Background of the Invention Field of the Invention [0001] This invention related generally to binding bales of bulk material, such as cotton. In particular, the invention relates to automated bale binding apparatuses engageable with bulk material compressors. Related Art [0002] Fibrous materials, such as cotton or nylon, are typically bound into bales by compression apparatus, usually hydraulic, that compresses a volume of the fibrous material into a preconfigured bale shape and size. During compression, the bale is engaged by a bale binding apparatus that installs bale binders, such as wire, metal strap or plastic strap, in a preconfigured length around the bale. The binding wire or strap is placed around a compressed volume of material in a baling station by feeding the wire or strap through a guide track that circumscribes the volume of material to be baled and guides the wire or strap into a loop around the bale. The loop is on a single plane, typically transverse to a long axis of the bale. Thereafter, the wire or strap is released from the track, tightened around the material to be baled and fastened or knotted. After the bale wire or strap ends are fixed or knotted, compression is released and the bound bale is ejected. [0003] Baling wire performance requirements vary depending upon the fibrous material being baled. Such requirements range from industry standard specifications to general operational parameters, such as minimum speeds required for profitability. The Cotton Council issues standard baling constraints specifying particular ranges for the length of wire around the bale and the tension that the wire must withstand. [0004] Compression of bulk material into a bale is often achieved with an "up press." An up press includes a pit below floor level in which a vertically oriented hydraulic unit raises and lowers a platen in order to compress a volume of bulk material above it. The hydraulic shaft raises the platen and compresses a preconfigured volume of bulk material into a baling station, where its upward travel is arrested by an upper platen, against which the bulk material is compressed by continued upper travel of the lower platen. The baling station is above ground level where it may be engaged by a bale binding apparatus. The operations of bale binding apparatuses are described in prior patents such as U.S. Patent No. 6,637,324 to Stamps and U.S. Patent No. 6,553,900 to Daniel et al. [0005] Up presses are expensive to build and install. The cost of up presses is directly proportional to the depth of the pit required by them. Deeper pits require correspondingly longer hydraulic reaches and deeper and larger lower platens and the following blocks that support them. The deep pits with their large dimension components require more expensive materials and components, such as steel. There is a need in the industry to reduce the amount and thus the expense of materials used. Correspondingly, there is a need in the art to use shallower platens. [0006] Another form of bale compression apparatus is called a "down press." Down presses are completely above a floor level and generally include a first and second compression box for receiving a volume of bulk material to be baled. A first box is typically filled with loose material while a second box is simultaneously compressed and baled. Filling a box with loose material happens at a first position engaged with a tramper, which fills the box. Bale binding occurs at a second position having a vertically oriented hydraulic press for compressing the volume of bulk material. Binding occurs at the compression station. The boxes are transposed from the filler station to the compression and binding station by rotation around a central column. The boxes, press and central column are supported by a frame having two end columns and a support lintel. Any automated bale binding apparatus used to bind the compressed volumes of bulk material must withdraw to a position outside the circumference of the rotation of the two boxes around the center column. Withdrawal of binding equipment in a direction perpendicular to a plane defined by the support frame would require moving the apparatus an impractical distance, and would be blocked by other equipment such as supply lines for hydraulics. Accordingly, prior art disengagement apparatuses that disengage guide track portions within the same plane as the bale loop are impractical for use with down presses because the bale loop plane is perpendicular to the support frame. [0007] Current automated baling machines use an articulated track to guide wire around bales of bulk material while that bale is under compression. Part of the wire guide track in current automated balers must be removable to a second position after the ends of the baling wire have been tied together in order to allow ejection of the bale and insertion into the baler of the next unit of material for baling. Material to be baled is typically introduced into the automatic baler under vertical compression. Typical pressures for an industry standard 500 pound, 20 by 54 inch bale are in excess of 300 tons. Horizontal plates called follower blocks apply compression through platens which contact the surface of the cotton or other material being compressed. The platens incorporate slots which run laterally to the longitudinal axis of the bale. The Industry Standard number of binding wires for cotton bales is six. Accordingly, there are six slots in the platens. These allow the baling wire to be wrapped around the bale while it is still under compression. The lateral slots have lateral channels behind them for insertion of wire guide tracks in both the upper and lower platens in automatic balers. [0008] It is in the nature of the compression apparatus that the circumscribing guide track must be disengageable, at least in part, so that the compression machinery can eject a finished bale and compress a new bale. Prior art devices have achieved the disengagement of a portion of guide track either by swinging it upwards and away from the baling station or sliding it outward from the baling station. These prior art solutions are typified by a fixed guide track portion and a moveable guide track portion. Both of these portions always remained within the plane of the bale loop, whether disengaged or not. [0009] Moreover, in order to loop baling wire around bulk material to be baled, release it from a guide track and knot the ends, tension must be generated in the wire. Likewise, in order to properly knot the ends of the wire, tension must be maintained in the twisting procedure that generates the knot. The wire tension must be maintained within prescribed ranges to optimize efficiency and to produce a final bale compliant with industry standards. [00010] Typically, tension is created in the wire by reversing the wire feed mechanism, hi other words, the wire feed mechanism reverses, pulling the wire out of the track and drawing it tight against the bail. In the case of a misfeed, it is necessary to not only loop a single wire around the bale, but it is also necessary to tension the wire. There remains a need in the art for a simple but effective apparatus for feeding and tensioning a single wire loop. [00011] U.S. Patent 3,119,536 issued to Berkeley on January 28, 1964 discloses a wire feeding apparatus. The device includes a constantly rotating shaft, a first gear connected to the rotating shaft, and a second gear which is selectively engaged with the first gear. The second gear is mounted on a square bar and is biased upwardly away from the first rotating gear. The Berkeley device uses pivot arms that push the second gear downwardly to overcome the bias and engage with the first gear such that wire is fed. The Berkeley device is relatively complex and expensive due to the number of components it requires. Moreover, the Berkeley device is inefficient in that it utilizes a constantly rotating shaft. [00012] Other prior art devices achieve selective drive of separate wire feed devices by separately powering each of three or more wire feed devices with an individually dedicated servo motor. While this achieves selective engagement of individual wire feeders, it clearly multiplies the expense by using multiple servo motors. There is a need in the art for a device with selective engagability capabilities that is less expensive. [00013] Once the wire is fed around the bale, it must be fixed or knotted. Typically, this is accomplished through the use of a knotter. A knotter is connected to each track. Knotters operate internally by a receiving a leading end of a bale wire after it has been driven in a circle around the bale and overlapping that end with the trailing end of the wire that has been cut to the appropriate length. Each wire end is seated in a slot in a gear. The gears in the knotter are arranged to twist the ends in opposite directions, effectively twisting them together in a knot. These gears are driven by a shaft, which is in turn driven from outside. [00014] Current machines, if they are to provide the desired feature of selectively engaging individual knotters, or disengaging other individual knotters, must individually drive each knotter. That is, a separate drive apparatus, typically a servo motor, must be engaged with the knotter drive shaft on each individual knotter. This solution to the problem of selectable individual engagement is obviously quite expensive. There is a need in the art for a more economical method and apparatus for achieving individual engagement selected. [00015] It is not uncommon for a wire being looped around the bulk material to bind up in the track or otherwise misfeed. In this case, it is necessary to remove the bound up wire and retie the bale. Presently, there exists no easy or convenient method for retying the bale. [00016] Either the wire can be looped manually which presents some hazard to the operator, or alternatively the tied wires may be cut and the process begun again. There remains a need for an automatic baling apparatus that can correct mis-feeding errors. [00017] U.S. Patent No. 3,528,364 issued to Freund on September 15, 1970 illustrates the problem in the existing art. The Freund patent discloses an apparatus for tying bales of material after it is compressed in a baling machine. In the Freund device, material is compressed into a bale, wire is looped around the bale, and both ends of the loop are placed in a twisting apparatus. The twisting apparatus consists of a several pinions and a vertical rack. Each pinion includes two diametrically opposed slots, and the loop ends are placed in these slots. When the vertical racks are displaced, the pinions rotate thereby twisting together the two ends of the loop. Because the pinions are in constant contact with the rack it is not possible to knot a single loop of wire. [00018] Accordingly, there is a continuing need in the automated baling art to improve the efficiency, reliability, and accuracy of the bale binding process. [00019] Further, there is a need in the ait for automated bale binding equipment for use with down presses that disengages in a direction parallel with the frame of the down press and in a direction nonparallel to the bale loop plane. Concomitantly, there is a need for guide track components that are disengageable in a manner allowing such a lateral disengagement of the binding apparatus from the baling station. Additionally, there is a continuing need in the art for durability, compact size, and economy. [00020] In order to accommodate shorter lower compression platens demanded in the industry, there is a need for a bale binding apparatus that inserts and removes an insertion portion of a removable guide track section without moving the insertion portion of the lower guide track section through any space lower than the level of its final insertion level. [00021] In order to accommodate the need for shorter platens in bulk material up presses, there is consequently a need for bulk material balers designed to engage up presses in a way that accommodates shorter platens. [00022] There further remains a need in the art for a more reliable and durable wire knotter drive that is capable of selective engagement of either a single knotter or a plurality of knotters. [00023] Finally, there remains a need in the art for an economical wire feeding apparatus for feeding and tensioning wire that is simple, reliable and inexpensive. Summary of the Invention [00024] It is in view of the above problems that the present invention was developed. The present invention is an improved baling machine for baling fibrous materials. The baling machine has a stand, a bed mounted on the stand, and a baling station located above the bed and mounted to the stand, the baling station has an upper platen and a lower platen, the upper platen and the lower platen being displaceable relative to one another, and the baling machine includes at least one of the following: a laterally displaceable guide track, an apparatus for selectively driving a wire knotter, an individually selectable feed module, or a lower guide track section. [00025] The laterally displaceable guide track for a bale binding apparatus includes a carriage with a guide track portion mounted on it with a hinge. The guide track portion has an engaged position and a disengaged position. The engaged position is aligned with at least one other guide track portion to define a bale loop plane, and the disengaged position is out of the bale loop plane. The mount allows the guide track portion to be moved between the engaged position and the disengaged position. The disengaged position allows the carriage to be withdrawn from a baling station for ejection of a finished bale. [00026] The apparatus for selectively driving a wire knotter includes generally a carriage that translates along a rail. The carriage has a horizontal shaft parallel with the direction of translation parallel and with the long axis of a bale. This shaft forms a mount on which all knotters will be pivotably mounted. Parallel with the shaft for pivotal mounting is a series of holes in the vertical mounts of the carriage. The holes form a tunnel therethrough. Into this space is installed a rack that is mounted on rollers so that it may move side to side through the vertical mounting surfaces and generally perpendicular to them. The rack is two sided in that there is a driven rack and drive rack. A single servo motor is mounted to the carriage with the drive gear engaged with the driven rack facing it. The other side of the rack has the drive rack which faces the cotton bale. Each knotter has an outwardly projecting drive shaft with a gear on it. When rotated into position, the gear meshes with the drive rack. Accordingly, when the single servo motor is turned, the rack translates and each knotter that is engaged with the rack is driven for operating its knotting functions. [00027] The individually selectable feed module includes a motor that rotates a drive shaft. Each wire feeder includes a fixed gear driven by the drive shaft and a pivotable gear that is adapted to move toward and away from the fixed gear. A feed wheel is connected to each gear. As the two gears approach one another and become engaged, the feed wheels frictionally engage a wire, thereby feeding it between them. [00028] In one embodiment, the pivotable gear is mounted on an eccentric and the eccentric is rotated by a linear actuator via a pivotable arm. The linear actuator extends linearly and rotates the eccentric. Rotation of the eccentric causes the pivotable gear to move toward or away from the fixed gear. As such, the linear actuator can be used to selectively control when the wire is fed through each individual wire feeder. [00029] The lower guide track section includes a platen portion, a first extension, a second extension, a first guide track section, and a second guide track section. The platen portion is substantially as long as a platen slot and dimensioned for deployment within the platen slot. The first extension extends outward from a first extent of the platen. The second extension extends outwards from a second extent of the platen in a direction opposite the first extension. The first extension has a strap receiving end face configured to cooperate with a first strap guide track on a carriage such that the first strap guide track on the first carriage is dimensioned to index laterally beyond a press frame. The second extension has a strap exit end face configured to cooperate with a second strap guide track on a second carriage such that the second strap guide track on the second carriage is dimensioned to index laterally beyond the press frame each of the receiving end face and the exit end face has a medial border and a peripheral border. The first guide track section is adapted for mounting on a laterally displaceable carriage and has an exit end face. The exit end face is adapted to operatively cooperate with the receiving end face of the first extension. The second guide track section is adapted for mounting on a second laterally displaceable carriage and has a receiving end face. The receiving end face is adapted to operatively cooperate with the exit end face of the second extension. The first carriage guide track section exit end face and the second carriage guide track section receiving face each have a medial border and a peripheral border. The medial borders of the first and second carriage guide track section end faces are dimensioned to define a clearance length. [00030] The invention further comprises guide track dimensions designed to accommodate the preexisting dimensions of down packer beds, while maintaining an optimal turning radius for guiding 10 gauge wire without jamming. The resolution of these industry problems is two-fold. First, a turning radius of a guide track channel is begun while the channel remains under the platen. Secondly, a first turning radius of 30 to 45 degrees is combined with a second turning radius 30 to 45 degrees. Within the guide track extensions these separate turning radiuses are separated by an intermediate portion having a much shallower arc or which may be substantially flat. It is another property of 10 guage binding wire that, when driven at high speeds, has a lower tendency to jam if turned incrementally, rather than continuously. [00031] The present inventions also include a bulk material bale binder. The bulk material bale binder has a stand adjacent a baling station and being installed to bind bales compressed by an up press having a moving lower platen, the lower platen having insertion slots for guide tracks. A guide track removal and insertion apparatus has a guide track removal frame, the frame being hingedly mounted on the stand such that the guide track removal frame may rotate between an engaged position and a removed position. A guide track mount, pivotably mounted on the guide track removal frame has an insertion position and a retracted position. A guide track section attached to the guide track mount has an insertion portion. A linkage has a first end operatively engaged with a stand and the second end operatively engaged with the guide track mount, such that during insertion and removal of the insertion portion of the guide track, the insertion portion remains at or above an insertion level at all times. [00032] Further features and advantages of the present invention, as well as the structure and operation of various embodiments of the present invention, are described in detail below with reference to the accompanying drawings. Brief Description of the Drawings [00033] The accompanying drawings, which are incorporated in and form a part of the specification, illustrate the embodiments of the present invention and together with the description, serve to explain the principles of the invention. In the drawings: [00034] Figure 1 is a perspective view of a down press, with a bale binder apparatus of the present invention disengaged; [00035] Figure 2 is a perspective view of a down press with a bale binder apparatus of the present invention with the guide track carriages in place and disengaged; [00036] Figure 3 is a perspective view of a down press with the guide track carriages in place and the guide track portions engaged; [00037] Figure 4 is a top view of a down press with the binder carriage of the present invention in place and the guide track portions withdrawn; [00038] Figure 5 is top view of a down press with the binder carriages in place and the guide track portions engaged; [00039] Figure 6 is a side view of a down press with the guide track carriages of the present invention in place and the guide track portions disengaged; [00040] Figure 7 is a side view of a down press with the binder carriages of the present invention in place and the guide track portions engaged; [00041] Figure 8 is a top view of the laterally disengageable guide track portion of the present invention in an engaged position; [00042] Figure 9 is a side view of the laterally disengageable guide track portion of the present invention in an engaged position; [00043] Figure 10 is a top view of the laterally disengageable guide track portion of the present invention in a disengaged position; [00044] Figure 11 is a side view of the laterally disengageable guide track portion of the present invention in a disengaged position; [00045] Figure 12 is a perspective view of the driver/knotter carriage of the present invention wit the guide track portions disengaged; [00046] Figure 13 is a perspective view of the driver/knotter carriage of the present invention with the guide track portions engaged; [00047] Figure 14 is a top view of the driver/knotter carriage of the present invention with the guide track portions disengaged; [00048] Figure 15 is a top view of the driver/knotter carriage of the present invention with the guide track portions engaged; [00049] Figure 16 is a front view of the driver/knotter carriage of the present invention with the guide track portions disengaged; [00050] Figure 17 is a front view of the driver/knotter portion of the present invention with the guide track portions engaged; [00051] Figure 18 is a side view of a guide track portion of the present invention mounted on its bracket in a disengaged position; [00052] Figure 19 is a side view of a guide track portion of the present invention on its mounting bracket in engaged position; [00053] Figure 20 is an exploded view of the receiver carriage of the present invention; [00054] Figure 21 is a front perspective view of the receiver carriage in the present invention; [00055] Figure 22 is a rear perspective view of the receiver carriage in the present invention; [00056] Figure 23 is an exploded view of the moveable guide track portion and its mount; [00057] Figure 24 is a side view of the multiple knotter drive in a first disengaged position; [00058] Figure 25 is a side view of the multiple knotter drive in a second engaged position; [00059] Figure 26 is an exploded view of the knotter; [00060] Figure 27 is a detailed perspective view of the servo motor and gear drive; [00061] Figure 28 is an exploded view of the servo motor gear drive and rack; [00062] Figure 29 is an alternative embodiment showing multiple knotters; [00063] Figure 30 is a schematic drawing of a control system; [00064] Figure 31 is a perspective view of a cotton baler; [00065] Figure 32 is a partial perspective view of a carriage unit; [00066] Figure 33 is a front view of the carriage unit; [00067] Figure 34 is a perspective view of the knotter drive; [00068] Figure 35 is a side view of the knotter drive in a second engaged position; [00069] Figure 36 is a side view of the knotter drive in a first disengaged position; [00070] Figure 37 is a perspective view of the wire feeding apparatus; [00071] Figure 38 is a rear perspective view of the wire feeding apparatus; [00072] Figure 39 is an exploded view of the wire feeding apparatus; [00073] Figure 40 is a perspective view of a cotton baler; [00074] Figure 41 is a perspective view of the carriage unit; [00075] Figure 42 is an exploded view of a motor drive gear box and drive shaft; [00076] Figure 43 is a schematic view of a control system; [00077] Figure 44 is a side view of the carriage unit illustrating the linear actuator in a first position; [00078] Figure 45 is a side view of the carriage unit illustrating the linear actuator in a second position; [00079] Figure 46 is a perspective view of a down packer and a laterally displaceable binder apparatus; [00080] Figure 47 is a schematic side view of the guide track of the present invention; [00081] Figure 48 is a perspective close up view of the bale binding loops of the present invention; [00082] Figure 49 is a side view of the bale binding loops; [00083] Figure 50 is a top view of the bale binding loops; [00084] Figure 51 is a perspective view of the lower guide tracks sections and lower platen; [00085] Figure 52 is a side view of the lower guide track of the present invention; [00086] Figure 53 is a side view of a prior art baler; [00087] Figure 54 is a partial top view of a prior art baler; [00088] Figure 55 is a side view of the present invention in an engaged position; [00089] Figure 56 is a side view of the present invention in a first removed position; [00090] Figure 57 is a side view of the present invention in a second intermediate removed position; [00091] Figure 58 is a side view of the present invention in a third intermediate removed position; [00092] Figure 59 is a side view of the present invention in a fourth intermediate removed position; [00093] Figure 60 is a side view of the present invention in a fully removed position; [00094] Figure 61 is a front view of the present invention; [00095] Figure 62 is a close up of a swing arm; [00096] Figure 63 is a close up of a lower pivot of a second tie rod; [00097] Figure 64 is a close up front view of a swing arm; and [00098] Figure 65 is a side view of the invention. Detailed Description of the Preferred Embodiments [00099] Referring to the accompanying drawings in which like reference numbers indicate like elements, Figure 1 illustrates a down press 10. The down press 10 generally includes a first compression box 12 with a first baling side 6 and a second compression box loading side 8. A second compression box is omitted for clarity on the loading side 8. While a first bale is being compressed and bound in baling station 24, oriented on the near side of the perspective image in Figure 1, a second compression box is being loaded with cotton at the loading side 8. Compression boxes 12 are moved from the loading size 8 to the baling side 6 by rotation around a vertical axis formed by a central piston 18 within central column 14. That is, the compression box 12 and central column 14 rotate so that the compression box 12 moves into the baling portion 6 with a load of loose cotton, there to be compressed from above by hydraulics (not shown). Bed 4 rotates also. The components of the down press that remain stationary are base 2 and end column 16. An opposite end column is omitted for clarity. [000100] On the baling side 6 of the down press a baling station 24 is formed. The baling station floor is one of the lower platens 20 or 20'. The lower platen 20 receives, restrains and resists against the compression of a volume of bulk material being down pressed onto it from above. The cotton is pressed down and the top side of the baling station is formed by upper platen 22. Upper platen 22 is connected to the vertically oriented downwards moving hydraulics (not shown) that move through the compression box 12. [000101] After a volume of bulk material has been compressed and bound with wire or strap, it is ejected from baling station 24. Simultaneously with the bale binding operation, the other compression box has been loaded at loading side 8. Thereafter, the down press rotates again and through its rotation transposes the position of the now empty compression box 12 and the other compression box (not shown), now loaded with uncompressed cotton. Clearly, in order to operate, there must be a clear path of 360 degrees around center axis 18 with a radius equal to the width of a compression box 12 and the bed 4. Accordingly, any binding equipment must be withdrawn beyond that radius. The prior art technique of removing binding equipment outward or upward parallel to the bale loops is impractical. The shortest removal distance is parallel to a radius of the rotation. [000102] In order to do this, the binding apparatus of the present invention has a first driver carriage 40 and a second return carriage 42. Each carriage includes an assembly of mounting brackets 50, generally vertically oriented. Driver carriage 40 rides laterally on a rail 43. Likewise, return carriage 42 rides on rail 44. The rails are oriented to be parallel with the long side of the compression box 12 and the bed 4. The first carriage 40 also carries with it multiple wire or strap drivers 46 and multiple wire knotters or strap fasteners 48. In the depicted embodiment, carriage 40 carries three wire drivers 46 and three knotters 48. There are six baling wires to be installed on a standard bale of cotton. Accordingly, in addition to translating along rails 43 and 44 to withdraw from the down press 10, the bale binding apparatus of the present invention also translates between a first three binding wire positions and a second three binding wire positions. [000103] Guide rails work in a known fashion, such as described in U.S. Patents 6,637,324 to Stamps and 6,553,900 to Daniel. Essentially, two longitudinal halves of any guide track portion are biased together by springs. They have a longitudinal channel therein for receipt and guidance of a progressing bale wire. The various guide track portions are oriented around a baling station, and consequently a bale in order to complete a loop of baling wire around the volume of bulk material to be baled. After a driver drives the wire through the complete guide track, a tensioning mechanism retracts the baling wire or strap from the guide track and tightens it around the bulk material. The tension placed on the bale wire or strap in a radially inward direction is sufficient to overcome the spring bias holding the lateral guide sections together, thereby releasing the wire or strap from the guide track for it to be tensioned against the bale, and fastened. [000104] The overall guide track of the present invention includes lower guide track portions 30, which reside in the lower platens 20 and 20', 32 and upper guide track portions which reside in the upper platen 22 and the guide track portions that form components of the carriages 40 and 42. All of these components are on a single bale loop plane that is perpendicular to the long axis of the bale. [000105] Figure 2 shows the bale binding apparatus of the present invention in its inward position, with its guide tracks disengaged. In figure 2, end column 16 and center column 14 are depicted along with bed 4 and stand 2 of the down packer. The compression box 12 has been omitted for clarity. Upper platen 22 appears, but the mechanisms that support it in the depicted compressed and ready to bale position, i.e., the hydraulic press, has been omitted for clarity. The compression hydraulics are oriented above the compression box 12 and supported by center column 14 and end column 16. [000106] It is apparent from figures 2 and 3, and particularly top views 4 and 5 that the width of the upper platen 22 is less than the width of the end column 16. hi order for guide tracks to work properly, the gap between one guide track portion and the next must be relatively narrow, on the order of an inch or so. End column 16 is substantially more than an inch wider than upper platen 22. Accordingly, in order for the carriages 40 and 42 to translate laterally out of and back into binding position, the guide track portions mounted on the carriages 40 and 42 must have a removed position sufficiently wide for those components to clear the end column 16. The present invention is directed towards overcoming this problem in an economical, durable, fast and precise way. [000107] Both carriages 40 and 42 have upper guide track portions 60 and 90 respectively. These guide track portions are mounted such that they have an extended, engaged position which is extended closer to one another, and narrows the gap between. This narrower space corresponds to the width of the upper platen 22, thereby bringing the upper guide track portions 60 and 90 into operative engagement and close, operative communication therewith. Upper guide track portions 60 and 90 also have a removed, disengaged position characterized by the fact that the removed position widens the gap between upper guide track portion 60 and 90 to a width sufficient to clear the end column 16 when the carriages 40 and 42 translate out of baling position, to allow the down packer to rotate. [000108] Figures 2, 4, 6 (end view) all show the upper guide track portions 60 and 90 in their disengaged, removed position. Figures 3, 5 and 7 show the upper guide track portions 60 and 90 in their engaged, operative position. In the depicted embodiment, the mounting of the guide track portion 60 and 90 is by a hinge, oriented on a substantially vertical axis. In the depicted embodiment, the movement of the upper guide track portions 60 and 90 between their removed, disengaged and their extended, engaged positions is mediated by a piston and cylinder which in the depicted embodiment is pneumatic. Other types of linkages and linkage actuators are within the scope of the present invention. [000109] Figures 8 and 9 show the guide track portion 60 of the present invention in its engaged position. In the engaged position, the guide track portion 60 is aligned with other guide track portions in a single plane. This plane will define the bale loop. A receiving face 62 of the guide track will receive a driven bale wire or strap from another guide track portion (not shown), which in the depicted embodiment would be a top portion that would guide bale wire or strap through an upper platen of the compression apparatus. Guide track portion 60 guides the wire or strap through a 90 degree turn from a horizontal direction across the top of a bale to a downward direction where it exits guide track portion 60 at exit face 63, thereafter to be received by a next guide track portion 64, which in turn guides the wire or strap into a fastener for fastening. Both moveable guide track portion 60 and the fixed guide track portion 64 are mounted on a mounting bracket 50. The carriage 40 will be laterally displaceable, generally along a plane defined by the frame of the down press, in the depicted embodiment. The moveable guide track portion 60 is mounted to mounting bracket 50 at hinge 52. It is further mounted to a moveable linkage providing for at least two positions of the moveable guide track portion 60. In the depicted embodiment, the linkage is a piston and cylinder assembly 70. The piston and cylinder assembly 70 is pneumatic in the depicted embodiment. Other drive methods may be used in alternative embodiments. A piston 74 is extendable from and retractable to cylinder 72. Cylinder 72 is hingedly attached at pivot point 82 to a further mount 80 which is fixedly attached to another portion of the carriage (not shown in Figure 8). Piston 74 is hingedly attached to bracket 76 at pivot point 78. [000110] Figures 10 and 11 are a top and side view respectively of the moveable guide track portion in a disengaged position. In figures 10 and 11 the piston 74 has been extended from cylinder 72. Through rotation at hinge points 78 and 82, the piston cylinder assembly extends to rotate bracket 76, which in turn rotates moveable guide track portion 60 to a disengaged position. The disengaged position is out of the plane of a bale loop. [000111] As can be seen by comparing the engaged position in figures 8 and 9 with the disengaged position in figures in 10 and 11, the moveable guide track portion extends into a baling station space when in its engaged position, and retracts from the baling station space to an overall dimension that is sufficient to clear the end column (not shown) when the carriage is withdrawn along the plane of the frame of the down press. [000112] Figures 12 - 19 are an assembly of three moveable guide track components 60 linked together as they would be on a three loop carriage. Figures 12, 14, 16 and 18 depict the moveable guide track portion 60 in its refracted, disengaged position. Figures 13, 15, 17 and 19 depict the moveable guide track portion 60 in its extended, engaged position. [000113] The laterally displaceable guide track portions and their mounting and actuation of the present invention may be deployed in any number of bale loop assemblies. Although in the depicted embodiment, three are shown, any where from one to eight, of guide track assemblies, corresponding to the number of loops on a standard (6) or a universal (8) bale, or less, is within the scope of the present invention. The assembly shown in the figures 12 - 13 appear in their three mount configuration in Figures 1 - 7. [000114] Figures 20, 21 and 22 depict the receiving side of the bale wire loop guide track, including the laterally displaceable receiving guide track portion 90. In these pictures, the receiving laterally displaceable guide track portion is shown in its extended position. [000115] Receiving laterally displaceable guide tracks 90 are moved between their extended and retracted positions together by piston and cylinder assembly 92, which includes cylinder 94 and piston 96. This piston cylinder assembly 92 is pivotably mounted to a stationary carriage wall 52 at pivot point 98 and again pivotably mounted to tie bar 100 at pivot point 102. By retracting piston 96, tie bar 100 is moved laterally, and the receiving laterally displaceable guide track portions 90 may be moved from their extended, engaged position to a retracted, disengaged position. The receiving laterally displaceable guide track portions 90 pivot out of the plane of bale loop around their hinged mounting 104. [000116] Similarly to the driver/knotter carriage 40, the receiving carriage 42 has components generally below the guide track components for mounting on a rail so that it may translate laterally between a withdrawn and an inserted position. [000117] Figure 23 is an exploded view of a subassembly of a single moveable guide track portion 60 as mounted on a single vertical carriage wall 51. [000118] In operation, the carriages 40 and 42 of the bale binding apparatus are in a withdrawn position, which is to say laterally displaced along rails 43 and 44 as seen in Figure 1. A finished bale is removed or ejected from the baling station 20 of baling side 6 of the down packer 10. While this bale has been bound, the other compression box (not shown) has been loaded with loose bulk material at loading side 8 of down packer 10. With the carriages 40 and 42 laterally displaced a sufficient distance, the down packer central column 14 and compression boxes 12 rotate around the vertical axis of center pivot 18. The upper platen 22 has been withdrawn upwards to provide clearance for rotation of compression box 12. When the new compression box 12, now full of loose material, has arrived at the binding portion 6 of the down packer 10, the carriages 40 and 42 translate laterally and inwardly along rails 43 and 44 until they arrive at a first binding position engaged with the baling station 24. [000119] In an embodiment having six bale loop guide tracks, knotters and drivers, there will only be one bale binding position. In the depicted embodiment, having three bale loop guide tracks, there will be two binding positions for the carriages 40 and 42. [000120] During the withdrawal translation of the carriages 40 and 42, all of the guide track portions 60 and receiving guide track portions 90 are in their retracted, disengaged position as seen in figures 2, 4, 6, 10 and 11. [000121] The carriages 40 and 42 advance either sequentially or simultaneously with the compression of the bulk material through compression box 12 by vertically oriented and downward progression of the hydraulics (not shown), until they are in baling position. When the top platen 22 has extended completely downwards, the bulk material has been compressed and is maintained in its compression between lower platen 24 and upper platen 22. At this point, all moveable guide track portions 60 and all moveable receiving guide track portions 90 are swung around vertical pivots into their extended engaged positions. These are indexed to correspond to the matching lower guide tracks 30 and upper guide tracks 32 pre-positioned in the slots provided for them in the lower platens 20 and upper platens 22. Each guide track portion has an exit end and a receiving end that closely cooperates with a receiving end and an exit end of its adjacent guide tracks. At this point, there are three complete guide track loops, each in a separate and parallel plane. This plane is non-parallel with, and, in the depicted embodiment, perpendicular to the lateral axis of the rails on which the carriages 40 and 42 travel. The lateral direction of the rails corresponds to the long axis of the bale. [000122] Wire or strap (wire in the depicted embodiment) is then driven in a complete circuit around the bale through all guide track portions. When a leading end of the bale wire arrives at the knotter attached to the carriage 40, a gripper, as is known, retains the leading edge, drive apparatuses are reversed in order to pull the wire out of guide track, also in a known fashion, so that the wire is drawn into contact with the bulk material being baled. Thereafter, a knotter knots the leading and trailing ends of the wire. The carriages 40 and 42 then translate laterally from a first baling position engaging a first three set of guide tracks to a second baling position engaging the second three sets of guide tracks. The baling process repeats. [000123] When six bale wires are in place and knotted, compressing pressure may be released. In the case of the down packer as depicted, pressure is released by raising the upper platen 22 with the vertical hydraulics. Either sequentially or simultaneously with a release of pressure, the carriages 40 and 42 may be laterally translated out of engagement with the baling station 24 and the rest of the down packer 10. However, in order to clear the width of end column 16, at this point the piston and cylinder assemblies 70 and 92 are activated in order to rotate the moveable guide track portion 60 and receiving moveable guide track portions 90 from their extended, engaged position to their retracted, disengaged position, which is preconfigured to provide a space wider than the width of end column 16. Thereafter, carriages 40 and 42 will translate laterally out of engagement with the baling station 20 and past end column 16 without any contact with any of the moveable guide track portion 60 or receiving moveable guide track portions 90. This process repeats. [000124] The down press 10 includes one or more knotters for knotting the strap or wire. In the case of multiple knotters, it would be beneficial to have a single drive for all of the knotters. [000125] Figures 24 and 25 illustrate a multiple knotter drive 210. The multiple knotter drive 210 includes a knotter 212, a bearing 214, and a tilt-out shaft 236. The knotter 212 is a device that, when engaged, twists together two ends of a wire loop wrapped around a bale. The bearing 214 is connected to the knotter 212 and mounted on the tilt-out shaft 236. As such, the knotter 212 is pivotable about the tilt-out shaft 236. A strap 240 is used to limit the degree to which the knotter 212 can pivot. One strap end is attached to the knotter 212 and the other strap end is attached to the carriage unit. In the event that maintenance is required on either a knotter or the rack, the strap can hold the knotter in a position convenient for maintenance without allowing it to swing freely. [000126] A knotter drive gear 230 is mounted on the knotter 212. In the depicted embodiment, the knotter gear 230 is a 21 tooth gear with a 1.67 inches (42 mm) pitch diameter and an outer diameter of 1.83 inches (47 mm). Turning this gear operates the knotter 212 to fasten wire ends. [000127] A linear actuator 216 is connected to the knotter 212. The linear actuator 216 moves linearly to pivot the knotter 212 about the tilt-out shaft 236. In the embodiment depicted in Figure 24, the linear actuator 216 is in a first disengaged position, and in the embodiment depicted in figure 25, the linear actuator 216 is in a second engaged position, hi the depicted embodiments, the linear actuator 216 is an air cylinder; other devices, however, may be used. [000128] The apparatus 210 also includes a servo motor 226, a gear box 224, and a pinion 228. The apparatus 210 further includes a rack 218. The rack 218 includes driven rack 222 and drive rack 220, which are fixed relative to one another. The pinion 228 drives the driven rack 222, and the drive rack 220 turns knotter drive gears 230. In the depicted embodiment, the pinion 228 has 48 teeth, a pitch diameter of 3.82 inches (97 mm), and an outside diameter of 3.98 inches (101 mm). The servo motor 226 provides a rotational input to the gear box 224, and a rotational output of the gear box 224 rotates the pinion 228. hi the depicted embodiment, the gear box 224 is a reduction-type gearbox with a ratio of 35:1. In other words, in the depicted embodiment, 35 full rotational inputs by the servo motor 226 results in 1 full rotational output by the gear box 224. [000129] The linear actuator 216 pivots the knotter 212 about the shaft 236 to selectively engage the knotter drive gear 230 with the rack 218. For example, in the first position depicted in Figure 24, the knotter drive gear 230 is disengaged but engaged in the embodiment depicted in Figure 25. [000130] Figure 26 provides a more detailed view of the knotter 212. The knotter 212 includes a twister housing 242 and a twister main shaft assembly 244. In the depicted embodiment, twister housing 242 and the twister main shaft assembly 244 are connected to one another using screw fasteners but other techniques may be used. The twister housing 242 includes a twister pinion 248. The twister main shaft assembly 244 includes a twister main shaft 246 and a twister drive gear 245. The twister drive gear 245 is connected to the twister main shaft 246. When the twister housing 242 is assembled to the twister main shaft assembly 244, the twister drive gear 245 is in driving communication with the twister pinion 248. The knotter drive gear 230 (not shown in Figure 26) is adapted for mounting on the twister main shaft 246. In operation, two ends of a wire loop are inserted into the twister housing 242. Then the knotter drive gear 230 rotates the twister main shaft 246, which rotates the twister drive gear 245 and ultimately the twister pinion 248. The rotating twister pinion 248 twists together two ends of a wire loop engaged by it. [000131] Referring to Figures 27 and 28, a more detailed view of the servo motor 226, gear box 224, and the rack 218 are shown. The rack 218 includes a driven rack 222 and drive rack 220. The drive rack 220 and the driven rack 222 are mounted on a rack bar 232. In the depicted embodiments, the driven rack 222 is 9.25 inches (235 mm) in length, and the drive rack 220 is about 30 inches (762 mm) in length. In the depicted embodiments, the drive rack 220 is mounted offset from the driven rack 222. However, in some embodiments, the drive rack 220 and the driven rack 222 are mounted on the same side of the rack bar 232. [000132] The pinion 228 is mounted on the gear box 224 which is connected to the servo motor 226. The servo motor 226 provides rotational input to the gear box 224 and output of the gear box 224 rotates the pinion 228. The pinion 228 engages the drive rack 222 and moves the rack 218 linearly. In the embodiments depicted in figures 27 and 28, the rack moves linearly about 0.343 inches (8.7 mm) for every full rotational input by the servo motor 226. [000133] In the embodiment depicted in Figure 29, there are three knotters 212 selectively engageable with the rack 218. While there are three knotters 212 in the depicted embodiment, those skilled in the art will understand a greater or lesser number of knotters can be used. For example, there may be as many as eight or as few as one knotter 212. The knotters 212 are selectively engaged by controlling the operation of the respective linear actuator 216. [000134] A control system 250 is illustrated in Figure 30. The control system 250 includes a control module 252. Other components of the control system 250 are described in U.S. Patent No. 6,628,998 issued to Stamps et al. on Sept. 30, 2003. The control module 252 is operatively connected to linear actuators 216a, 216b, 216c, and to the servo motor 226. As examples, the control module 252 and the linear actuators 16 may be electrically or pneumatically connected. The control module 252 may receive input directly from an operator or instructions from another machine. The control module 252 selectively engages the linear actuators 216 and the servo motor 226. In one example, the control module 252 engages all three linear actuators 216a, 216b, and 216c and subsequently engages the servo motor 226. In another example, the control module 252 engages only one of the linear actuators, such as 216b, and subsequently engages the servo motor 226. In yet another example, the control module 252 engages two of the linear actuators, such as 216a and 216c, and subsequently engages the servo motor 226. In this manner, the knotters 212 can be selectively engaged. For example, if a wire mis-feeds in a particular track, the wire can be re-strung and the particular knotter can be singularly engaged to tie the re- strung wire. Alternatively, a malfunctioning knotter may be disengaged. Its corresponding bale loops may be knotted by another knotter, which would be indexed into its position as signaled by the controller. [000135] Figure 31 illustrates the fibrous material baling machine 10. As an example only, the multiple knotter drive 310 may be incorporated into the down packing machine 10. The multiple knotter drive may also be used with "up packers," or otherwise. The baling machine 10 includes the carriage unit 40, and the carriage unit 40 includes the multiple knotter drive 310 (best seen in figure 32). The carriage 40 rides on the rail 43. The rail 43 is oriented such that the carriage 40 and the binding equipment mounted on it may be withdrawn from proximity with the press. [000136] Figures 32 and 33 provide a more detailed view of the carriage unit 40. The carriage unit 40 includes a servo motor 326, a gear box 324, a pinion 328, and a rack 318. The servo motor 326 provides rotational input to the gear box 324, and the gear box 324 rotates the pinion 328. The pinion 328 is in driving relationship with the rack 318 and moves the rack 318 linearly when the pinion 328 is rotated. The carriage unit 40 also includes plates 360, on which components are mounted. The plates 360 are vertically oriented and each have an opening 361 which receives the rack 318. [000137] As can be seen, the rollers or cam followers 334, 335 are used to mount the rack 318 in a way that allows for its lateral translation. They are oriented both for vertical and horizontal roller axes. The rollers 334, 335 are arranged in any configuration that will allow side to side translation but otherwise restrain the rack from movement in any other direction. [000138] Cam followers 334 are mounted on the plates 360 and are in rolling contact with the rack 318. The cam followers 334 guide and support the rack 318 within the opening 361. Some embodiments may include additional cam followers 335 to further guide the rack 318. [000139] The rack 318 is only as long as it needs to be; typical knotters twist the wire ends together seven times, and, this requires a lateral translation of the rack for execution. [000140] Also mounted on the carriage unit 310 is a tilt-out shaft 336. The tilt- out shaft 336 traverses the plates 360 and is held in place by collets 338. The tilt-out shaft 336 is used to support a knotter 312 (best seen in Figure 34). [000141] Referring now to Figure 34, a bearing 314 is mounted on the knotter 312, and the bearing 314 is connected to the tilt-out shaft 336. In this manner, the knotter 312 is pivotable about the tilt-out shaft 336. A linear actuator 316 (best seen in Figures 35 and 36) is connected to the knotter 312. [000142] The linear actuator 316 is mounted in any convenient place on the carriage. The actuator may be mounted to the vertical plates 360. It may be hingedly mounted to facilitate a rotational motion of the knotter. The opposite end of the actuator 316, the piston arm, is hingedly mounted to the knotter. [000143] In Figure 34, the knotter engagement actuator 316 is obscured by an overlying actuator. This is the actuator for the guide track, which is hingedly mounted and may be laterally displaced. [000144] Figures 35 and 36 respectively illustrate a first and second position of the linear actuator 316. In the first position, the linear actuator 316 is retracted. In the second position, the linear actuator 316 is extended. [000145] The rack 318 includes a driven rack 322 and a drive rack 320. The driven rack 322 engages the pinion 328, and the drive rack 320 selectively engages a knotter drive gear 330. The knotter drive gear 330 is placed in a driven relationship with the drive rack 320 when the linear actuator 316 is in the second extended position and is removed from the driven relationship when the linear actuator 316 is placed in the first position, hi the first position, there is about 0.4 inches (11 mm) of clearance between the drive rack 320 and the knotter drive gear 330. [000146] In operation, the linear actuator 316 is engaged such that it pivots the knotter 312 about the tilt-out shaft 336 thereby engaging the knotter drive gear 330 with the drive rack 320. Thereafter, the servo motor 326 is engaged. When the servo motor 326 is engaged, the servo motor 326 rotates an input of the gear box 324 such that the gear box 324 rotates the pinion 328. The pinion 328 moves the rack 318 linearly such that knotter drive gear 330 is rotated. Accordingly, operation of the servo motor 326, when the knotter drive gear 330 is in communication with the drive rack 320, causes the knotter 312 to knot the ends of the wire loop which is wrapped around the bale. [000147] The knotter has mounted upon it an entry section of guide track. This section of guide track receives a leading end of a wire that has been driven in circle around the bale. This end is received from a next preceeding guide track portion. The knotter guide track portion has a curved engagement face, in order to accommodate the rotation of the knotter assembly out of engagement with the rack. Further disengagement of the knotter assembly by rotation around the mounting shaft 336 allows greater access for maintenance, particularly in light of the removal with the knotter of the aforesaid section of guide track. [000148] There is also provided a method of assembling an apparatus for selectively driving a pivotable knotter. The method includes the steps of: providing a tilt-out shaft; pivotably mounting at least one knotter on the tilt-out shaft; providing a rack; placing a pinion in driving communication with the rack; connecting a knotter drive gear to the pivotable knotter; and connecting a linear actuator to the pivotable knotter, the linear actuator adapted to pivot the pivotable knotter from a first engaged position to a second disengaged position such that lateral movement of the rack drives all knotters that are in the engaged position. [000149] There is provided a method of selectively engaging a pivotable knotter. The method includes the steps of: providing a rack; providing a servo motor in a driving relationship with the rack; connecting a knotter drive gear to the pivotable knotter; connecting a linear actuator to the pivotable knotter; actuating the linear actuator such that said knotter drive gear engages the rack; and engaging the servo motor such that the rack moves linearly and rotates the knotter drive gear. In some embodiments, the method further includes the step of selecting a linear actuator for engagement via a control module. [000150] Should an individual knotter or the rack require maintenance, the actuator can be engaged to withdraw the knotter for maintenance. The actuator may be disengaged and the knotter held in a convenient position for maintenance by strap 340. A degree of disengagement for maintenance may be greater than a simple disengagement due to malfunction to be maintained during continued baling operations with the other functioning knotters. [000151] The down press 10 includes one or more apparatus for feeding the strap or wire around the bale. It would be beneficial to have a wire feeding apparatus that is selectively engageable. [000152] Figures 37 and 38 illustrate a wire feeding apparatus 410. The wire feeding apparatus 410 includes a base plate 412, a first gear 414, a first feed wheel 416, a second gear 418, and a second feed wheel 420. The wire feeding apparatus 410 also includes wire guides 426. The wire guides 426 direct the wire into and away from the feed wheels 416, 420. [000153] The gears 414, 418 have a ratio in the range of about 1 : 1 to about 2:1. As an example, each gear 414, 418 may have 42 teeth. In the depicted embodiment, the gears 414, 418 are made of crucible steel, and the wheels 416, 420 are made from tool steel. In some embodiments, the wheels 416, 420 are also black oxide coated. The first feed wheel 416 is connected to the first gear 414, and the second feed wheel 420 is connected to the second gear 418. [000154] In the depicted embodiments, each wheel 416, 420 is circumscribed by three grooves 460. Those skilled in the art will understand that a greater or lesser number of grooves may be used. The grooves 460 are dimensioned to accept a particular size of wire. As an example only, the grooves 460 may be dimensioned to accept a 10 gauge wire. The grooves 460 on each wheel 416, 420 are aligned with the grooves on the other wheel. [000155] The first gear 414 is pivotable such that it can be moved toward and away from the second gear 418. As the first gear 414 is pivoted towards the second gear 418, the two gears 414, 148 intermesh such that a wire is captured between the grooves 460 of the feed wheels 416, 420, thereby feeding the wire. [000156] The wire feeding apparatus 410 also includes an eccentric 436, a pivotable arm 422, and a linear actuator 430. As used herein, the term "eccentric" means a component having an eccentric axis of revolution so that the component can impart reciprocating motion. In the depicted embodiment, the eccentric 436 is a cylinder with a hole 437 offset from the center of the cylinder. The hole 437 is adapted to receive a first spindle 432, and the eccentric 436 rotates about first spindle 432 located in the hole 437. In the depicted embodiment, the first gear 414 rotates about the eccentric 436. [000157] The pivotable arm 422 is operatively connected to the first gear 414 such that as the pivotable arm 422 is pivoted, the first gear 414 moves toward or away from the second gear 418. In the depicted embodiment, the eccentric 436 includes a slot 462 that receives the pivotable arm 422 and moves with the pivotable arm 422. As such, when the pivotable arm 422 moves, the eccentric 436 rotates about the first spindle 432. [000158] The linear actuator 430 pivots the pivotable arm 422. In the depicted embodiment, the linear actuator 430 is an air cylinder and includes fittings 428 for receiving a fluid, such as air. However, other types of actuators, a hydraulic cylinder for example, may be used. The linear actuator 430 not only provides a simple mechanism for selectively engaging the feed wheels, but also the linear actuator 430 compensates for wear in the grooves 460 to ensure that the wire is adequately engaged. In other words, as grooves 460 wear out, to a limited extent, the linear actuator 430 decreases the distance between the feed wheels 416, 420. When the linear actuator 430 moves the pivotable arm 422, the pivotable arm 422 rotates the eccentric 436. Thus, actuation of the linear actuator 430 rotates the eccentric 436 and moves the first gear 414 toward or away from the second gear 418. [000159] Figure 39 illustrates an exploded view of the wire feeding apparatus 410. The wire feeding apparatus 410 includes a connecting arm 424, the feed wheels 416, 420, a grease fitting 458, an external bearing 439, a thrust washer 451, a first grease seal 440, a spherical roller bearing 441, a second grease seal 452, the eccentric 436, a retaining ring 443, a prelubricated bearing 455, a needle bearing 453, a sensor actuator 446, an external retaining ring 450, the first gear 414, the pivotable arm 422, the linear actuator 430, the first spindle 432, a second spindle 434, and the base plate 412. In some embodiments, the wire feed apparatus 410 also includes a spacer 438. As a groove 460 wears out, the spacer 438 may be inserted between the wheel 416, 420 and the gear 414, 418. For example, if the wheel 416, 420 has two grooves 460 and the first groove wears out, the spacer may be inserted to select the second groove. The connecting arm 424 connects the first spindle 432 to the second spindle 434 thereby providing additional stability. [000160] In the depicted embodiment, the linear actuator 430 includes a front mounting swivel flange 447, tubing 448 connected to the fittings 428, and a rod clevis 449. The front mounting swivel 447 is used to mount the linear actuator 430. The tubing 448 is used to supply fluid, compressed air for example, to the linear actuator 430. The rod clevis 449 is adapted to receive the pivotable arm 422. [000161] The first and second spindles 432, 434 are mounted to the base plate 412. Bearings 441 are mounted on the second spindle 434, and the second gear 418 mounts on the bearings 441. The prelubricated bearing 455 mounts on the first spindle 432, and the eccentric 436 mounts onto the prelubricated bearing 455. In the depicted embodiment, the hole 437 of the eccentric 436 receives the prelubricated bearing 455. The prelubricated bearing 455 mounts onto the first spindle 432, and the eccentric 436 pivots about the first spindle 432. [000162] The first gear 414 is mounted on the eccentric 436. As such, when the eccentric 36 is rotated or pivoted about the first spindle 432, the first gear 414 travels an arcuate path. As assembled, when the eccentric 436 is pivoted about the first spindle 432, the first gear 414 pivots toward or away from the second gear 418. As such, there is a clearance between the first feed wheel 416 and the second feed wheel 420 when the first gear 414 is moved away from the second gear 418. In the depicted embodiment, there is a clearance of 0.140 inches (3.6 mm). The clearance is sufficient to prevent the frictional driving of any wire between the channels 460 of wheels 416, 420. [000163] Referring now to figure 40, and as an example only, the wire feeding apparatus may be used with the baling machine 10. The baling machine 10 includes, among other things, the carriage unit 40. In the depicted embodiment, the carriage unit 40 includes a servo motor 512, a gear box 514, and a plurality of wire feeding apparatus 600. [000164] Figure 41 illustrates a more detailed view of the carriage unit 40. In figure 41, the gear box is omitted for clarity. The carriage unit 40 includes the wire feeding apparatus 600. In the depicted embodiment, there are three wire feeding apparatuses 600. Those skilled in the art will understand that a greater or lesser number of wire feeding apparatus 600 may be used. For example, there may be as few as one feeding apparatus 600 and as many as eight wire feeding apparatuses 600. Each wire feeding apparatus 600 includes a linear actuator 630. The carriage unit 40 also includes the servo motor 512 and a drive shaft 516. [000165] Figure 42 illustrates the servo motor 512, the gear box 514, and the drive shaft 516. The drive shaft 516 includes spur gears 520 and mounting flanges 518. The mounting flanges 518 support and locate the drive shaft 516. Each spur gear 520 mates with a corresponding second gear 618 (best seen in figure 41) and is sized accordingly. In the depicted embodiment, the spur gears 520 each have 24 teeth. The ratio between the second gears 618 and the spur gears 520 is from about 1:1 to about 2:1. In the depicted embodiment, the second gears 618 and the spur gears 520 have a ratio of 1.75:1. A first mounting sleeve 524 is used to mount the motor 512 to the gear box 514. A second mounting sleeve 522 is used to mount the gear box 514 to the carriage unit 40. The gearbox 514 is a gear reducer with a gear ratio in the range of about 5 : 1 to about 7: 1. In the depicted embodiment, the gear box 514 has a gear ratio of 5.955:1. [000166] A control system 470 is illustrated in figure 43. The control system 470 includes a control module 472. Components for appropriate control systems 470 are described in U.S. Patent No. 6,633,798 issued to Stamps et al. on Sept. 30, 2003. They may include, for example, Programmable Logic Controllers (PLCs). The control module 472 is operatively connected to linear actuators 630a, 630b, 630c, and to the servo motor 512. The control module 472 and the linear actuators 630 may be electrically connected such that electrical signals from the control module 472 actuate and de-actuate actuators 630. The control module 472 may receive input directly from an operator or instructions from another machine. The control module 472 selectively engages the linear actuators 630 and the servo motor 412. In one example, the control module 472 engages all three linear actuators 630a, 630b, 630c and subsequently engages the servo motor 512. In another example, the control module 472 engages only one of the linear actuators, such as 630b, and subsequently engages the servo motor 512. In yet another example, the control module 472 engages two of the linear actuators, such as 630a and 630c, and subsequently engages the servo motor 512. In this manner, the wire feeding apparatus 600 can be selectively engaged. For example, if a wire mis-feeds in a particular track, the particular wire feeding apparatus 600 can be singularly engaged to re-feed the wire. [000167] Figure 44 and 45 illustrate operation of the linear solenoid 630. In figure 44, the first gear 614 is shown in a first position away from the second gear 618. In the first position, the wire is not fed because there is a clearance between the first gear 614 and the second gear 618. In figure 45 however, the linear actuator 630 has moved the first gear 614 to a second position. In this second position, there is very little clearance between the first feeding wheel and the second feeding wheel. As such, the feeding wheels frictionally engage the wire and feed it around the bale. [000168] In figure 44, the drive shaft 610 is rotating which in turns rotates the second gear 618. However, because there is a clearance between the first gear 614 and second gear 618, the first gear 614 does not rotate. [000169] In the engaged, driving, second position shown in figure 45, the drive shaft 610 rotates, which in turn rotates the second gear 618. Because the first gear 614 is now in contact with the second gear 618, it also rotates. The two gears 614, 618 rotate in opposite directions and pull or push the wire depending upon the rotational direction of the servo motor 512. The drive shaft 610 can be rotated in either direction. As such, the wire can be moved in either direction. This is significant because in the baler 10, wire must first be fed around the bale, but it must then be reversed and pulled back to tension the wire out of its guide tracks and then draw the wire taut against the bale. [000170] A method of assembling a wire feeding apparatus is provided. The method includes the steps of: providing a feed module base plate; connecting a first spindle to the base plate; connecting a second spindle to the base plate; mounting an eccentric on the first spindle; connecting a first gear to the eccentric; connecting a first feed wheel to the first gear; mounting a second gear on the second spindle; connecting a second feed wheel to the second gear; and connecting a pivotable arm to the eccentric. The method further includes the step of connecting an actuator to said pivotable arm. The actuator is deployed to mediate the travel of one of the wheels to and from an engaged position that feeds wire. [000171] There is also provided a method of controlling a wire feeding apparatus. The method includes the steps of: providing a fixed gear connected to a first feed wheel and a pivotable gear connected to a second feed wheel, the pivotable gear mounted for movement toward and away from the fixed gear; providing a pivot arm connected to the pivotable gear and a linear actuator connected to the pivot arm; engaging the linear actuator; moving the pivotable gear toward the fixed gear; frictionally engaging a wire with the first feed wheel and the second feed wheel; engaging a servo motor; and rotating a drive shaft connected to the fixed gear. In some embodiments, the method further includes the step of selecting at least one other linear actuator for engagement. [000172] The down press 10 includes one or more lower guide track sections. It would be beneficial to have guide track dimensions designed to accommodate the preexisting dimensions of down packer beds, while maintaining an optimal turning radius for guiding ten gauge wire without jamming. [000173] Figure 46 illustrates the down press 10. As noted above, the down press 10 includes the base 2, the bed 4, the baling side 6, the box loading side 8, the compression box 12, the central column 14, the end column 16, the central piston 18, the lower platens 20, 20', the upper platen 22, the baling station 24, the driver carriage 40, the return carriage 42, the rails 43, 44, the wire drivers 46, the knotters 48, and the upper guide track portions 60,90. [000174] Figure 47 illustrates a sectional side view of the down press 10. Numerous components have been omitted for clarity. A lower guide track section 700 is dimensioned for deployment within a platen slot 722 of the lower platen 20. The lower guide track 700 is comprised of a platen section 702, a first extension 704 and a second extension 706. The first extension 704 has a strap receiving end face 708. The second extension 706 has a strap exit end face 710. In the depicted embodiment, an uppermost extent of the receiving end 708 and the exit end 710 of the lower guide track 700 is substantially coextensive with a lower platen bed 4 in its upper extent. That is, the uppermost extent of the lower guide track 700 is substantially at the same vertical level as the uppermost portion of the lower platen bed 4. In the depicted embodiment, this is slightly higher than the top face 726 of the lower platen 720. An upper extent of the first and second extensions that is substantially that is equal to height of the upper surface 726 of the lower platen 720 is also within the scope of the present invention. [000175] In the depicted embodiment, the receiving end face 708 and the exit end face 710 are substantially horizontal. Thus, the combination of lower platen 720, lower platen bed 4 and the lower guide track 700 present a single horizontal plane over which an exit end of a first carriage guide track section 730 and a receiving end of a second carriage guide track section 732 may translate laterally without interfering with either the platen bed 4 or any other components of the down press. Each of said first carriage guide track section 730 and said second carriage guide track section 732 has an end face, 731 and 733 respectively. The first carriage guide track section end face 731 and the receiving carriage guide track section end face 733 are also substantially horizontal. Thus, when the first and second carriages are indexed into an engaged position, the exit end face 731 of the first carriage guide track section closely cooperates with the receiving end face 708 of the lower guide track 700 and, similarly, the exit end face 710 of the lower guide track closely cooperates with the receiving end face 733 of the second carriage guide track section 732. [000176] The extensions 704 and 706 allow the vertical guide track sections 730 and 732 to be dimensioned to avoid an end column of the press when their carriages are withdrawn. That is, the extensions 704 and 706 are long enough for the vertical tracks 730 and 732 to be short enough to be laterally withdrawn without hitting the down press end column. [000177] The first extension receiving face 708 and the second extension exit face 710 of the lower guide track 702 each have a medial border 740, 742 respectively and a peripheral border 744, 746 respectively. In the depicted embodiment, the medial borders 740, 742 are dimensioned such that they are outside a clearance length. [000178] The exit face 731 of the first carriage guide track section 730 and the receiving face 733 of the second carriage guide track section 732 each also comprise a medial border 734, 736 respectively, and a peripheral border 748, 750 respectively (see Figure 52). The medial border 734 of the first carriage guide track section 730 is outside a clearance dimension, as is the medial border 736 of the receiving face 733 of the second carriage guide track section 732. The clearance length is dimensioned such that it is at least as long as the down press end column is wide. That is, the clearance length is dimensioned such that upon a lateral withdrawal of the carriages past the end column, any component outside the clearance length will not touch the end column of the down press. [000179] The lower guide track 700 is also dimensioned such that it may be manually inserted and withdrawn in sliding engagement with the lower platen slot 722 when the carriages are laterally withdrawn, for maintenance or repair. [000180] Also depicted in Figure 47 is an indication of one outer edge of the 21 of the lower platen 20, and a demarcation 716 of the outer edge of the end column 16. The later outer edge dimension 716 of the end column defines a minimum clearance length. [000181] Figure 48 illustrates the lower guide track section 700 located in the lower platen slot 722. In the embodiment depicted in Figure 48, there are six lower platen slots and six lower guide track sections. [000182] Figure 49 illustrates the lower platen slot 722 of the lower platen 20. In the depicted embodiment, the lower guide track section 700 has been omitted for clarity. [000183] Figure 50 illustrates the relationship between the lower guide track sections 700 and the guide track sections 60, 90 when the guide track sections are in the engaged position. [000184] Figure 51 illustrates the lower platen 20. In the depicted embodiment, the lower platen 20 has six lower platen slots 722 and six lower guide track sections 700. As described above, each lower guide track section 700 includes the platen section 702, the first extension 704 and the second extension 706. [000185] Figure 52 depicts a side view of the lower guide track section 700, first carriage guide track section 730 and return guide track carriage section 732. On the first extension 704, the first extension receiving face 708 is depicted. The first extension receiving face lies between a first extension receiving face medial border 740 and a first extension receiving face peripheral border 744. The second extension 706 includes exit face 710, which lies between the exit face medial border 742 and the exit face peripheral border 746. The first carriage guide track section exit face 731 lies between its medial border 734 and its peripheral border 748. The second carriage vertical guide track section receiving face 733 lies between its medial border 736 and peripheral border 750. [000186] Also depicted in figure 52 are the dimensions of the turning radius within each guide track portion. These radii include an effective radius 760 and 760'. The effective radius is comprised of an upper radius 762 and 762' and a lower radius 764 and 764'. Between these is an area of relative flattening. [000187] Figure 52 designates a position at which a turning radius of the guide tracks begins, at 770. This turning radius begins inside the outer edge 21 of the platen 20. [000188] Figure 52 depicts at least three novel elements that are combined in order to address the problem of retaining the lower guide track within the preconfigured bed dimensions, maintaining a knotter stand off dimension that is adequately close to the side of the bale, and turning the bale wire through a sufficiently gradual arc to prevent jamming. These elements include beginning the turning radius at a point inside outer edge 21. Thus the baling wire has begun its upwards turn even while it continues to progress horizontally underneath the bale. Next, the channel turn is executed incrementally, with a lower radius 764 and an upper radius 762, separated by an area of relative flattening. The intermediate area may be literally flat for some distance, or may simply be an arc that is broader, that is having a greater turning radius, than the effective radius 760. Thus, the channel within the guide track is dimensioned to make a first incremental turn, allow the wire to travel a distance with little or no turning, and then make a second incremental turn. In the depicted embodiment, each of the upper radius 762, 762' and lower radius 764, 764' is in the range of 35 to 40 degrees. These angles incorporate critical values found to dramatically reduce the incidence of jamming. [000189] A final element in accommodating minimum turning radius of the wire in combination with the preconfigured bed dimensions and the necessary stand off dimension is to finish the turn of the guide wire with the channel inside the first carriage guide track section 730. Whereas prior art taught that a first carriage guide track section would incorporate a complete 90 degree turn and have a substantially vertical exit face 708, in the present invention the exit face relative to the channel passing through it is not perpendicular. [000190] Although the components above have been described in conjunction with a "down press," many of the components may also be used with an "up press." [000191] Figures 53 and 54 depict a prior art "up press" bale binder apparatus. A bale forming and binding apparatus 810 has two positions: the solid lines illustrate a first position wherein the moveable wire guide section 848 completes the wire guide track trajectory as when the binding operation is occurring; and the broken lines illustrate a second position wherein the moveable wire guide section 848 is in a position 848a. A floor plate 812 supports vertical support stands 814 on either side of the bale forming and binding station 816. A binding assembly carriage 818 is borne by stands 814. The base extension 820 of the carriage 818 carries the fixed tying heads 840 and attached wire guide track sections 839. The carriage 818 translates in a direction perpendicular to the plane of the drawing along an overhead track 822 attached to the upper rear extent of the stands 814 and its motion is controlled by drive 824. [000192] Extending from the upper forward extent of the stands 814 are a pair of pivot axis brackets 825 holding the pivot axis 826 which carries the moveable guide track support strut assembly 828. Extending forward from the center of the strut assembly 828 is a member 830 pivotally connected at pin 832 to the piston arm 834 which is extended and withdrawn by action of the piston 836. The action of the piston 836 may be by any means but is preferably pneumatic. [000193] The binding wire entering the apparatus 810 from the wire supply (not shown) at the wire control head 841 are directed by guide track sections 838 to and from the tying head 840 which fastens the wire into a closed loop. The guide track section 844 lies in a channel within the bale forming compressor 842 which accommodates the wire trajectory above the bale forming station 846 containing the bulk material (not depicted). The positions 828a, 834a, 836a and 848a show the parts 828, 834, 836 and 848 in their respective positions when the apparatus is in the arrangement whereby the moveable guide track section is at a remove from the bale forming station 846. The upper moveable guide track section terminus 850 and the lower moveable guide track section terminus 852 meet the guide track sections 844 and 838 respectively to complete the wire guide track. The dashed line 854 illustrates the path of motion of the lower terminus 852 as it transits between positions. [000194] As evident by dash line 854, an insertion portion of guide track 848, including guide track end 852 describe an arc of travel that extends substantially lower than the final insertion position of the guide track in the lower platen. The insertion level of the lower guide track, IL is a level at which it engages the stationary portion of the guide track 838 and completes a guide track loop around the baling station. This arc of travel 854 requires a dimension D, which must be clear of obstructions so that the guide track 852 can transverse it. In order to achieve this, the prior art bale binder depicted in figure 53 required a lower platen that was increased in height by at least dimension D. [000195] Figures 55, 56, 57, 58, 59 and 60 depict the shortened platen compatible lower guide track insertion and removal assembly of the present invention in six different positions along its arc of travel. The assembly is in operative engagement with an otherwise standard bulk material bale binder for an up press. Depicted in Figures 55- 57 are binder stand 916 and baling station 946. [000196] Also shown is a moveable guide track section 948, which includes an insertion portion 950. In the depicted embodiment, the removable guide track section 948 and the insertion portion 950 do not move relative to one another. The removable guide track section 948 is attached to guide track mount 960. In the depicted embodiment, the removable guide track section 948 and insertion portion 950 do not move relative to the guide track mount 960. Guide track mount 960 is pivotably attached at pivot axle 962 to the guide track removal and insertion frame 928. As the apparatus moves through its arc of travel, the removable guide track section 948 and its mount 960 move relative to the guide track removal frame 928 by rotating around pivot 962. [000197] As in the prior art, guide track removal frame 928 is moved into and out of its engaged position by a piston and cylinder assembly 936, which may be hydraulic or pneumatic mechanical or electromechanical (omitted from Figures 55-57 for clarity). The removal frame may be pivotably connected with the cylinder and the stand with the piston, or visa versa. [000198] The movement of the guide track removal frame 928 is around pivot 926, by which it is mounted on a bracket extension 925 fixedly attached to stand 916. When a bale has been bound and is ready for ejection, piston and cylinder assembly 936 swings the removal frame 928 around pivot 926 up and away from the baling station 946. Thereafter the bound bale is ejected and more bulk material is installed in the compression pit, the compressor raises the lower platen, compressing the material in the baling station 946, and the guide track removal frame 928 is rotated back down in order to engage removable guide track section 948 with the fixed guide track portions so that the bale binder apparatus is again ready for binding the next bale. [000199] The depicted embodiment of the present invention maintains the insertion portion 950 of the removable guide track section 948 at or above an insertion level IL. The insertion level, of course, corresponds to a platen slot dimensioned to receive the insertion portion 950 of the removable guide track section 948. Figure 55 depicts the removable guide track section 948 fully lowered and folly engaged with the rest of the bale binding apparatus for binding. Figure 56 depicts the removable guide track frame and removable guide track 946 and removable guide track 948 at a first intermediate position through which the apparatus will move during removal from the baling station. Figures 57, 58 and 59 depict the apparatus at intermediate positions and Figure 60 at a folly removed position. In Figure 55, the insertion portion 950 is at an angle with the removal frame 928, that in the depicted embodiment, is substantially perpendicular. As the removal frame rotates to moves the guide track section 948 from its engaged position to its removed position, the insertion portion 950 changes its angle relative to the removal frame 928. The angle ANG changes from the substantially perpendicular insertion angle to a more acute angle. As is apparent in Figures 55-57, the insertion portion 950 of the removable guide track section 948 is maintained at or above the insertion level IL at all times. This achieved with linkage 970. [000200] Linkage 970 includes a first tie rod 974 having a first end pivotably attached to the stand. In the depicted embodiment, the pivotable attachment 972 of the first end of tie rod 974 is on the bracket extension 925. It is within the scope of the present invention that tie rod 974 may be attached to any portion of the stand 916 or its fixed attachments, provided that the fixation point does not move with the guide track removal frame 928. The second end of tie rod 974 is attached to a first swing arm 980. This attachment of the second end of tie rod 974 is at a pivot point 976. Swing arm 980 is attached to guide track removal frame 928 at a swing arm pivot point 978. [000201] As guide track removal frame 928 swings up and away from the baling station 946, a distance between first tie rod pivot 972 and a closed position of second tie rod pivot point 976 is biased to increase. The tie rod, being rigid, exerts tension on swing arm 980. Because swing arm 980 is pivotably mounted at pivot 978 to the guide track removal frame 928, it rotates in response to the exerted traction of tie rod 974. In the depicted embodiment, the rotation is clockwise. The clockwise rotation during removal of guide track removal frame 928 pushes a compressive force on a second tie rod 984 (see Figure 59). The second tie rod 984 is attached to the first swing arm 980 at the pivot point 982. [000202] A second end of second tie rod 984 is pivotably attached at pivot 986 to a bottom area of the guide track mount 960 at bracket 990. The second tie rod pushes guide track mount 960 to rotate around guide track mount pivot point 962. The compressive force exerted on second tie rod 984 is received by bracket 990 which is attached to guide track mount 960. This correspondingly rotates the guide track mount 960 and removable guide track section 948, also in a clockwise direction, relative to guide track removal frame 928 as it swings up and away from the baling station 946. [000203] For reinsertion of the removable guide track section 948, piston and cylinder assembly 936 lowers the guide removal frame 928, and the linkage 970 rotates the guide track mount 960 and removable guide section 948 in the opposite direction, that is counter clockwise in the depicted embodiment. [000204] Figure 61 is a front view of the entire removal frame. It can be seen that the top or first tie bar 974 has a bend in it formed by two complementary angles of approximately 30 degrees. For baling standard bales of cotton according to the standards of the International Cotton Council, six bale wires are used. Accordingly six guide track sections 948 are mounted on the removal frame 928. Because these six frames guide track sections 948 are mounted, the guide track section mount 960 is configured as a rectangle to accommodate the dimensions of the guide track sections 948. The use of the guide track mount 960 saves material cost and improves durability by over individual pivotable mounting of each individual guide track section 948. [000205] As can be seen, the guide track mount 960 is pivotably mounted at spanner 962. A close up front view of this connection is seen at Figure 63. There can be seen that the guide track mount 960 is pivotably mounted to the removal frame 928 at pivoting joint 990 so that the removal frame 960 can rotate around a bar, which in the depicted embodiment is a approximately two inch diameter pipe welded onto the removal frame 928. Also seen in Figure 63 is a close up of the pivoting joint 962 whereby the second tie rod 984 exerts pressure in a levered relation to the pivot 990 of the guide track section frame 960. That is to say, the pivoting joint 962 is sufficiently offset from the axis of rotation 990 of the guide track mount 960 to obtain a mechanical advantage thereover and cause the mount to rotate around axis 990 when the frame 928 is raised. Thus, the guide track sections 948 and insertion portions 950 mounted to guide track mount 960 will move from their insertion angle through increasingly more acute angles as the guide track mount 960 pivots when the removal frame 928 is raised. [000206] Figures 62 and 64 are close-ups, a side view and front view respectively, of the swing arm 980. As can be seen, the joint 978 in the depicted embodiment is constructed by welding a cup 979 into the side of the side portion of the removal frame 928 and installing therein a semi-spherical bearing, which allows the swing arm 980 to rotate around the axis 978. As best seen on Figure 63, the first tie rod 974 is pivotably mounted at 976 to a first portion of the swing arm 980. When the removal frame 928 is raised, tie rod 974 will exert a tractive force, that is, it will pull swing arm 980 at a direction that is clockwise in the depicted embodiment and centered around axis 978. A second portion of the swing arm 980 serves as a mount for pivot point 982, to which a first end of a second tie rod 984 is pivotably mounted. As the swing arm 980 rotates clockwise, it will exert a compressive force on tie rod 984. As has been seen in Figures 61 and 63, it is this pushing or compressive force on tie rod 984 against this pivotable mount 962 of the second end of the second tie rod 984 that completes the linkage and pivots guide track mount 960. [000207] Figure 65 illustrates the binder stand 916, baling station 946, the removal frame 928, the swing arm 980, tie rods 974, 984, and the axis 990. [000208] In operation, a bale is bound, and binding wires knotted and the bale completed. Before compression can be released, the guide track must be removed from the lower platen slots. Accordingly, the removal frame 928 is rotated upwards by the piston and cylinder assembly 936. Removal frame 928 rotates around axis 926. Because this axis is offset from a pivot point 972 of first tie rod 974, the linkage 970 has an actuating force applied to it simply by virtue of the fact that the removal frame is being raised. As has been seen, the first tie rod 974 rotates the swing arm 980 in a clockwise direction, which causes the second tie rod 984 to push downwards and outwards, which, by virtue of its levered interaction with guide track mount 960 and its pivotable mounting at axis 990, causes the guide track mount 960 to rotate, carrying with it the guide track sections 948 and turning the insertion portions 950 thereof through increasingly acute angles as the frame is raised. [000209] As displayed in Figures 56 - 58, the simultaneous rotation of the insertion portion 950 through its increasingly acute angles relative to the perpendicular insertion angle, occurs simultaneously with the rotation upwards of the removal frame 928. In this manner, a lower reach is established at the insertion level and maintained above it. That is, the insertion is level is the lowest point of the travel arc of the insertion portion 950 of the removable guide track sections 948. Accordingly, shorter slots and therefore shorter lower platen following blocks may be used, saving material cost. Prior art platens and/or the following blocks that support them were over 12" high — 13 5/8" in the most common models. This was to accommodate dimension D, representing wasted spaced below IL. In the embodiments depicted herein, dimension D is substantially about 5-6" high, 5 1A" as shown. Accordingly, the present invention saves 5 to 6" of wasted height and corresponding material cost. It allows use of a platen/follower block assembly that is substantially 9" or less in height. [000210] After the removal frame 928 has reached a level sufficient for clearance, a finished bale is ejected. Thereafter, a new volume of bulk material is compressed into the baling station 924 and held there. Next, the removal frame 928 is rotated clockwise and downwards to reinsert the removal guide track sections 948 into their operative position, which closely cooperates with other guide track sections in a known manner. The linkage works in an opposite manner, and may be assisted by gravity, such that swing arm 980 rotates in a counterclockwise direction, the insertion portions 950 also rotate in a counterclockwise direction until they rotate once again into a substantially perpendicular angle to the removal frame 928 as they are inserted into the slots dimensioned to receive them in the following block of the lower platen. Once again, the insertion level is the lowest level of the arc of travel of the insertion portions 950 of the removal guide track sections 948 as they are inserted. [000211] In view of the foregoing, it will be seen that the several advantages of the invention are achieved and attained. [000212] The embodiments were chosen and described in order to best explain the principles of the invention and its practical application to thereby enable others skilled in the art to best utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated. [000213] As various modifications could be made in the constructions and methods herein described and illustrated without departing from the scope of the invention, it is intended that all matter contained in the foregoing description or shown in the accompanying drawings shall be interpreted as illustrative rather than limiting. Thus, the breadth and scope of the present invention should not be limited by any of the above- described exemplary embodiments, but should be defined only in accordance with the following claims appended hereto and their equivalents.