Abstract:
Broadly, one aspect of the present invention is an articulated combine having increased on-board grain storage capacity (e.g., 1,200 bushels) and which is composed of a forward unit having an operator&#39;s cab, an engine, a grain harvesting assembly, a grain transfer assembly, and being devoid of an on-board grain bin; and a rearward unit jointedly attached to the forward section and having, steerable and powered wheels, an on-board grain bin for receiving grain from the forward section grain transfer assembly, and a grain off-loading assembly. The grain transfer assembly, joint, and grain off-loading assembly and controls, form other aspects of the present invention.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is a divisional application of U.S. Ser. No. 09/481,046, filed Jan. 11, 2000, now U.S. Pat. No. 5,125,618, which is a divisional application of U.S. Ser. No. 09/040,985, filed Mar. 18, 1998, now U.S. Pat. No. 6,012,272, the disclosure of which is expressly incorporated herein by reference. 
    
    
     CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is cross-referenced to application Ser. No. 08/927,872 filed Sep. 11, 1997, the disclosure of which is expressly incorporated herein by reference. 
     STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH 
     Not applicable. 
     BACKGROUND OF THE INVENTION 
     The present invention generally relates to combines and more particularly to an articulated (jointed) combine which employs, inter alia, an improved joint, unloading capability and control, steering, and extremely large grain storage capacity. 
     A modem agricultural combine typically unloads or transfers clean grain from its on-board storage hopper utilizing an auger of fixed length which swings out in a fixed radius and fixed elevation arc from its stowed position. The stowed position generally is pointing to the rear of the combine. The auger in turn generally is driven by a mechanical arrangement of belts, chains, clutch, and gearbox. The unload auger in most combine: designs swings out to the operator&#39;s left. The auger length generally is limited by the practical distance that it can extend beyond the rear of the combine in its stowed position without creating a serious maneuvering hazard. 
     As the size of on-board storage hoppers and capacity of combines has increased, the time required to maneuver the machine next to the grain receiving wagon or truck and the grain transfer time have become a major component of the total harvesting time. Conventional combines have a grain hopper capacity of 250 to 300 bushels and unload auger capacities of 1.9 to 2.6 bushels per second. 
     The unload time of the hopper typically is about 2 to 3 minutes with the unload auger running at maximum speed and 1 to 2 minutes are taken to maneuver the combine into the optimum unload position next to the truck or wagon. Re-positioning the combine and running the auger at less than maximum speed are often encountered when topping off the truck or wagon which is receiving the grain. As modern combine harvesting capacities approach 3,000 bushes per hour, the unload cycle must be repeated every 8 to 10 minutes. Therefore, the total unload time or non-harvesting time is a significant reduction of total grain harvesting productivity. 
     This productivity loss can be countered by a second operator utilizing a tractor and grain cart following the combine back and forth through the field to unload the on-board combine storage hopper without stopping the harvesting process. Alternatively, a combine with an integrated grain cart, as disclosed in application Ser. No. 08/927872, cited above, can be utilized to reduce the number of unload cycles and at least double the rate at which grain is discharged to the receiving vehicle. 
     Unloading combines into semi-trailer road trucks has become the prevalent practice as opposed to field wagons which were utilized in the past. These road trucks typically are parked at the side of the road and not in the field where the combine is operating. This necessary practice almost always creates an elevational difference between the two vehicles. These road trucks themselves also have widely varying heights. These two conditions create a big variation in the optimum elevation of the discharge point of the combine unloading system. Combine manufacturers have attempted to address this problem with ever longer augers and higher fixed swing out arcs. There are, however, limits to both. This fixed point discharge point frequently ends up too high, too low, too far from the combine, or too close to the combine for optimum truck loading conditions. Such conditions require repositioning the while combine with respect to the vehicle it is loading. 
     Existing combine unloading systems can unload from one side of the machine only. This frequently requires 180° turns by the combine to position it on the proper side to unload the grain into the road truck. It also means that the combine can be unloaded into a moving grain cart when traveling only in one direction through the field since access to one side of the combine is virtually always blocked by unharvested crop. 
     When topping off or completely filling the truck or wagon, it is necessary for the operator to inch the combine forward or backward during the process. In addition to being cumbersome, the combine must be positioned close to perfectly parallel to the receiving vehicle or a stop and reposition is necessary. The lack of parallelism frequently cannot be solved by moving the auger through its fixed arc. 
     An agricultural combine has multiple steering requirements. Precise control is needed as the row harvesting units such as a cornhead, are guided through the rows of grain. When the end of the field is reached, a tight turning radius is needed to proceed back across the field in order to harvest the crop immediately adjacent to the just-completed rows or round. Concomitant with its field performance, this large vehicle also must be controlled on the roadway at speeds of around 20 mph and around tight corners. Another steering associated problem is to turn multiple axle, heavily-loaded bogies with large tires in a tight radius while minimizing sliding the tires in the horizontal direction which places high stresses in the suspension, piles up dirt in the field, and causes excessive tire wear. 
     An early attempt at an articulated combine is reported in U.S. Pat. No. 4,317,326. The design capacity is stated to be around 360 bushels. Its unloading mechanism is limited to one side of the combine and steering is accomplished only by articulation steering cylinders. To date, no articulated combine is commercial. Clearly, there is a need for a more flexible, faster, and convenient combine which overcomes these and other problems such as those set forth above. 
     BRIEF SUMMARY OF THE INVENTION 
     The present invention is addressed to solving the problems detailed above by providing an articulated (jointed) combine which employs, inter alia, an improved joint, unloading capability and control, transfer of grain from a forward unit to a grain bin on a rearward unit, and extremely large grain storage capacity. Broadly, then, one aspect of the present invention is a combine, preferably articulated, having increased on-board grain storage capacity and which is composed of a forward unit having an operator&#39;s cab, an engine, a grain harvesting assembly, a grain transfer assembly, and being devoid of an on-board grain bin; and a rearward unit jointedly attached to the forward section and having, steerable and powered wheels, an on-board grain bin for receiving grain from the forward section grain transfer assembly, and a grain off-loading assembly. 
     Another aspect of the present invention is directed to a joint for a powered articulated vehicle, such as a combine for joining a forward unit to a rearward unit. The joint includes an upper frame member carried by the forward unit and having a recess on its lower side and a lower frame member carried by the forward unit, having a recess on its upper side, and being spaced-apart vertically below the upper frame member so that the recesses are in vertical registration. The joint further includes a shaft carried by the rearward unit and a bearing retainer assembly carried by the end of the shaft and disposed between the recesses. The bearing assembly includes an outer annulus surmounting an inner hub which hub is connected to the shaft with thrust bearings inserted between the annulus and said hub, whereby the inner hub co-rotates with shaft with respect to the outer annulus. The bearing assembly also includes a pair of nibs carried by the outer annulus which nibs reside in the upper and lower recesses and which nibs are associated with tapered roller bearings so that the outer annulus co-twists with the shaft respect to the forward unit. Uniquely, the joint is stiff in the longitudinal axis formed along the forward unit frame members and the rear unit shaft. 
     A further aspect of the present invention is an improved articulated combine of a forward unit and rearward unit which connected by a joint wherein the improvement is directed to transferring clean grain from the forward unit to the rearward unit. Such improved combine is composed of a rearward unit which has a forward and the forward unit has a back, both of which conform in shape to each other and both of which are curved to match the radius of articulation of the combine. The rearward unit forward has a horizontal slot in it. The grain transfer assembly has an elongate discharge end which fits into the rearward unit forward horizontal slot for providing grain transfer capability to the on-board rearward unit grain bin while the forward and rearward units are being turned about the joint interconnecting the forward and rearward units. 
     Yet another aspect of the present invention is an unload assembly for unloading clean grain from a combine grain bin and which is composed of a telescoping grain movement assembly composed of a proximal grain mover and a distal grain mover. The proximal grain mover is pivotally attached to the grain bin for movement to either side of the grain bin and for movement vertically. The distal grain mover is in telescoping attachment with the proximal grain mover and from which clean grain is discharged from the unload assembly. 
     Advantages of the present invention include a combine design, preferably an articulated combine, which enables grain storage capacity of between 500 and 1,000 bushels or more. Another advantage is an articulated combine which can unload clean grain to either side and which is controlled by a unique control system. A further advantage is a unique steering system for an articulated combine. These and other advantages will be readily apparent to those skilled in this art. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     For a fuller understanding of the nature and objects of the present invention, reference should be had to the following detailed description taken in connection with the accompanying drawings in which: 
     FIG. 1 is a side elevational view of the novel combine (or harvester) with extra large storage capacity, novel joint, clean grain transfer ability, and unloading capacity; 
     FIG. 2 is an overhead view of the grain trailer depicted in FIG. 1; 
     FIG. 3 is a sectional view taken along line  3 — 3  of FIG. 1; 
     FIG. 4 is a sectional view taken along line  4 — 4  of FIG. 3; 
     FIG. 5 is a single axle rear unit version of the combine depicted in FIG. 1; 
     FIG. 6 is a track driven rear unit version of the combine depicted in FIG. 1; 
     FIG. 7 is a side-elevational cut-away view of the novel clean grain transfer assembly depicted in FIG. 1; 
     FIG. 8 is a partial side elevational view of a joystick used to control the clean grain transfer assembly depicted in FIG. 7; 
     FIG. 9 is a top view of the joystick shown in FIG. 8; 
     FIG. 10 is a schematic of the hydraulic vertical control for the clean grain transfer assembly of FIG. 7; 
     FIG. 11 is a schematic of the hydraulic swing control for the clean grain transfer assembly of FIG. 7; 
     FIG. 12 is a schematic of the hydraulic telescoping control for the clean grain transfer assembly of FIG. 7; 
     FIG. 13 is a schematic of the hydraulic speed control for the clean grain transfer assembly of FIG. 7; 
     FIG. 14 is a schematic of the hydraulic steering system for the novel articulated combine; 
     FIG. 15 is an overhead view of a the novel combine with an alternative conveyor assembly for feeding grain from the grain bin to the novel clean grain transfer assembly; 
     FIG. 16 is a side-elevational cut-away view of the alternative clean grain transfer assembly depicted in FIG. 15; and 
     FIG. 17 is a view along line  17 — 17  of FIG.  16 . 
    
    
     The drawings will be described in detail below. 
     DETAILED DESCRIPTION OF THE INVENTION 
     The present invention addresses problems associated with modern farming combines by providing a harvester which can unload readily on either side and to virtually any height road truck. The harvester also increases the harvested grain carrying capacity from about 200-300 bushels in conventional combines to about 500-1,200 bushels utilizing the rearward-only grain bin because the rearward unit has more space than there is over the front axle. This is important because the capacity of a typical road semi-trailer is 1,000 bushels. This means that the novel combine can fill an entire road truck from its on-board grain bin in a single unloading. Moreover, the unique unloading system permits unloading of clean grain from the rearward grain cart on either side of the combine. Such increased grain storage capacity is possible because locating the grain bin on the rearward unit permits a much lower center of gravity to be designed into the rearward unit. 
     In order to ensure that the extra weight can be easily maneuvered by the novel harvester, the rearward unit has powered and steerable wheels. The typical grain bin located on the forward unit now has been eliminated by dint of the rearward unit on-board storage bin. The forward unit now only needs to have an operator&#39;s cab, an engine, a harvesting assembly (including grain cleaning), and a clean grain transfer assembly for transferring clean grain from the forward unit to the rearward cart grain bin. Finally, the forward and rearward units are interconnected by a unique two-axis joint. Chaff from the harvesting assembly is discharged downwardly and to the side of the two-axis joint which needs to be rounded in design so that the chaff does not build up on any horizontal surfaces. 
     Steering problems associated with heavily-loaded, large tired bogies is inventionally solved by a compound or combination steering system which utilizes steerable wheels on the rearward bogey or unit and conventional steering cylinders at the articulated joint. Compound steering systems have been used in agricultural tractors to provide for both tight turning radiuses and precise row steering. An example of such a system is disclosed in U.S. Pat. No. 4,802,545 which proposes a 4-wheel drive tractor equipped with both an articulation joint and a pivotable front axle in a wagon-wheel configuration. The pivoting front axle is used for precise row steering and articulation is added for tight radius turns. 
     The present invention utilizes powered and steerable rearward units to support the harvested grain, as first disclosed in application Ser. No. 08/927,872 (cited above). The steerable and powered rear axles also minimize the horizontal sliding problem by providing a coordinated turning radius of multiple axle configurations. The steerable rear wheels are used for relatively small steering corrections and for precise row following while harvesting The rotation of the rear wheel steering wheels of approximately 15° to 20°, then, is augmented by conventional steering cylinders at the articulation joint to accomplish tight radius turns. Limiting the rear wheel turning in degrees also minimizes their intrusion into space needed to maximize grain carrying capacity. 
     Although more elaborate control systems may be utilized, the compound steering disclosed herein may be safely implemented using two rather conventional steering valves or a multiple port valve actuated by the operator steering wheel located in the combine cab. When the operator moves the steering wheel a small increment, the first valve or port directs hydraulic fluid to the steering cylinder at the rear axles. If the operator continues turning the steering wheel in the same direction, hydraulic fluid or oil will be directed further to the rear axle steering cylinders until they reach a maximum travel and articulation begins by the valve now directing oil to the articulation cylinders. When the operator calls for the vehicle to return to a straight ahead direction, the articulation cylinders return to their balanced, equal extension, home position. The rear wheel steering cylinders then receive oil flow from the steering valves in the reverse direction to move the rear wheels to their straight ahead home position. At all relevant times, both the rearward unit wheel steering cylinders and the articulation cylinders are held in position by check valves until the steering valve directs oil flow to them which causes the check valves to open. The check valves prevent external forces from causing the combine to drift when the operator is not calling for a change in direction. Alternatively, the operator can override these controls and manually articulate the novel combine. 
     Referring initially to FIGS. 1 and 2, innovative combine  10  generally includes forward unit  12  and rearward unit  14 . Forward unit  10  is seen to include cab  15  in which the operator is seated, cornhead or small grainhead  16 , engine compartment  18  (fan discharge shown in the drawings), and powered non-steerable wheel pair  20 . Rearward unit  14  is interconnected to forward unit  12  via joint assembly  22  and clean grain is transferred from forward unit  12  to rearward unit  14  via grain cleaning and transfer assembly  24  seen in the cut-away view. Rearward unit  14  is seen to include clean grain unloading system  26  in its stored position and in phantom in a raised position, grain bin  28 , and powered and steerable wheel pairs  30  and  32 . Use of a dual axle configuration of powered and steerable wheels supporting grain bin  28  on rearward unit  14  contributes to the capability of grain bin  28  holding upwards to 1,000 bushels of grain or more. Providing the grain bin capacity only on rearward unit  14  translates into a lower center of gravity for grain bin  28  which also enables such higher storage capacity and provides more even weight distribution per axle. 
     As seen in FIG. 2, clean grain from forward unit  12  is transferred to grain bin  28  via grain transfer assembly  24  which includes a generally horizontal transfer device (e.g., auger, bucket conveyor, cleated conveyor, or the like) which extends into a slot in the side of grain bin  28  which confronts forward unit  12 . Note should be made of the arcuate configuration of the rear of forward unit  12  and the front of rearward unit  14  and that these arcuate; configurations conform to each other. Moreover, the arc of such configuration is based or, the articulation radius of curvature. Such conforming arcuate design permits forward unit  12  to be turned either to the right or to the left, as shown in phantom in FIG.  2 . 
     Slot  34  in the front wall of grain storage bin  28  permits horizontal transfer device  36  to continue to dump grain into bin  28  as forward unit  12  is turned from side to side, also as shown in phantom in FIG.  2 . Slot  34  is associated with a “slide” which commences at the top of bin  28  and slants downwardly to meet with hopper fill auger  38  (often called a “bubbler” auger). Such slant ensures that all grain transferred into bin  28  will be directed to the bottom of bubbler auger  38  for distribution of clean grain within bin  28 . Transfer device  36 , suitably a conveyor could be fixed to forward unit  12  with slot  34  taking up its movement as combine  10  is steered left or right. In this regard, the origination point of transfer device  36  does not need to be located at the centerline of forward unit  12 , but can be located to the side of the joint and still feed grain to grain bin  28 . Additional flexibility, then, is afforded the combine designer because of the ability to locate the feed end of transfer device  36  to one side of the other of the centerline of forward unit  12 . 
     Alternatively, conveyor  36  could be pivotally mounted to forward unit  12  and slot  34  would not need to be substantially the entire width of grain bin  28  as steering of combine  10  would be taken up by such pivot mounting. In such embodiment, slot  34  need only be an opening through which grain is transferred into bin  28  via transfer device  36 . Also, conveyor  36  would need to be located over the joint axis (centerline of forward unit  12 ) when pivotally mounted to forward unit  12 . Conveyor  36  even could be biased to return to a central station once a turn was completed. 
     Once the clean grain has been transferred into bin  28 , it is distributed within grain bin  28  by hopper fill auger  38 , which extends from a front corner of bin  28  to around the upper mid-section of bin  28 . Grain is unloaded from bin  28  commencing with unload or drag augers  40  and  42  which are located along the bottom of bin  28  and which vertical auger  44  powered by motor  45  (seen in phantom in FIG.  2  and in cross-section in FIG. 7) which suitable also could be a bucket conveyor or other suitable device for transporting grain vertically to clean grain unloading system  26 . 
     Referring to FIG. 7, a cross-sectional view of the grain unloading system of the present invention is shown in detail. Clean grain housed in bin  28  is dragged to vertical auger  28  by augers  40  and  42 . Auger  44  could, of course, be replaced by a bucket elevator or other convenient mechanism for vertically transporting clean grain from within bin  28  up the level of unloading system  26 . Motor  88 , which conveniently is a hydraulic motor, motivates unloading system  26  to rotate about the longitudinal axis of auger assembly  44  in either direction in order to unload the grain into a grain cart, road truck, or other storage location. Unique is the ability to move unloading system  26  to either side of combine  10 . 
     Shroud  90  confines the grain for dumping onto conveyor system  92  which itself is shrouded because the conveyor of conveyor system  92  rotates in the clockwise direction. Again, conveyor system  92  conveniently could be replaced with an auger, a chain with, paddles, or other grain moving device. As shown, conveyor system  92  employs upstanding cleats in order to urge the grain along the desired path. 
     The vertical elevation of unloading system  26  is determined by actuator  94  which can be a rod and piston assembly as shown connecting vertical auger assembly  44  to conveyor system  92 . Power again conveniently is supplied by a hydraulic motor; although, other power means may be employed as is necessary, desirable, or convenient in conventional fashion. 
     In order to be able to unload grain a given distance from combine  10 , telescoping conveyor assembly  96 , which preferably rotates in the counter-clockwise direction, telescopes from conveyor assembly  92 . While a rack and pinion assembly powered by a motor (not shown) is evident in the drawings, a rod and cylinder assembly or other mechanism could provide telescoping movement of conveyor assembly  96 . For that matter power, to move the conveyors in conveyor assemblies  92  and  96 , hydraulic motors (not shown) preferably are provided. Preferably, conveyor system  96  rotates in the opposite direction of conveyor system  92 ; although, such opposite direction movement of conveyors  92  and  96  is not necessary for the unique unloading system of the present invention. Ultimately, clean grain exits conveyor assembly  96  via spout  98 . With the ability to rotate unloading system  26  to either side of combine  10 , to control the vertical elevation of unloading system  26 , inching control, and to extend the length of unloading system  26 , the novel grain unloading system has the ability and capability to unload grain in trucks parked at a different elevation than is combine  10 , parked a variety of distances from combine  10 , and parked on either side of combine  10 . Depending upon the type of grain conveyance utilized, conveyor assembly  96  could be open or closed at its top. 
     With respect to operation of clean grain unloading system  26 , reference is made to FIGS. 8 and 9 which show a unique joystick control system which controls such unloading system. Initially, joystick  100  is fitted with finger toggle switches  102 ,  104 ,  106 , and button  108 . Toggle switch  102  is activated by the operator&#39;s fingers and causes unloading system  26  to move vertically up and down. Switch  104  conveniently is thumb activated and is an on-off switch for unloading system  26 . Switch  106  is a combine inching switch, that is, it causes combine  10  to move slowly forward or backward to place spout  98  exactly where the operator desires. Such slow movement is known as “inching” in this field. Button  108  is a “home” button which means that unloading system  26  is returned to its stored position as shown in FIG. 1, for example. 
     Another capability of joystick  100  is that it can move forward, backward, and laterally left and right. These movements cause unloading system  26  to extend (say, forward movement of joystick  100 ), retract (backward movement), swing to the left (left movement), and swing to the right (right movement). Finally, joystick  100  is rotatable to control the speed of the conveyors making up unloading system  26 . 
     Joystick  100  accomplishes the described movements of unloading system  26  by signaling electrohydraulic valves with a signal sent to manually adjustable flow control valves for, say, movement of unloading system  26  up/down, left/right, in/out, and home. Joystick  100  signals a proportional servo valve for on/off and conveyor speed (e.g., activates a linear electric servo that moves a pump swash plate). Joystick  100  signals the propulsion system of combine  10  in order to inch the combine forward or reverse by by-passing the normal operator speed control of the vehicle. It should be obvious that the novel combine takes advantage of the hydraulic system already in place in conventional combines and extends their use in order to desirably power the unloading system  26  and wheel pairs  30  and  32 . Other power means, of course, could be employed; however, hydraulic power tends to be more reliable. 
     Implementation of such joystick movements of unloading system  26  is displayed in FIGS. 10-13. Referring initially to FIG. 10, lines  110  and  112  are connected to a source of voltage (say, 12 volts supplied by the combine). Contacts  114  and  116  are joystick  100  contacts for raising and lowering, respectively, unloading system  26 . Ground  117  is provided in conventional fashion. Upon closure of one of joystick contacts  114  or  116 , bi-directional valve with adjustable flow  118  is fed hydraulic fluid at, say, 2,000 psi from a hydraulic pump which feeds rod and cylinder assembly  94  via lines  120  and  122  with oil returned to reservoir  124  via line  126 . Assembly  94 , then, raises and lowers unloading system  26  (conveyor systems  92  and  96 ). 
     Referring to FIG. 11, lines  128  and  130  run to joystick contacts  132  and  134  which actuate bi-directional valve with adjustable flow and float  136  which actuates motor  88  for swinging unloading system  26  either left or right. Ground  138  and return line  140  to reservoir  124  are provided in conventional fashion. A rod and cylinder or other means could be substituted for motor  88 . 
     Referring to FIG. 12, lines  140  and  142  run to joystick contacts  144  and  146  which actuate bi-directional two flow valve (slow/fast speed)  148  which actuates motor  150  for extending unloading system  26  in and out (telescopingly extending unloading system  26 ). Ground  150  and return line  154  to reservoir  124  are conventionally provided. A rod and cylinder or other means could be substituted for motor  150 . 
     Referring to FIG. 13, the unload system speed control is shown. Specifically, line  156  has on/off switch  108  which activates linear servo unit  158 . Line  160  at, say, 2 volts, runs to joystick  100  potentiometer (actuated by rotation of joystick  100 ) which in turn runs to linear servo unit  158 . Linear servo unit  158  controls variable displacement pump  164  which runs from, say, 0-2,000 psi. In turn, pump  164  pumps oil through flow divider  166  which divides the hydraulic flow to motor  168  via line  167  which runs drag augers  40  and  42  and upstanding auger  44  (the speed of drag augers  40  and  42  needs to be controlled and matched with the speed of auger  44  since these drag augers feed grain to auger  44 ) with the oil then returning via line  170  to reservoir  124 . At this point in the description it should be noted that reservoir  124  is notated on the drawings as the reservoir for all hydraulic fluid circuits. Obviously, additional reservoirs could be used as is necessary, desirable, or convenient. 
     Next, hydraulic fluid or oil from flow divider  166  flows via line  172  into second flow divider  174  which splits the hydraulic fluid flow between motor  176  via line  178  which motor runs conveyor assembly  92  and motor  180  via line  182  which motor runs outer conveyor assembly  96 . Flow divider  174  permits more flow to pass into line  182  than into line  178 , say, 55%/45%, in order for outer conveyor assembly  96  to run at a faster rate, say, 10% faster, than conveyor assembly  92  in order to prevent plugging of conveyor assembly  96 . Oil from motor  176  returns via line  184  to reservoir  124  while oil from motor  180  returns to reservoir  124  via line  186 . 
     An alternative clean grain unloading system is presented in FIGS. 15-17. Specifically, auger  44  has been replaced with bucket conveyor assembly  286  which is powered by hydraulic motor  288  which is located at the top sprocket of assembly  286 . Rotation of assembly  286  and raising/lowering of conveyor assembly  26  is accomplished by cylinder assemblies  292  and  294 . Channel ring  287  which is held in position by bars  296 ,  297 , and  298 . Riding within channel ring  287  are four wheel assemblies  289   a-d  which are connected to bucket conveyor assembly  286 . Thus, as the rod of cylinder assembly  292  extends/retracts, conveyor assembly  286  rotates within channel ring  287 . 
     Cylinder  294  is attached at one end to the channel ring  287  via a wheel and at its other end to conveyor assembly  286 . As conveyor assembly  286  rotates (by cylinder assembly  292 ), conveyor assembly  294  also rotates by dint of its wheeled attachment to channel ring  287 . Cylinder  294  causes conveyor assembly  286  to tilt as its rod extends/retracts and such tilting can be accomplished regardless of the rotational position of assembly  286 . Because of the moment created when conveyor assembly  286  tilts, it is disposed within circular channel  290  about its lower end. Wheel assemblies  300  and  302  are attached at one end to conveyor assembly  286  with their wheeled opposite ends disposed in the inner channel formed within ring  290 . As cylinder  294  causes conveyor assembly  286  to rotate, the wheels of assemblies  300 / 302  become pivot points for the lower end of assembly  286  to also rotate. 
     Next, it will observed that inner conveyor assembly has been replaced (compared to the conveyor assembly in FIG. 7) with an auger housed within a shell for conveying grain from bucket conveyor  286  to telescoping cleated conveyor  96 . Motor  306  effects rotation of auger  304 . Finally, it also is possible to string guy wires from combine  10 , say at conveyor assembly  286  (or  44  in FIG. 7) to support conveyor assembly  96 ,  92 , and/or  304 , as is necessary, desirable, or convenient. For that matter, other means of supporting the weight of telescoping assembly  26  may be designed and implemented depending upon needs. For example, conveyor assembly  96  may be made of aluminum in order to reduce its weight. 
     Regarding to the novel two-axis joint of the present invention, unique to joint  22  is that it is a “single point” joint. That is, joint  22  is designed to be only about a foot or so high. No other structural connection between forward unit  12  and rearward unit  14  is required by dint of the design of joint  22 . That is not to say that other structural connection cannot be made between forward unit  12  and rearward unit  14 , but that such other structural connection is unnecessary. In fact, it is a positive advantage that no other structural interconnection is needed between the two units because the combine designer has greater flexibility in locating equipment, lines, feeders, etc. because of the single point joint design disclosed herein. 
     Referring to FIGS. 3 and 4 which illustrate joint  22 , initially, however, it will be observed that a pair of steering cylinders,  46  and  48 , are seen in FIG. 2 to connect forward unit  12  to rearward unit  14  of articulated combine  10 . Such steering cylinders are conventionally used to assist in the steering of articulated vehicles and are provided here for such steering use in the present articulated combine design. Now, with respect to the two-axis joint, pipe  50  is attached to rearward unit  14  at one end and is constructed as a round pipe or structural tube because it is in the chaff/straw flow path from grain cleaning and transfer assembly  24 . Shaft  52  extends from pipe  50  towards forward unit  12  and is inserted into bearing retainer assembly  60  which is inserted between upper frame member  54  and lower frame member  56 . These frame members  54  and  56  are bolted to forward unit  12  via bolts  58   a-d,  although other attachment means certainly can be envisioned. Each frame member  54  and  56  has an inner recess which confront each other and into which is inserted bearing retainer assembly  60 . 
     Bearing retainer assembly  60  has a pair of nibs or ears which fit into frame member  54  and  56  recesses and which ride on tapered roller bearings  62   a - 62   d  to provide sideways movement to units  12  and  14  via shaft  50 . Such sideways movement permits combine  10  to be steered. A hole penetrates through bearing retainer assembly  60  into which a tapered threaded end of shaft  52  fits and is secured via nut  64 . Now, thrust bearings  66  and  68  fit into recesses which adjoin the hole through bearing retainer assembly  60  and which thrust bearings permit shaft  52  to rotate and which, thus, enable units  12  and  14  to rotate with respect to each other. Such rotation permits units  12  and  14  to traverse uneven terrain during harvesting or other movement of combine  10 . Note, however, that pipe  50  and shaft  52  are not permitted to move in a vertical direction due to the unique construction of joint assembly  22 . Thus, a unique dual axis joint has been disclosed. 
     Harvester  70  shown in FIG. 5 is a 500 bushel version of the novel articulated harvester because it has a single axle for rearward unit  72 . Wheel pair  74  again is powered and optionally steerable (all wheel pairs may be designed to be oscillating with a walking beam or non-oscillating as is necessary, desirable, or convenient in conventional fashion,) while wheel pair  76  for forward unit  78  is powered and non-steerable. Steering may be accomplished only by steering cylinders  46  and  48  in this combine embodiment. The operation of the joint axis, grain bin, and unload conveyor system remains the same for this embodiment of the present invention. 
     FIG. 6 shows yet another embodiment of the present invention where combine  80  is provided track driving system  82  for rearward unit  84 . Forward unit  86  remains the same as described with respect to combines  10  and  70 . A unique steering system for track driven combine  80  is disclosed in applicant&#39;s application Ser. No. 09/210,331, filed Dec. 11, 1998 (attorneys docket no. DIL 2-003). 
     Steering the novel articulated combine, both in the field and on roadways, presents some unique problems because of the articulation joint connecting forward unit  12  and rearward unit  14 . One steering system for accomplishing this task is set forth in FIG.  14 . The combine operator in cab  15  steers combine  10  via steering wheel  188  which is connected to valves  190  and  192 , which optionally could be replaced with a single multi-port valve. Valves  190  and  192  are fed hydraulic fluid via line  194  at, say, 2,000 psi and are also connected to reservoir  124  via lines  196  and  198 , respectively. Since steering is accomplished by both articulation steering cylinders  46  and  48 , and by a pair of steering cylinders,  200  and  202  attached to wheel pair  30  and by an additional pair of steering cylinders associated with wheel pair  32  (not shown in the drawings). Since steering is initiated by wheel pairs  30 / 32  first turning, hydraulic fluid from valves  190 / 192  flow via lines  204  and  206  to transition servo valve  208  which also is fitted with oil return lines  210  and  212  to valves  190 / 192 , respectively and line  214  which runs to tank  216  (as stated above, hydraulic fluid or oil tanks  124  and  216  may be the same or different tanks). 
     Transition servo valve  208  operates by first passing hydraulic fluid through line  218 , to check valve  220  which also has return line  222  to transition servo valve  208 . Check valve  220  is associated with steering cylinders  200 / 202  via distributor line  224 . Cylinders  200 / 202  have return distributor line  226  to check valve  220 . Check valve  220  holds the pressure on cylinders  200 / 202  in order that inadvertent bumps and other obstacles do not cause wheel pair  30  (or  32 ) to deviate from their set course unexpectedly. Now, it is anticipated that wheel pairs  30 / 32  will only need to turn a slight bit, say 10° to 20°. When wheel position sensor  228  senses that maximum travel of cylinders  200 / 202  is approaching, oil in transition servo valve  208  commences to be diverted slowly into line  230  which runs to check valve  232  which also is fitted with return line  234 . Once full stroke of cylinders  200 / 202  is reached, all of the hydraulic fluid is shunted to line  230  and check valve  220  holds cylinders  200 / 202  in position. 
     Check valve  232  is associated with steering cylinders  46 / 48  via distributor line  226  and return distributor line  238 . Steering cylinders  46 / 48  now articulate combine  10  to effect full turning of it. When the turn is completed, the system works in reverse, that is steering cylinders  48 / 48  and returned to their home position first followed by wheel cylinders  200 / 202 . The flow through transition servo valve  208  as described is intended to make the turning transition between cylinders  200 / 202  and  46148  as smooth as possible. 
     Now, operator knows the precise position of wheel pairs  30 / 32  by means of sensor  228  and of articulation steering cylinders  46 / 48  (and hence the relative position of forward unit  12  and rearward unit  14  about joint assembly  22 ) by means of sensor  240 . Sensors  228 / 240  are connected, respectively, by lines  242  and  244  to steering controller  246  which publishes their respective positions to the operator via displays  248  and  250  which are connected to controller  246  by lines  252  and  254 , respectively. Controller  246  is connected by line  256  to a source of power (say, the 12 v battery of combine  10 ) and is actuated by switch  258  which determines whether a manual or automatic articulating mode is established, switches  260  and  262  which are left/right rocker switches. These switches also are located in cab  15  for the operator&#39;s use. In turn controller  246  actuates transition servo valve  208  and manual articulate valve  264  by lines  266  and  268 , respectively. 
     Manual articulate servo valve  264  is energized by line  270  which is connected to, say, 2,000 psi hydraulic fluid with line  274  returning the fluid to reservoir  216 . Manual articulate servo valve  264  is connected by lines  276  and  278  to check valve  280  which in turn is connected by lines  282  and  284  to check valve  232 . Manual articulate servo valve  264  permits the combine operator to manually cause operation of articulation steering cylinders  46 / 48  as an override to steering controllers  246  and transition servo valve  208  Thus, the operator can permit the compound steering system to operate fully automatically or the operator can override such system and manually articulate combine  10  while steering wheel  188  controls steering wheel pairs  30 / 32 . This gives the operator the maximum flexibility in steering combine  10  in expected as well as unexpected conditions. 
     It will be appreciated that the foregoing description is illustrative of how the present invention can be practiced, but it should not be construed as limiting the present invention. Finally, all citations referred to herein are expressly incorporated herein by reference.