Art

The bearing assemblies for the bale support roll on a round baler are typically exposed to exceptionally high operating loads and contamination from trash, crop material and other debris. Once contaminated with debris, the bearings may fail and quickly overheat, leading to possible fires.

Various systems have been devised for minimizing the exposure of bearing assemblies to crop material and other trash, and for preventing ingress of such material into the vicinity ofthe assemblies. For example, rolls have been secured to stub shafts which project outwardly through the baler sidewalls where they are supported by bearing assemblies on the exterior ofthe baler. Additionally, rolls have been provided with radially projecting collars or cleanout discs adjacent the ends thereof for rotational movement therewith. The collars fling material outwardly away from the roll. However, these conventional clean-out devices are not appropriate for the support roll.

Thus, a need exists for structure that deals with the bearing failure problem as it relates specifically to the support roll.

Objects and Summary ofthe Invention

Accordingly, an important object ofthe present invention is to provide a way of decreasing the risk of fire from failed bearings at the journal points of the support roll on a round baler. Another important object ofthe present invention is to provide structure for rotatably mounting the support roll to the sidewalls, which can withstand the relatively high loads and contamination associated with the support roll. A further object of the invention is to increase the time for the operator to detect a contaminated and failing bearing before conditions become so bad that the failure starts a fire. Finally, an object ofthe present invention is to improve upon conventional round balers by reducing shut-down time associated with failure ofthe current single bearing assemblies.

In accordance with these and other objects evident from the following description ofa preferred embodiment ofthe invention, the round baler has bale forming mechanism cooperating with first and second laterally spaced sidewalls to define a baling chamber. The mechanism includes a support roll located in a lower portion of the chamber to carry weight ofthe bale as it is formed. Moreover, the baler includes a first pair of bearing assemblies for rotatably supporting one end ofthe support roll on the first sidewall, and a second pair of bearing assemblies for rotatably supporting the other end ofthe support roll on the second sidewall.

Of course, the support roll may be entrained by a number of transversely spaced belts and positioned adjacent the crop infeed opening ofthe baling chamber. If desired, the support roll may be carried on the tailgate ofthe baler.

Preferably, each pair of bearing assemblies includes an inboard assembly in juxtaposition with an outboard assembly. The support roll is preferably tubular and sealingly receives the juxtaposed bearing assemblies therein so that the outboard assemblies seal the inboard assemblies from environmental contamination, while the exposed, outboard assemblies may be readily inspected by the operator. Further, a transversely extending stationary through-shaft is concentrically disposed within the roll to ensure proper alignment ofthe bearing assemblies inteφosed between the through- shaft and support roll.

Brief Description ofthe Drawing Figures

A preferred embodiment ofthe invention is described in detail below with reference to the attached drawing figures, wherein:

FIG. 1 is a vertical cross-sectional view ofa round baler having a support roll which is provided with the double bearing support structure constructed in accordance with the principles ofthe present invention, the near sidewall being removed to reveal internal details of baler construction; FIG. 2 is a fragmentary, horizontal cross-sectional view ofthe support roll supported by a pair of bearing assemblies at each end thereof, in accordance with the present invention, particularly illustrating the constructional details of the preferred support roll and structure for mounting the same to the baler; FIG. 3 is an enlarged, fragmentary, horizontal cross-sectional view ofthe right end of the support roll depicted in FIG. 2, particularly illustrating the internal details ofthe bearing assemblies and the structure for fixing a through-shaft supporting the bearing assemblies to a support arm extending from the baler sidewall; FIG. 4 is an end view ofthe right end ofthe support roll depicted in FIG.

2, particularly illustrating the concentricity ofthe through-shaft, bearing assemblies, hub and support roll;

FIG. 5 is side elevational view ofthe support arm, particularly illustrating the ring for co plementally receiving the marginally flattened end ofthe through-shaft; and

FIG. 6 is an enlarged, fragmentary, horizontal cross-sectional view similar to FIG. 3, but illustrating prior art structure for supporting the support roll on the sidewall including a single bearing assembly and a stub shaft.

Detailed Description ofthe Preferred Embodiment

Turning now to FIG. 1, the round baler 10 selected for illustration generally includes a chassis 12 having ground wheels 14 and a forwardly extending tongue 16 that is adapted for connection with a towing vehicle (not shown). The chassis 12 carries a pair of upright, laterally spaced sidewalls 18 and 20 (see also FIG. 2) which cooperate to define a space within which bale forming and bale wrapping operations may be carried out as the baler is advanced across a field. Within the space defined by the sidewalls 18 and 20, the baler 10 further includes bale forming mechanism 22 for compacting and rolling crop material into a round bale.

The sidewalls 18,20 present stationary forward portions fixed to the chassis 12 by suitable means and rearward portions swingably attached to the forward portions by a pivot assembly 24. The rearward portions of the sidewalls 18,20 cooperatively define a tailgate 26 which is swingable between an open, discharge position (not shown), in which the tailgate 26 has sufficiently raised to allow a completely formed bale to be discharged from the baler 10, and a closed, baling position (FIG. 1), in which bale wrapping and rolling operations are performed.

As previously mentioned, the sidewalls 18,20 cooperatively define a space within which bale forming and bale wrapping operations may be carried out. In the illustrated embodiment, the bale forming mechanism 22 and sidewalls 18,20 cooperate to define a so-called "variable chamber," belt-type machine, wherein the baling chamber is initially relatively small and then grows progressively larger as the bale increases in diameter within the baler 10. It will be appreciated, however, that the principles ofthe present invention are also applicable to a "fixed chamber" machine in which the dimensions ofthe baling chamber are at least substantially constant throughout the baling cycle, with the diameter ofthe chamber corresponding substantially with the diameter ofthe full size bale when completed.

With the forgoing caveat in mind, the bale forming mechanism 22 ofthe variable chamber baler illustrated herein include a series of cooperating belts and rolls supported by the sidewalls 18,20 for rolling and compacting a bale as it forms within the baler 10. As shown in FIG. 1, the baler 10 is provided with a plurality of laterally extending, stationary rolls including a lower drive roll 28, upper drive roll 30, idler rolls 32,34,36,38,40,42, a trash clearing roll 44, and a support roll 46. The rolls 28-46 span the sidewalls 18,20 are arranged in a general circular pattern viewing FIG. 1 for guiding a plurality of endless, laterally spaced, side-by-side belts 48 as the belts 48 are driven linearly during bale formation and wrapping. Although not illustrated in detail, it will be appreciated that the trash clearing roll 44 includes a number of laterally spaced slats 50 received within the spaces defined between the belts 48 for clearing trash from the moving belts 48.

The bale forming mechanism further includes a pair of movable slack takeup rolls 52 and 54 mounted near the upper portion ofthe baler 10 on downwardly spring biased arm structure 56 to maintain tension on the belts 48, yet permit the paying out of stored slack as the bale increases in diameter during formation. Near the fore- and-aft center ofthe baler 10, the belts 48 are looped under the lower drive roll 28, over the upper idler roll 38, and under the support roll 46 to present a pair of opposed, front and rear runs 48a and 48b, which are initially generally upright, as illustrated in phantom in FIG. 1, but which become bowed out in fore-and-aft directions, as illustrated in solid lines, as the bale grows beyond its initial starting core dimensions. A pair of retaining rolls 58 and 60 are mounted on a second swingable arm structure 62 that is also spring biased downwardly to the phantom line position in FIG. 1; the retaining rolls 58, 60 receiving the belt runs 48a and 48b therebetween so as to form a baling chamber 64 between the runs 48a, 48b which is bounded at the sides by the sidewalls 18,20.

Initially, the chamber 64 assumes a generally upright, somewhat triangular configuration, as shown in phantom lines in FIG. 1, with the retaining rollers 58, 60 at the apex ofthe chamber 64. Thereafter, the chamber 64 becomes distended and circular in transverse configuration as the growing bale pushes forwardly on the belt run 48a and rearwardly on the belt run 48b to cause additional slack to be paid out and for the arm 62 to rise as additional hay is progressively added to the bale.

The chamber 64 is open at the bottom to present a crop infeed entrance 66 that is defined between the support roll 46 and a starter roller 68. A crop pickup mechanism 70, supported generally below the entrance 66 and forwardly ofthe support roll 46, is operable to lift crop material off the field as the baler 10 is advanced and to feed the material into the chamber 64 via the entrance 66.

The drive rolls 28 and 30 are drivingly coupled with the power source of the towing vehicle to drive the belts 48 and are driven in clockwise directions viewing

FIG. 1, as indicated by arrows 72 and 74, respectively. Thus, when the baling chamber 64 is in its initial upright condition, as shown in phantom in FIG. 1, the front run 48a is moving generally downwardly and forwardly while the rear run 48b is moving generally upwardly. Consequently, hay introduced into the chamber 64 via the entrance 66 is acted upon by the upwardly moving rear run 48b and the downwardly moving front run

48a so as to tumble forwardly and coil into a growing bale. Assisting in the initial starting ofthe core and the coil-up action is the starting roller 68 which is driven in a clockwise direction viewing FIG. 1, as indicated by arrow 76.

During the formation ofthe bale, which is illustrated in its final size in solid lines in FIG. 1 and is denoted by the numeral 78, a small amount of hay is sloughed off the bale 78 due to slippage between the belts 48 and the surface ofthe bale 78, and some of that residue tends to collect within the open area immediately above the roll 28 and forwardly of the front belt run 48a. However, such accumulating material is immediately discharged from that area by the action of the cleanout discs, broadly denoted by the numeral 80, in FIG. 3 which protrude into the collecting region and have their protruding portions moving downwardly in a direction oppositely to the upwardly moving belts 48 in that area. Such cleanout discs 110 are the subject of United States Patent No. 5,097,760, entitled "POWERED TRASH REMOVAL APPARATUS FOR ROUND BALER", assigned of record to the assignee ofthe present invention. Once the bale 78 is fully formed, it is desirable that the bale be tightly wrapped with either twine or a web-type wrapping material. The illustrated baler 10 is provided with a swingable twine dispensing tube 82 located adjacent the front ofthe baler which performs in the usual way for dispensing a supply of twine to the bale 78. However, it is entirely within the ambit ofthe present invention to provide the baler 10 with a net wrapping apparatus (not shown) similar in principle to the construction disclosed in United States Patent No. 5,216,873, entitled "WRAPPER CUTOFF MECHANISM FOR ROUND BALERS", assigned of record to the assignee of the present invention.

CONVENTIONAL STRUCTURE FOR MOUNTING SUPPORT ROLL 46

FIG. 6 shows that in the past, the support roll 46 has been rotatably mounted to the sidewalls 18,20 by a single pre-packed bearing assembly, generally designated 84, at each end ofthe support roll 46 (only the bearing assembly adjacent sidewall 20 being shown). Each bearing assembly 84 includes an inner race 86, a concentric outer race 88 and a ball-bearing ring 90 inteφosed therebetween to allow relative rotational movement between the inner race 86 and outer race 88. A pair of elastomeric, resilient sealing rings 92,94 are fixedly secured to the outer race 88 to span the annular opening between the inner and outer races 86,88. A radial innermost boundary of the rings 92,94 sealingly engages the inner race 86 to contain a grease packing surrounding the ball-bearing ring 90. The inner race 86 includes a pair of annular retainer clips 96,98 projecting from the outer periphery thereof to maintain the sealing engagement between inner race 86 and sealing rings 92,94. Although the rings 92,94 and clips 96,98 are in touching relationship, it will be appreciated that this configuration and corresponding frictional interengagement between the rings 92,94 and clips 96,98 do not hinder relative rotational movement between the inner and outer races.

A hub 100 seats within the tubular support roll 46 and is secured thereto by mechanical fasteners, such as set screws (not shown), although other suitable means may be used to secure the hub 100 to the support roll 46 such as welding or press-fitting the hub 100 therein. The hub 100 snugly circumscribes the outer race 88 ofthe bearing assembly 84 such that the support roll 46, hub 100 and outer race 88 rotate with one another. The hub 100 presents an inner step 102 which prevents lateral inward movement ofthe assembly 84.

On the other hand, rotational movement ofthe inner race 86 is checked by a stub shaft, generally designated 104, projecting laterally inwardly from each ofthe sidewalls 18,20. A threaded set screw 106 extends through a chamfered opening 107 within the sidewall 20 and is received within internally threaded bore 108 at the end of the stub shaft 104 to fixedly secure the shaft 104 to the sidewall 20. The shaft 104 includes cylindrical retainer steps 110 concentric with bore 106. The steps 110 have progressively smaller diameters as the support roll 46 is approached so that the innermost step has a diameter no greater than the inner race 86. It will be appreciated that the steps 110 prevent lateral outward shifting of the bearing assembly 84, while providing exposure ofthe assembly 84 to ambient conditions to allow cooling thereof. The shaft 104 further includes a frusto-spherical support portion 112 press-fit within the inner race 86 for supporting and preventing rotational movement of the latter. The curvilinear periphery of frusto-spherical portion 112 provides self-alignment of the bearing assembly 84 relative to the shaft 104 and hub 100. Of course, the periphery of the frusto-spherical portion 112 also tolerates some manufacturing inaccuracy (e.g., misalignment ofthe support roll 46 and hub 100, or shaft 104 and sidewall 20).

DOUBLE BEARING MOUNTED SUPPORT ROLL 46

As best illustrated in FIG. 2, a first pair and a second pair of bearing assemblies, broadly denoted by the numerals 114 and 116, are provided at opposite ends of the support roll 46 to rotatably couple the roll 46 to the sidewalls 18 and 20, respectively. Turning specifically to FIG. 3, the second pair of bearing assemblies 116 includes a inboard bearing assembly 118 in juxtaposition with an outboard bearing assembly 120. The bearing assemblies 118,120 are constructed in an identical manner to bearing assembly 84 illustrated in FIG. 6 and therefore will not be described in detail hereinbelow. Suffice it to say that the bearing assemblies 118 and 120 include inner races 122 and 124, concentric outer races 126 and 128, and pairs of elastomeric, resilient rings 130,132 and 134,136 fixedly secured to the outer races 126 and 128 to span the annular opening between the inner and outer races, respectively. Similarly, the other pair of bearing assemblies 114 includes an outboard bearing assembly 138 in juxtaposition with an inboard bearing assembly 140. It will be appreciated that the pair of bearing assemblies 114 is identical in construction with the second pair of bearing assemblies 116, and accordingly, is not illustrated in detail nor discussed hereinbelow.

A first hub 142 and second hub 144 are fastened by mechanical fasteners, such as set screws (not shown), within the tubular support roll 46 at opposite ends thereof. Using the hub 144 as an example, hub 144 presents a solid configuration, except for a central opening 145 which snugly circumscribes the outer races 126,128 of the bearing assemblies 118,120 such that the support roll 46, hub 144 and outer races 126, 128 rotate with one another. The hub 144 presents an inner step 146 which prevents lateral inward movement ofthe assemblies 118,120. Of course, the first hub 142 is similarly inteφosed between the bearing assemblies 138,140 and the support roll 46.

A stationary through-shaft 148 extends laterally between the sidewalls 18,20 to support the inner races 122,124. The through-shaft 148 is mounted to first and second fore-and-aft support arms 150 and 152, respectively. The arms 150 and 152 are attached to the rear portion ofthe sidewalls 18 and 20, respectively, to project forwardly from the tailgate 26 and dispose the support roll 46 along the lower boundary of the chamber 64 as illustrated in FIG. 1. As best shown in FIG. 3, a set screw 154 extends through chamfered opening 156 in support arm 152, and is received within an internally threaded bore 158 at the end ofthe through-shaft 148 to fixedly secure the shaft 148 to the sidewall 20. Of course, the other end of the through-shaft 148 (adjacent sidewall 18) is similarly secured to the support arm 150. However, as illustrated in FIGS. 3-5, the through-shaft includes a marginally flattened end 160 adjacent sidewall 20 which is complementally received within a D-shaped opening 162 of ring 164. The ring 164 is preferably welded to support arm 152 to further prevent rotational movement of the through-shaft 148 during baling operations. It will be appreciated that this configuration also facilitates assembly ofthe invention by preventing rotational movement ofthe shaft

148 while the set screws 154 are tightened within bores 158.

The bearing assemblies 118, 120, 138, 142 are press-fit onto the through- shaft 148 such that rotational movement of the inner races is prevented. Preferably, retaining collars 166 and 168 are provided adjacent the outboard bearing assemblies 142 and 120, respectively, to prevent lateral outward movement ofthe assemblies toward the end ofthe shaft 148. As well known in the art, the retaining collars include a small lip 170 (see FIG. 3) which fits about a portion ofthe outboard bearing assembly 120. A radially extending set screw 172 is threaded into the collar 168 to secure the same to the shaft 148. As apparent by comparing FIG. 3 with FIG. 6, the annular spaced defined between the retaining collar 168 and hub 144 (FIG. 3) is significantly larger than the space defined between the conventional retainer steps 110 and hub 100 (FIG. 6). It will be appreciated that the relatively larger space provided by the preferred embodiment of the present invention prevents trash from being trapped adjacent the outboard bearing assembly 120. Further, the through-shaft 148 ensures alignment of the bearing assemblies 118,120,138,140 relative to one another and to the support roll 46, and maintains such alignment ofthe assemblies.

In use, the double bearing assemblies 114 and 116 capably perform their journaling functions for the support roll 46, while at the same time reducing the risk of overheating at such journal points due to bearing contamination and failure. Using the assembly 116 as an example, it will be seen that the outer bearing 120 effectively seals and protects the inner bearing 118 from contact with dirt, grime and residue in the area. Because the outer race 128 of bearing 120 is pressed into the hub 144, the inner race 124 is fixed to the shaft 148, and the dual elastomeric seals 134,138 are present between the races 124, 128, it is very difficult for moisture and deleterious materials to gain access to the inner bearing 118. Consequently, even though the outer bearing 120 may begin to experience the negative effects of continuous exposure to environmental conditions over time, the inner bearing 118 tends to remain unaffected and in good operating condition. Consequently, the end ofthe support roll 148 remains journaled by at least one fully functional bearing if the other one starts to fail. Ideally, during routine inspections by the operator, the failing condition ofthe outer bearing 120 will be noticed and the operator will replace the distressed bearing before conditions become more serious. However, even if he fails to notice the deteriorating condition of the outer bearing 120 and take appropriate action, the inner bearing 118 is still available to carry out the joumaling function at that end of the roll, assuming circumstances have not become so adverse that the outer bearing 120 is unable to shield the inner bearing 118 from the very conditions that have caused the outer bearing to fail. Thus, the double bearing arrangement serves to extend the time available for the operator to notice the deteriorating outer bearing and replace it before the journal at that end ofthe support roll becomes so contaminated and disfunctional that it overheats sufficiently to cause a fire. Furthermore, the fact that the load on the end ofthe support roll is shared by two bearings instead of concentrated in only one has the effect of prolonging bearing life and reducing the rate of heat build-up in a contaminated bearing. The foregoing description of a preferred form of the invention is to be used for puφoses of illustration only, and should not be utilized in a limiting sense in inteφreting the scope ofthe present invention. Obvious modifications to the exemplary embodiments, as hereinabove set forth, could be readily made by those skilled in the art without departing from the spirit ofthe present invention. For example, the principles ofthe present invention are equally applicable to a roll positioned in a similar location ofa fixed chamber baler and exposed to similar operating conditions.

The inventors hereby state their intent to rely on the Doctrine of Equivalents to determine and assess the reasonably fair scope of their invention as pertains to any apparatus not materially departing from but outside the literal scope of the invention as set out in the following claims.

Claims

What is claimed is:

1. In a round baler, the improvement comprising: first and second laterally spaced, upright sidewalls; bale forming mechanism located between the sidewalls and cooperating therewith to form a baling chamber, said bale forming mechanism including a laterally extending support roll in a lower portion ofthe chamber positioned to carry weight of the bale as it is formed, said support roll presenting a pair of opposite, first and second ends; a first pair of bearing assemblies rotatably supporting the first end on the first sidewall; and a second pair of bearing assemblies rotatably supporting the second end on the second sidewall.

2. In a round baler as claimed in claim 1, said bale forming mechanism further including a series of laterally extending rolls and laterally spaced belts entraining said rolls, said belts also entraining said support roll.

3. In a round baler as claimed in claim 1, said support roll being tubular; and a laterally extending, stationary through-shaft concentrically disposed within the support roll, said through-shaft being fixed to the sidewalls, said first and second pairs of bearing assemblies being inteφosed between the support roll and the through-shaft rotatably supporting the support roll thereon.

4. In a round baler as claimed in claim 3, said through-shaft having a marginally flattened end adjacent said second sidewall. said second sidewall having an opening associated therewith configured for complementally receiving said marginally flattened end whereby to prevent the through-shaft from rotating relative to the sidewalls.

5. In a round baler as claimed in claim 3, said bearing assemblies including an annular inner race, a concentrically spaced, annular outer race, and a ball-bearing ring therebetween providing relative rotational movement between the inner and outer races.

6. In a round baler as claimed in claim 5, said support roll having first and second cylindrical hubs fixedly received therein for rotational movement therewith, said hubs each presenting a central opening fixedly receiving the outer races of an associated pair of assemblies such that said hubs rotate with said outer races, said inner races being secured to the through-shaft such that the inner races are stationary.

7. In a round baler as claimed in claim 6, said first and second pairs of bearing assemblies each including an inboard bearing assembly in juxtaposition with an outboard bearing assembly, said central openings of the hubs presenting interior walls which sealingly engage the outer races ofthe assemblies, said inner races sealingly engaging the through-shaft, said hubs having a solid configuration such that said hubs and said outboard assemblies seal the inboard assemblies from environmental contamination.

8. In a round baler as claimed in claim 1 , said sidewalls presenting forward portions and separate rearward portions swingably attached to the forward portions, said rearward portions cooperatively defining a tailgate which swings between a discharge position and a closed position, said support roll being rotatably supported on the tailgate for swinging movement therewith.

9. In a round baler as claimed in claim 1 ; and pickup mechanism for transferring crop material from a windrow to the baling chamber, said chamber having a crop infeed opening configured to receive crop material delivered thereto by the pickup mechanism, said support roll being positioned adjacent the infeed opening such that crop material moving therethrough passes the support roll.

10. In a round baler as claimed in claim 1 , said first and second pair of bearing assemblies each including an inboard bearing assembly in juxtaposition with an outboard bearing assembly.

11. In a round baler as claimed in claim 10, said support roll being tubular, said inboard and outboard bearing assemblies being sealingly received within the support roll such that the outboard assemblies seal the inboard assemblies from environmental contamination.

12. In a round baler, the improvement comprising: a mobile frame supporting first and second laterally spaced, upright sidewalls, said sidewalls presenting forward portions and separate rearward portions swingably attached to the forward portions, said rearward portions cooperatively defining a tailgate which swings between a discharge position and a closed position; a series of transverse rolls extending between said sidewalls and a plurality of laterally spaced belts entraining said rolls, said rolls and belts cooperating with the sidewalls to form a baling chamber, said baling chamber having a crop infeed opening configured to receive crop material delivered thereto by a pickup mechanism, said series of rolls including a support roll in a lower portion of the chamber positioned to support weight ofthe bale as it is formed, said support roll further being positioned adjacent the crop indeed opening such that crop material coming into the chamber through said opening passes in close proximity to the support roll, said support roll presenting a pair of opposite, first and second ends; structure projecting generally laterally inwardly from the rearward portions of the sidewalls for mounting the support roller thereon; and means for rotatably coupling the support roll to the structure, said coupling means including a first pair of bearing assemblies rotatably supporting the first end ofthe support roll on the first sidewall, and a second pair of bearing assemblies rotatably supporting the second end ofthe support roll on the second sidewall.

13. In a round baler as claimed in claim 12, said support roll being tubular, said structure for mounting the support roll to the tailgate including a transversely extending stationary through-shaft concentrically disposed within the support roll, said through-shaft being fixed to the rearward portions ofthe sidewalls to mount the support roll on the tailgate, said bearing assemblies being inteφosed between the support roll and the through-shaft to rotatably support the support roll on the through-shaft.

14. In a round baler as claimed in claim 13, said through-shaft having a marginally flattened end adjacent said second sidewall, said second sidewall having an opening associated therewith configured for complementally receiving said marginally flattened end whereby to prevent the through-shaft from rotating relative to the sidewalls.

15. In a round baler as claimed in claim 13, each of said bearing assemblies including an annular inner race, a concentrically spaced, annular outer race, and a ball-bearing ring therebetween providing relative rotational movement between the inner and outer races.

16. In a round baler as claimed in claim 15, said support roll having first and second cylindrical hubs fixedly received therein for rotational movement therewith, said hubs each presenting a central opemng fixedly receiving the outer races of an associated pair of assemblies such that said hubs rotate with said outer races, said inner races being secured to the through-shaft such that the inner races are stationary.

17. In a round baler as claimed in claim 16, said first and second pairs of bearing assemblies each including an inboard assembly in juxtaposition with an outboard bearing assembly, said central openings of the hubs presenting interior walls which sealingly engage the outer races ofthe assemblies, said inner races sealingly engaging the through-shaft, said hubs having a solid configuration such that said hubs and said outboard assemblies seal the inboard assemblies from environmental contamination.

18. In a round baler as claimed in claim 12, said first and second pair of bearing assemblies each including an inboard bearing assembly in juxtaposition with an outboard bearing assembly.

19. In a round baler as claimed in claim 18, said support roll being tubular, said inboard and outboard bearing assemblies being sealingly received within the support roll such that the outboard assemblies seal the inboard assemblies from environmental contamination.