METHOD AND APPARATUS FOR CONTINUOUSLY CASTING METAL

Abstract: The present invention provides novel methods and apparatus for continuously casting molten metal in a block caster. In accordance with the present invention, novel track (705) and drive systems (505, 510) are provided for reducing imperfections that can be created in a cast by movement of a beam chain (390) through a casting cycle.

Description: METHOD AND APPARATUS FOR CONTINUOUSLY CASTING METAL FIELD OF THE INVENTION The present invention relates to a method and apparatus for continuously casting metal. In particular, the present invention relates to a method and apparatus for continuously casting molten metal into strips, sheets and slabs using improved track and drive systems in a block caster. BACKGROUND OF THE INVENTION There are a number of known methods and apparatus for continuously casting metal into strips, sheets and slabs. The term "metal" as used herein, refers to any type of castable metal, including, but not limited to, aluminum, steel, iron, copper, zinc, nickel, titanium, magnesium, manganese and their alloys. In a typical continuous casting process, molten metal is supplied from a tundish to a system of rollers, belts or chains which define a continuously moving mold. Block casters are particularly useful in continuously casting metal because they can provide a wide range of solidification rates, which allows a wide range of control over the physical properties of the metal being cast. A typical block caster includes two synchronized, counter-rotating chains containing chilling blocks which travel through casting loops. The casting loops are disposed in close relation to one another such that the counter-rotating chains can be forced together to define a flat plane, continuously moving mold assembly for receiving molten metal. As the molten metal is poured from a tundish and contacts the surfaces of the mold, heat transfer between the molten metal and the mold surfaces causes the molten metal to solidify. The counter-rotating beam chains in a block caster travel in a track which defines the shape of the casting loops. Typically, the casting loops are oval in shape, containing two substantially linear sections and two non- linear bends, however, other shapes have been employed. Generally, in one linear section of the casting loop, the chilling blocks are cooled and in the other linear section the chilling blocks define a casting region. The chain can be driven around the track through the use of a drive system, which typically is a system of gears or sprockets in mesh with the chain. In known block casters, the chain is comprised of a number of chilling blocks, which are affixed to support beams. The chilling blocks define the continuously moving mold and are in direct contact with the molten metal. The support beams are typically used to interlink the chilling blocks together to form an endless "beam" chain and can contain features for meshing with the track and drive systems. The chilling blocks themselves are typically not interlinked or in mesh with the track and drive systems because the chilling blocks experience thermal and physical deformations during casting which could adversely affect the operation of the caster. Thus, it is desirable that the chilling blocks be at least partially thermally isolated from the support beams. For example, U.S. Patent No. 3,570,586 by Lauener, assigned to Lauener Engineering Ltd., generally describes a block caster with chilling blocks thermally isolated from support beams, which travel through a casting loop along a guideway. It is desirable in a continuous block caster to provide a substantially smooth, planar mold surface for casting metal sheets, strips or slabs. The amount by which of the mold surface approximates a smooth plane can have a direct impact on the surface quality and the microstructure of the cast. For example, changes in block height or block surface angle can create surface imperfections in the cast or can create insulating gas pockets between the block surface and the molten metal affecting the solidification rate of the metal and thus the microstructure of the cast. U.S. Patent No. 5,133,401 by Cisko et al., assigned to the Aluminum Company of America, discloses a block casting apparatus purportedly for solving the problem of poor surface accuracy of a cast slab. The disclosed apparatus utilizes a chilling block and support beam structure. The support beams contain inboard and outboard or "offset" rollers for carrying the beam chain along horizontal upper and lower guide tracks. The support beams are interconnected using elastic hinges to form an endless beam chain. The beam chain is driven around the guide tracks using an opposed-torque gearing system in mesh with gear racks which are located on the bottom surfaces of the support beams. Known casting systems, however, such as that disclosed in by Cisko et al., allow individual chilling blocks to tilt around an axis (the "y-axis") transverse to the casting direction, negatively impacting the amount the mold surface approximates a smooth plane. The meshing of the gear rack system disclosed by Cisko et al. can be dependent upon manufacturing tolerances. Moreover, the offset roller system requires precise manufacturing tolerances of the rollers and the guide track to prevent binding or excess movement of the rollers in the track. It is also generally desirable that a block caster contain features which accommodate the differences in track length and beam chain length. Differences in beam chain length and track length can occur when fitting beams in a chain and also during casting as a result of thermal effects upon the beam chain or the track. If these differences are not compensated-for, the blocks can move relative to one another in the casting region, reducing the quality of the cast through "banging," i.e., unnecessary contact between adjacent blocks, or by allowing molten metal to seep between chilling blocks causing damage to the caster and the chilling blocks. Damage to the caster and the chilling blocks causes lost production due to down-time required to repair the caster and/or to replace damaged chilling blocks. In known block casters, such as that described in the •401 patent by Cisko, et al., elastic hinges have been used for interlinking the support beams to accommodate differences in beam chain and guide track lengths. The use of elastic hinges in the beam chain and an opposed-torque gear drive system, however, can cause problems in meshing the gear drive system with the gear racks on the support beams. Elastic hinge systems are designed to allow adjacent blocks to exert pressure upon one another in the casting region to prevent gaps between chilling blocks from forming. The use of an elastic beam chain alone, however does not compensate for reductions in the quality of the cast due to banging between blocks. It is further desirable that a block caster be designed to substantially reduce imperfections in the cast and damage caused to chilling blocks caused by mechanical forces such as vibrations and the like propagated by blocks traveling along a track. Moreover, it is desirable to substantially reduce any additional forces or effects created by blocks traveling through a casting cycle which can negatively impact the quality of the cast. The '401 patent by Cisko et al., previously described herein, also discloses the use of tracks which are asymmetrical about a plane parallel to a lateral plane through the mold cavity. Cisko et al. disclose that each bend in their elongated oval track consists of two smoothly joined quadrants each having a different radius and center. and that typically no two of the four radii of the four quadrants are the same. The asymmetrical track design disclosed in the '401 patent by Cisko et al. purportedly minimized the "mechanical noise" generated by the "mechanical excitation" of the chilling blocks banging against each other in the bends of the track as can occur when using an elastic beam chain. The asymmetrical tracks are an attempt to reduce the net effects of mechanical excitation in the bends by maintaining the inputs from positive and negative block acceleration out of phase. The asymmetrical track design for dampening mechanical excitation described by Cisko et al., however, does not substantially compensate for other forces or effects which can negatively impact the quality of the cast which are propagated by chilling blocks traveling through a casting cycle. SUMMARY OF THE INVENTION In accordance with the present invention, methods and apparatus are provided for continuously casting metal sheets, strips or slabs in a block caster which provide for a substantially planar mold surface. The present invention provides methods and apparatus for compensating for differences in beam chain length and track length in a block caster. The present invention provides methods and apparatus for reducing damage to chilling blocks in a block caster, and for reducing damage to the caster itself. The present invention provides methods and apparatus for substantially reducing vibrations and the like generated by chilling blocks traveling through a casting cycle, and for substantially reducing other undesirable forces and/or effects propagated by the beam chain traveling through a casting cycle which negatively impact the quality of the cast. In accordance with the present invention, novel track and drive apparatus are provided, including prestressed beam chains, tracks, roll supports, and caster drives. In accordance with the present invention, pre-stressed beam chains are provided which comprise a plurality of interlinked support beams held together, for example, by a tensioning device. In accordance with the present invention, tracks are provided which contain both fixed portions of track and movable track segments for compensating for changes or differences in beam chain and track lengths. In combination with the pre-stressed beam chains of the present invention, such tracks also assist in reducing unnecessary contact between adjacent blocks as they travel through a casting cycle. In accordance with the present invention, roll supports are provided which contain main rollers and counter-rollers for traveling on a track having two opposed surfaces. Such roll supports also contain features for meshing with the caster drives of the present invention. In accordance with the present invention, caster drives are provided which include, for example, the use of wor gears and synchronization systems for moving beam chains along the caster tracks. In accordance with the present invention, apparatus are provided which reduce the rotational forces created by the beam chain as it travels through a casting cycle, such as through modification of the numbers of blocks or beams in a beam chain and the number of blocks or beams in the bends of a track. In accordance with the present invention, methods and apparatus are provided for reducing speed variations in roller speed as beams in a beam chain travel along a track. For example, through the use of compensating curves placed in the track, speed variations in roller speed can be reduced as the rollers travel from linear sections of a track to the non-linear sections of the track. In accordance with the present invention, methods are provided for casting metal using the apparatus of the present invention. For example, methods are provided for detecting problems in the caster through monitoring the movement of the movable segment in the tracks of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 illustrates one embodiment of the tensioning unit of the present invention and one embodiment of the roll support of the present invention viewed in a direction normal (the "z-direction") to the casting surface of a block. Figure 2 illustrates another, close-up view of the embodiment of the tensioning unit of the present invention shown in Figure 1. Figure 3 illustrates one embodiment of the tensioning unit, one embodiment of the compression unit, one embodiment of the track and one embodiment of the roll support of the present invention viewed in the casting direction (the "x-direction") . Figure 4 illustrates one embodiment of the track and one embodiment of the roll support of the present invention viewed in a direction transverse (the "y-direction") to the casting direction. Figure 5 is a view, in the z-direction, of one embodiment of one beam chain having portions of support beams cut away to view one embodiment of a drive system of the present invention. Figure 6 illustrates one embodiment viewed in the y- direction of a moveable track segment of the present invention. Figure 7 is a cut-away view of one embodiment of the moveable track segment of the present invention shown in Figure 6. Figure 8 illustrates one embodiment of the moveable track segment of the present invention shown in Figures 6 and 7, showing how the track can be expanded or contracted without affecting the ability of the beam chain to travel along the track. Figure 9 is a diagram of acceleration forces propagated in a known block caster by a beam chain as a result of the polygon effect. Figure 10 illustrates a pivot point travel path used in determining one embodiment of the polygon effect compensation curves of the present invention. Figure 11 illustrates one embodiment of the polygon effect compensation curves of the present invention and the effect using such curves has on polygon effect forces. Figure 12 illustrates a known track profile which does not compensate for rotational forces generated by blocks. Figure 13 illustrates one embodiment of a track profile of the present invention which partially compensates for rotational forces generated by blocks. Figure 14 illustrates another embodiment of a track profile of the present invention which partially compensates for rotational forces generated by blocks. Figure 15 is an illustration of yet another embodiment of the present invention which compensates for rotational forces generated by blocks. DETAILED DESCRIPTION The quality of a cast can be limited by the imperfections created in the cast by the casting process. The quality of the exterior surface of a cast can be enhanced by, for example, increasing the flatness of the mold surface so that it approximates a smooth plane, maintaining substantially constant speed of the beam chain in the casting cycle, substantially synchronizing the two counter-rotating beam chains, and reducing undesirable forces propagated by the blocks and beam chain as they travel through the casting cycle. The present invention relates to novel methods and apparatus for continuously casting molten metal in a block caster which provide for enhanced cast quality through the use of improved track and drive systems. The apparatus of the present invention provides enhanced cast quality by providing a substantially planar mold surface for solidifying the molten metal. In particular, the present invention provides apparatus which reduce the tilting of blocks in a beam chain along an axis (the "y-axis") transverse to the casting direction as the blocks travel through a casting cycle. A reduction in block tilting can be achieved through the use of the novel beam chains, roll supports, drive meshing systems and track designs of the present invention. In one embodiment of the present invention, the track and drive systems of the block caster utilize an endless, pre-stressed beam chain having fixed pitches. As used herein, the term "pitch" refers to the length of the segments of the beam chain between pivot points in the beam chain, i.e., the points where support beams in the beam chain are pivotally interlinked. The pre-stressed beam chain can also include chilling blocks mounted to the interconnected support beams. The term "block" as used herein, refers to a chilling block itself or a chilling block which has been attached to one or more block holding plates. For stressing the beam chain, the support beams can be interlinked using a tensioning unit, including for example, hydraulic or pneumatic cylinders, bands or springs. One advantage of pre-stressing the beam chain in the present invention is to prevent the individual blocks from separating from one another as they travel through the casting region. Separation of blocks in the casting region allows the blocks space in which to tilt and can allow molten metal to seep between chilling blocks, causing to damage the caster or the beam chain. In general, the pre- stressed beam chains of the present invention will only allow separation of the blocks and beams to occur during casting as a safety feature in an emergency situation. The differences in beam chain length and track length such as can occur during casting can be accommodated by changing the track length rather than the length of the pre-stressed beam chain. Also, the pre-stressed beam chains of the present invention do not, in general, rely upon the caster drive system to compress the blocks in the casting region to eliminate gaps between adjacent blocks. In one embodiment of the present invention, the tensioning unit which interlinks the support beams in a beam chain can be a spring-loaded device comprising a spring, such as a plate or coiled spring, disposed around a bolt connecting two adjacent support beams. For example, a bolt having a spring coiled around its length can be pivotally attached on one end to a support beam, and a sheath covering the bolt and spring can be pivotally attached on one end to an adjacent support beam. The bolt and sheath device can be designed to allow the bolt to slide freely in and out of the sheath, while maintaining position of the spring around the bolt in a compartment formed by the bolt and the inner surface of the sheath. The spring can be contained on the free end of the bolt by a nut or the like. The spring can be retained within the sheath through which the bolt can slide by a lip on the free end of the sheath which forms an aperture only large enough to allow passage of the bolt. Thus, the spring is confined within a compartment defined by the bolt and the outer sheath. The spring can provide connective force between the adjacent support beams to which the bolt and sheath are attached, which can be adjusted by adjusting the positioning of the nut on the free end of the bolt to compress the spring, causing the fixed ends of the bolt and the sheath to be drawn together. This in turn causes adjacent support beams to be compressed together. In another embodiment, the sheath can be a two-piece member having raised ends which mate together, such that when the two ends are closed against one another, such as by the use of a nut or the like, the spring can be compressed, increasing the connective force between adjacent support beams. When a number of support beams are linked together to form an endless beam chain and the tensioning units are adjusted to compress adjacent support beams together, the chain is "prestressed." Although the support beams in the pre-stressed beam chain are compressed against one another, typically, the blocks mounted upon such support beams do not contact one another prior to experiencing thermal loading during casting, i.e., when the blocks are cold. Even after thermal loading, adjacent blocks can remain separated from one another by a small gap which will not be sufficiently large to allow molten metal to seep between the blocks. Even if the blocks make contact with one another after thermal loading, the adjacent blocks typically exert little to no force upon one another. The force required by the tensioning units to prevent adjacent beams from separating from one another, i.e., maintaining fixed pitch, during casting varies depending upon, for example, caster operational temperatures and support beam and block geometries and masses. The support beams which are interlinked to form the pre-stressed beam chain should also contain features such as rollers or the like for transporting the individual blocks in the chain around a continuous track. As used herein, the term "casting cycle" refers to the completion of a single revolution of the continuous track by the beam chain. In the apparatus of the present invention, the transport system employed is a roll support, wherein rollers mounted on a supporting member extending from a support beam flange travel along a continuous track. It is desirable that the roll support design substantially prevents binding of the rollers as the rollers negotiate bends in the track. In addition, it is preferable that the roll support be designed to substantially minimize block tilting. The roll supports of the present invention can include, for example a main roller and a counter-roller mounted on a supporting member extending from a support beam flange. Such roll supports minimize the distance between the axis of the load bearing roller (the main roller) and the casting surface of the chilling block, reducing the tendency of the block to pivot along the roller axis as it is driven along the track, thereby reducing block tilting. In addition, in the roll supports of the present invention, the axes of the main, load bearing roller and the counter-roller can also be offset in the casting direction (the "x-direction") to further reduce pivoting of the block along the main roller axis. In one embodiment of the roll support of the present invention, a main, load bearing roller, and a compressible counter-roller can be mounted on supporting member extending from a support beam flange. At the junction of the supporting member and the support beam flange, an apparatus, such as a wedge or similar device for adjusting the beam height, beam surface angle and beam pitch can be inserted. The rollers of the roll support can be arranged to compress and travel along a track for transporting the beam chain. The main roller can be fixed in position on an axle extending from the supporting member. The counter- roller can be mounted on one end of a lever-like member pivotally mounted to the supporting member. The other end of the lever-like member can be in contact with the supporting member using a compression device, such as a spring or the like for applying force to the lever to compress the counter-roller to the track surface. The roll support can also include a guide roller or the like for preventing movement of the individual blocks in a direction transverse to the casting direction (the "y-direction") as the block travels along the track. In an embodiment of a roll support, the main roller travels on an "upper" track surface and the counter-roller travels on a track surface opposed to the upper track surface. The counter-roller can be compressed to the opposed track surface, by the force exerted by a spring or the like on the one end of the lever-like member, also causing compression of the main roller with the upper track surface. The main roller can also be compressed to the upper track surface by the weight of the support beam and block assembly. The compressive forces exerted by the rollers on the track serve to pinch the rollers to the track and maintain the contact of the rollers with the track while the chain travels along the track through the casting cycle. The force applied by the compression unit which can be required for maintaining the main and opposed rollers in contact with the track system varies, for example, with the block and support beam masses. The compression unit should provide enough force to keep the rollers in contact with the track surfaces during the entire casting cycle. The endless track upon which the beam chain travels typically will contain two or more bends and two or more substantially linear sections when viewed from the y- direction. In particular, the track can have an elongated, substantially oval shape in profile when viewed from the y- direction. In order to accommodate the roll support of the present invention, the track system of the present invention can contain an upper track surface and an opposed track surface. In those embodiments where a guide roller is used to prevent movement of the blocks in the y- direction, an outer guideway can also be used. The tracks of the present invention are simple in design and can be manufactured to relatively low tolerances without substantially affecting cast quality. Moreover, when using the roll support and track of the present invention, the roll support is generally incapable of pinching or binding as it travels along the track, even after the track and roll support undergo substantial thermal expansion or deformation. In order to drive the pre-stressed beam chain along the track and through a casting cycle, the beam chain can also contain features for meshing with the drive system. More particularly, for meshing with the drive system, the support beams in a beam chain can contain pivot rollers, pins, cogs, gear racks or the like mounted on the support bea flanges. It is desirable to employ a drive meshing system which can reduce lever-like action of the block as it pivots on the roll support while being engaged by the drive system. It is further desirable to utilize a meshing system which is not overly sensitive to manufacturing tolerances or thermal deformation of the roll support and support beam during casting. In one embodiment, the present invention utilizes at least one pivot roller mounted to individual support beams for meshing individual beams in a beam chain to the drive system. Preferably, a pivot roller can be aligned on an axis common with the main roller of the roll support to reduce pivoting of the block while the beam chain is engaged by the drive system. The apparatus which comprise the track systems of the present invention, including, the pre-stressed beam chain, the roll support, the drive system meshing and the track, can be more readily understood by reference to Figures 1 through 4. Figure 1 illustrates one embodiment of the tensioning unit and one embodiment of the roll support of the present invention as viewed along an axis (the "z- axis") normal to the casting direction. In Figure 1, looking down through a support beam flange (cut away) , two roll supports 5, including main rollers 10, and counter rollers 15 having an axes 20 offset from the axis 25 of the main roller 10 in the x-direction 30, are attached to supporting members 35 extending from a support beam flange (200 in Figure 3) . At the junction of the supporting member and the support beam flange, an apparatus, such as a wedge or similar device for adjusting the beam height, beam surface angle and beam pitch can be inserted (not shown) . The roll supports 5 also contain pivot rollers 40 and needle bearings 45, which are aligned on the same axis 25 as the main rollers 10. A tensioning unit 50 is attached to the roll supports 5 near the bases of the pivot rollers 40, using pivoting attachments 55. Roll supports 5 also contain nose members 60, which mate with the needle bearings of an adjacent roll support after the two support beams are interconnected. Figure 2 illustrates a cut-away, close-up view of the embodiment of the tensioning unit of the present invention shown in Figure 1. In Figure 2, once again looking down through a support beam flange (200 in Figure 3) , the interior of a tension unit 50 is shown, which includes a bolt 100 having a lip 110 attached at one end and a spring 120 disposed around bolt 100 which is contained on its one end by the lip 110 on bolt 100 and on its other end by a lip 125 on sheath 130. Bolt 100 can be pivotally connected to supporting member 135 of a roll support and sheath 130 can be pivotally connected to an adjacent supporting member 135' of an adjacent roll support. The tension of spring 120 can be increased or decreased, e.g., by adjusting the position of lip 110 along the longitudinal axis of bolt 100. Lip 110 can be a nut which has been screwed onto bolt 100 for changing the tension in spring 120. The tension in the spring 120 can also be controlled by nut 145 and backing nut 150. By screwing down nut 145, the two parts of sheath 130 can be joined together forcefully to further compress spring 120, causing sheath 130 to slide along bolt 100, and forcefully connecting the two adjacent roll supports. Figure 3 is another view of one embodiment of the tensioning unit, one embodiment of the compression unit and one embodiment of the roll support of the present invention as shown in Figures 1 and 2 on a track 230. In Figure 3, looking in a direction along an axis (x-axis) parallel to the casting direction (x-direction) at the roll support 5 including a supporting member 205 extending from support beam flange 200, attachment of the tension unit 50 to the base of pivot roller 40 ' on each roll support interlinks the individual support beams in the beam chain. The view in Figure 3 shows how a compression unit 210, which has been pivotally mounted 220 on the supporting member 205, presses counter roller 15 against the track 230 by the force exerted by spring 240 which acts upon the lever created by the pivotally mounted compression unit 210. The compressive force applied by counter roller 15 to the opposed surface 250 of track 230 also transmits compressive force to the main roller 10 causing it to be forced into contact with the upper surface 260 of track 230. In Figure 3, a needle bearing 45 is shown, upon which a nose member 60 (in Figure 1) of an adjacent roll support will bear after interlinking of adjacent support beams. Figure 4 illustrates another view of one embodiment of the track and one embodiment of roll support of the present invention. In Figure 4, looking at the roll support in the y-direction one can more readily understand the roll support of the present invention. The needle bearing 45, shown in Figures 1 and 3, can be mated to nose member surface 300 of nose member 60 of roll support 310 shown in Figure 4. The tensioning unit described previously (not shown) creates a compressive force between support beams 310 and 335, forcing them together at intersection 300 between needle bearing 45 and nose member 60, resulting in the formation of a substantially smooth mold surface 330 when the blocks are under thermal loading, as shown. After the blocks 315 and 320 are thermally loaded, such as during casting, the blocks can make contact with one another along surface 325, although no force is exerted by adjacent blocks upon one another at surface 325. Thus, Figure 4 shows how multiple support beams can be mated together to form a beam chain. Figure 4 also shows the positioning of main rollers 10 in relation to the position of counter roller 15. Main rollers 10 are in contact with the upper surface 260 of track 230, and counter roller 15 is offset from the axes of the main rollers 10, and in contact with opposed surface 250 of track 230 as a result of the compressive force applied by the compression unit (not shown) . While nearly any drive system can be used with the pre-stressed beam chains of the present invention, it is desirable to employ a caster drive which does not adversely impact the quality of the cast, such as results from block tilting in the casting region. In particular, the drive system should exert substantially minimal forces on the beam chain through the drive meshing apparatus. Excessive forces can cause beam and block tilting. Preferred drive systems for use in the present invention should not be overly sensitive to manufacturing tolerances and should exhibit little to no reduction in performance due to thermal loading while casting. Such systems can utilize horizontal gear drives, vertical gear drives, wheel drives, sprocket drives or worm-gear drives and the like. In one embodiment, the present invention utilizes a novel worm-gear drive system for driving the individual beams in the beam chain along the track guideway and through a casting cycle. The worm-gear drive can include a motor connected to a cylindrical shaft having substantially spiral channels machined into its surfaces for accepting the pivot rollers mounted on a support beam. The longitudinal axis of the shaft can be aligned parallel to the beam chain in the x-direction to allow the pivot rollers mounted on support beams in the beam chain to mesh with the channels in the shaft. As the shaft is rotated, the pivot rollers in mesh with the channels in the shaft can be driven in the casting direction (or opposite to the casting direction if desired) and around the track. Rotation of the worm-gear can be controlled, for example, by control of the motor speed. The motor can be connected to the worm gear using, for example, a linkage of universal gears and drive shafts or the like. For maintaining substantially uniform beam chain speed along the caster track when using a worm gear drive system, a single beam chain can be in mesh with two worm-gear drive apparatus, one positioned on either side of a line drawn in the x- direction through the casting region of a caster. The worm-gear drive system is preferred for use in the present invention for several reasons. The worm gear drive can substantially minimize the number of parts required for driving the beam chain along the track and can substantially reduce the space requirements of the drive system. The worm-gear drive system can provide reduced obstruction of the caster, allowing relatively easy access to various parts of the caster for maintenance. In contrast to known drive systems, the worm-gear can be capable of being in contact with the pivot rollers from as few as one, but preferably at least as many as three beams at any one time. By using a drive system which engages several pilot rollers at once, errors caused by thermal deformations and low manufacturing tolerances during meshing of beams can be reduced because the effects from several beams simultaneously engaged by the drive system can be averaged out between the several beams. The movement of counter-rotating beam chains in a caster should be synchronized to obtain the most desirable cast quality. Synchronization of beam chain movement can be achieved through the use of mechanical or electrical systems. Nearly any mechanical or electrical synchronization system can be employed successfully in the present invention. Typically, the synchronization system utilized is dependent upon practical considerations, such as space and economic constraints, for example. In general, the use of two motors (one for driving each beam chain) can require more space, can increase the initial cost of producing the caster and can increase operational costs for the caster. Mechanical synchronization systems, which use shafts, spur gears and other apparatus, can allow the two beam chains to be driven by one motor, however, such systems do not provide as flexible control over beam chain movement as electrical synchronization systems. In the present invention, when using the worm-gear drive system and one motor to drive each beam chain, it is preferred to utilize electronic synchronization to control movement of the beam chains because electronic synchronization systems provide for more accurate control and adjustment to the individual beam chain speeds. The drive systems of the present invention can be better understood by reference to Figure 5. Figure 5 illustrates one embodiment of a drive system of the present invention in cut-away view in the z-direction of the surface of a beam chain 390. In Figure 5, worm-gears 400 consisting of a cylindrical shaft having helical channels machined into their length can be placed on each side of axis 405 drawn in the casting direction along a beam chain. Worm-gears 400 are driven by, for example, drive shafts 410 which are in turn driven through gearing 415 powered by a motor, such as an electric motor 420. Worm-gears 400 are engaged with pivot rollers 425, which drives the beam chain 390 along the track 430 and through a casting cycle using a roll support having main roller 440 and counter-rollers 450. In the embodiment illustrated in Figure 5, one motor drive is used for each beam chain, i.e., there are a total of two motor drives used in the entire caster, one for the upper beam chain and one for the lower beam chain, which are electronically synchronized and each motor drives two worm gears. While each of the components of the novel track and drive systems described herein can be capable of providing enhanced cast quality, it should be understood that it is the combination of the improved track and drive systems which produce the most desirable cast quality. In particular, a substantially planar mold surface can be obtained when using a worm gear drive to synchronously move the pre-stressed beam chains at substantially constant speed through the casting cycle. The quality of a cast produced by continuous block caster can also be affected by forces generated by the blocks as they travel through the casting cycle. For example, in block casters using elastic chains, the acceleration of the blocks as they negotiate the bends in an elongated oval track can result in banging between the blocks as they exit the bends. The forces propagated by adjacent blocks striking one another can be transmitted through the entire casting cycle, including the casting region, resulting in a reduction in the quality of the cast. In the present invention, however, the use of a pre- stressed beam chain can substantially prevent adjacent blocks from making contact with one another as they are driven through the casting cycle. Moreover, it has also been found that use of a track system which includes at least one movable segment allows for adjustment of track length to compensate for differences between the length of the beam chain and the track length, and helps to maintain compression of the beam chain after changes have occurred in beam chain or track length during casting caused, for example, by thermal loading. In one embodiment of the present invention, the movable track segment can be a movable "half-moon" placed in one bend of the track. The movable half-moon can be controlled pneumatically, electromagnetically, hydraulically or mechanically, at any time, including during casting, to increase or decrease the force on the beam chain by extending or shortening the track length. The force exerted on the half moon, the rate of change of force exerted on the half-moon or the distance which the half-moon travels can be monitored during casting to determine whether problems, such as seepage of molten metal between blocks, are occurring in the caster, prior to substantial damage occurring to the caster. In a preferred embodiment, a hydraulic cylinder or the like can be operated automatically to provide for constant tension of the pre-stressed beam chain. The movable segment should be designed to prevent gaps from occurring in the track between the fixed portion of the track and the movable segment which can affect the movement of the beam chain along the track. For example, a two-part sliding apparatus can be used, such that only half of a roller in a roll support of the beam chain is in contact with each half of the two-part sliding track apparatus. Thus, as the track length is extended or retracted, no gaps form in the track because at least one- half of each roller can be in contact with the track at all times. A better understanding of the movable segment of the track can be obtained by reference to Figures 6 through 8. Figure 6 illustrates track profile of one embodiment of a movable track segment in the present invention viewed in the y-direction. In Figure 6, moveable track segment 505 can be moved relative to the fixed portion of the track, for example, by using hydraulic cylinder 510 to move the half-moon in direction 515 to increase the length of track 520 or in direction 525 to decrease the length of track 520. The movement of moveable track segment 505 accounts for differences in track 520 length and the length of pre- stressed beam chain (not shown) , such as may result from thermal expansion of the blocks. Hydraulic cylinder 510 can be monitored to ensure that sufficient pressure is applied to the beam chain to allow smooth movement of the beam chain along the track 520 and to prevent excess force from being applied to moveable track segment 505 so as to create forces great enough to overcome the compression forces between blocks in a pre-stressed beam chain, resulting in gaps occurring between chilling blocks. Figure 7 is a cut-away view of one embodiment of a movable track segment, such as that shown in Figure 6. In Figure 7, movable segment 505 can be moved in direction 515 to extend the track length or can be moved in direction 525 to shorten the track length using, for example, a hydraulic cylinder or the like (not shown) . Movable segment 505 can be mated to the track 520 along interface 530 for preventing gaps from occurring as the movable segment 505 is moved, for example, by sliding segment 505 along interface 530. In this manner, the track 520 and movable segment 505 can comprise a two-part sliding apparatus. Figure 8 is a cross-sectional view of one embodiment of a two-part sliding apparatus for increasing and decreasing track length. In Figure 8, movable segment 505 can be slidably moved into or out of the page along interface 530 between movable segment 505 and a portion of the stationary track 520 by, for example, use of a hydraulic cylinder. Because approximately half of a main roller 540 and half of a counter-roller 550 of one embodiment of a roll support of the present invention ride on the track 520 and on the movable segment 505 at any one time, gaps that form between the track and moveable segment during changing of track length do not affect the movement of the beam chain as it travels along the track because approximately half of each roller is supported either by the track or the movable segment. While not intending the present invention to be constrained by theory, it is also believed that as beams of fixed pitch in a beam chain move from distinct sections of track, i.e., from linear to curved sections of the track, forces can be generated and propagated throughout the beam chain which can reduce cast quality. In the present invention, beams of fixed pitch in a beam chain travel on a track using a roll support or the like. As used herein, the term "speed" when used to describe pivot point speed, refers to the component of the pivot point λ velocity which is tangential to the track surface. Theoretically, each "pivot point" in the beam chain, (typically the roller axes of rollers of a roll support) can be driven with a constant caster drive speed V D along the linear sections of track with substantially constant speed V.,. Also theoretically, each pivot point in the same beam chain can be driven with caster drive speed V D along the curved sections of track (having a constant radius of curvature) with substantially constant speed V 2 . At constant beam pitch and constant caster drive speed V D , pivot point speed V 2 will be greater than V, because pivot points in the curved track sections are forced to travel a greater distance over the curved track surface. Thus, the pivot points of a beam chain having fixed pitches theoretically travel at a first speed V, in the linear sections of the track, and travel at a second, greater speed V 2 in the curved sections of the track. In practice, however, as the pivot points in a beam chain enter bends in the track, the pivot points have been observed to move with variable speed. In order for the speed of a pivot point to increase, the pivot point must experience acceleration. For example, in a continuous caster which employs elongated, substantially oval tracks, the pivot point must experience acceleration as it leaves a linear section of track and enters the curved section of track. The acceleration of a pivot point entering a bend is not instantaneous, and in general, the pivot point speed is initially slower than the theoretical speed V 2 . As the pivot point experiences acceleration, its speed increases beyond the theoretical speed V 2 , then slowly decreases towards the theoretical speed V 2 . An opposite phenomenon can be observed as a pivot point leaves a curved section of track and enters a substantially linear section of the track, i.e., exits a bend in the track. Such pivot point speed and acceleration variation is referred to herein as the "polygon effect". The polygon effect can cause reduction in the cast quality as the forces generated are propagated throughout the beam chain, particularly in the casting region. While the typical track profile of an elongated oval has been specifically discussed, the polygon effect can be observed in nearly any track configuration. In accordance with the present invention, methods and apparatus are provided for reducing the polygon effect and the resultant decrease in cast quality. Such methods and apparatus are not constrained to any particular track geometry. A better understanding of the polygon effect can be obtained by reference to Figure 9. Figure 9 is an illustration of how the polygon effect can be propagated as rollers connected by fixed pitches, i.e., rollers in a roll support, travel from substantially linear sections of an elongated, substantially oval track to a curved sections of the track and vice versa. The illustration in Figure 9 represents speed variations of pivot points in a beam chain of fixed pitches being driven at constant drive speed along the bottom track of a horizontal caster which does not compensate for the polygon effect. In Figure 9, a y- direction profile of a track in a horizontal block caster shows that a plot of pivot point speed 600 created in the bends 605 can be propagated through the beam chain to the straight segments 610 of track 615, resulting in reduction in the quality of the cast. The sinusoidal shape of the pivot point speed 600 illustrates the pivot point speed variations, referred to herein as the "polygon effect". Because the blocks are engaged by the drive system before entering the casting region (i.e., in one of the two bends) , the speed variations are observed to be dampened in the casting region relative to the other portions of the track. As used herein, the phrase "polygon effect compensating curves" refers to modifications in the caster track which have the effect of reducing the polygon effect and reducing the decrease in cast quality as a result of the polygon effect. For example, in a continuous caster which employs elongated, substantially oval tracks, the sinusoidal variation in pivot point speed can be reduced by the placement of polygon effect compensating curves at the entrance or exit (or both) to at least one bend in the track. The effect of the track modification can be to increase pivot point speed more rapidly (increase pivot point acceleration) at the entrance to the bend, then to reduce pivot point speed (decelerate the pivot point) as the pivot point moves through the length of track corresponding to one pitch. Different track geometries, however, create different speed variations, and polygon effect compensation curves can be obtained and used for such different track geometries. Different track geometries include, without limitation, tracks having two or more interconnected linear sections. One example of a polygon effect compensating curve which can be used in an elongated, substantially oval track can be a section of track inserted at the entrance to a bend in a track (i.e., where a substantially linear portion of a track begins to become curved) which decreases the slope of the track, then rapidly increases the slope of the track, i.e., the compensating curve can be sinusoidal when viewed in the y-direction. These adjustments can be made to one or more entrances to the bends in a track, to one or more exits to the bends in a track, or to both at least one entrance and at least one exit to a bend in a track. The benefits of polygon effect compensation in this manner are realized if only one track profile adjustment is made, however, the polygon effect compensation observed generally increases with the number of adjustments made. Thus, the most desirable polygon effect compensation can be obtained when polygon effect compensating curves are used at all the entrances and all the exits to bends in a track. One can gain a better understanding of how the polygon effect compensation curves can be obtained by reference to Figure 10. In one embodiment of the methods and apparatus of the present invention, as shown below and in the drawing in Figure 10, the polygon effect compensating curves for an elongated, substantially oval track for use in a continuous block caster can be calculated indirectly as a function of the relative position (5) of a pivot point in a pivot point path. Ideally, a pivot point travel path 700 for pivot point p 2 is desired such that the relative position of pivot point p 1 in the last pitch p' of the linear section of the track, i.e., Δp P is substantially equivalent to the relative position of a preceding pivot point p 3 in the second pitch p" of a bend, i.e. , Δφ ~ Φ ~ ' as the pivot points move along the track. Thus, δ = AR = AΦ P Φ The desired pivot point travel path 700 for pivot point p 2 can be calculated from the following formulae where the pitch (p) and the sum of pitches in both bends in the track (n) are known: Φ = 2-π n R = 2*sιn (i) a = p • (1 - δ) + R-sin (φ • (1 + δ) ) b = R - R- cos (ø • (1 + δ) ) c = y'a 2 + 2 x? - P ' ( s ~ χ ) + d z 2 = R - e R 2 - X, φ 2 = if I x 2 = 0 , 0 , atan | 2 ΔR 2 = R 2 - R Where: R = Radius of the pivot point travel path as the pivot point moves through a bend in a track; φ = bend angle for one pitch of a bend in the track; R 2 = calculated desired radius of the pivot point travel path for pivot point p 2 ; ΔR 2 = calculated change in pivot point travel radius for a given δ ; and φ 2 = calculated bend angle for a given δ . The polygon effect compensation curves for the track can be determined by changing the track radius a substantially equivalent amount to the change ΔR 2 in pivot point travel radius , at a calculated bend angle φ z , i.e., providing a track profile which results in the desired pivot point travel path 700. It has been observed that for the polygon effect compensating curves in an elongated, oval track to provide the most desirable effect, each bend in a track should be at least about 3 pitches long. Although polygon effect compensating curves can be derived mathematically, such curves can also be obtained through, for example, the use of computer aided design (CAD) systems or the like. Moreover, one need not use mathematically calculated polygon effect compensating curves to obtain some of the benefits of the present invention. For example, satisfactory results can be obtained through the use of approximated compensating curves. A better understanding of the polygon effect compensating curves of the present invention can be obtained by reference to Figure 11. Figure 11 illustrates one embodiment of polygon effect compensating curves of the present invention in an elongated, substantially oval track viewed in the y-direction. In Figure 11, polygon effect compensating curves 705 have been placed in the track profile 710 at the entrance and exits to the bends 715 of the elongated oval track. Polygon effect compensating curves 705 are sinusoidal when viewed in the y-direction, for compensating for the sinusoidal nature of pivot point speed. A track having a profile including polygon effect compensating curves 705, such as is shown in Figure 11, reduces the polygon effect, as is shown by the smooth pivot point speed diagram 720 shown in Figure 11. The dampening and smoothing of the polygon effect results in substantially constant pivot point speed in the linear sections 725 of the track. Therefore, while the polygon effect can not be completely eliminated, variations in pivot point speed can be substantially minimized by using the polygon effect compensating curves 705 in the entrance and exits to the bends 715 of track 710. Even when compensating for the polygon effect, forces propagated by the block masses as the blocks rotate through the bends in the track can be transmitted to other blocks in the beam chain and can affect the quality of the cast. It has been found, however, that rotational forces of the block masses can be reduced by offsetting the occurrences of these rotational forces. In a block caster using an elongated oval-shaped track profile, offsetting of the rotational forces can be accomplished by providing track profiles which provide for (1) an uneven number of blocks in a track, and an even sum of blocks in all the bends in the track, (2) an even number of blocks in a track, and an uneven sum of blocks in all the bends in the track, or preferably, (3) an uneven number of blocks in a track, and an uneven sum of blocks in all the bends in the track. The term "bend" as used herein, refers to the semicircular end portions of the track beginning and ending at the points where the track changes from substantially linear portions to curved portions. Thus, in a typical oval track, there are two "bends." The number of blocks in a beam can be adjusted by adjusting track length. The number of blocks in the bends in a track can be adjusted, for example, by adjusting the radii of the bends. In many cases, the radii of the two bends in the track can be substantially the same. In a preferred embodiment, when using an elongated oval track, in order to offset the rotational forces, the number of blocks (or beams) in a beam chain and the sum of the blocks in both bends of the track should obey the following mathematical formulae: 1 = 1 + 2 i m = 1 + 2k where 1 = the total number of blocks in a beam chain; = the sum of the blocks in both bends of a track; i = integer e {3,4,5,6,7,...}; k = integer e {1,2,3,4,5,...}; and where i > k+2. Moreover, it has been found that when compensating for rotational forces in this manner, the radii (R) of pivot point travel paths for the bends of the track can be determined by the formula: R = 2sι i n n rø where: m is in the range of about 0.5+2k and about 1.5+2k; and p = pitch, i.e., the fixed distance between pivot points in a beam chain. The rotational forces offset system can be more easily understood by reference to Figures 12 through 15. Figure 12 represents a view of a beam chain profile in the y- direction of a known block caster which does not compensate for rotational forces created by blocks moving through a casting cycle. Figures 13, 14 and 15 illustrate embodiments of the present invention for compensating for rotational forces created by blocks moving through a casting cycle. In Figures 12 through 15, beam chain profiles in an elongated oval shape have a number of pivot points 801 defined by the location of the main rollers in the beam chain. The distance between pivot points, i.e., the pitch of a block in the chain, is numbered 805. By counting the number of pitches between pivot points, the numbers of blocks in a beam chain and the number of blocks in the bends in a track can be determined. In Figure 12, the number of blocks in the beam chain is even (10) , and the sum of blocks in the bends of the track is even (4) . In this case, the rotational forces created by block masses traveling through the casting cycle are substantially at a maximum. None of the rotational forces have been offset. In Figure 13, by changing one of the radii of the bends of the track, the number of blocks in the beam chain can be changed to an odd number (9) , however, the sum of the blocks in the bends remains even (4) . In this case, the rotational forces have been only partially offset and typically can result in about a 25 percent decrease in the amplitude of forces transmitted by the blocks through the beam chain compared to rotational blocks when in the positions shown in Figure 12. In Figure 14, both radii of the bends have been changed to give an uneven sum of blocks in the bends (3) , however, the number of blocks in the beam chain is now even (8). Similar to the case in Figure 13, the rotational forces have been partially offset and typically can result in about a 25 percent decrease in the amplitude of forces transmitted by the blocks through the beam chain compared to rotational forces created by blocks when in the positions shown in Figure 12. In Figure 15, however, the manipulation of the radii of the bends in the track and the length of the track provides for an odd number of blocks in the beam chain (9) , and an odd sum of blocks in the bends of the track (3) . In this case, the rotational forces created by the blocks can be substantially offset, reducing the negative impact these forces can make on the cast. Implementation of the solution shown in Figure 15 can result in about a 90 percent decrease in the forces transmitted by the blocks through the beam chain compared to rotational forces created by blocks when in the positions shown in Figure 12. While each individual improvement in the apparatus of the track and drive systems of the present invention can be useful for improving cast quality, when used in concert, the track system and drive system improvements can be particularly useful for enhancing cast quality, such as by providing a substantially planar casting surface and for reducing forces generated by the blocks traveling through the casting cycle. The methods of the present invention comprise methods for using the apparatus of the present invention. In the method of the present invention, metal can be continuously cast in a block caster which includes the improved track and drive systems. In one embodiment of the methods of the present invention, molten metal, for example, aluminum, aluminum alloys, or steel can be supplied from a tundish or the like to the moving mold of a block caster, where it can be solidified and removed from the caster as a strip, sheet or slab. The moving mold can comprise two beam chains, such as pre-stressed beam chains, disposed in close relation to one another, traveling in synchronized fashion through casting cycles. The prestressed beam chains can be further comprised of several support beams and block assemblies interconnected by tensioning units which interlink and compress adjacent beams together. The prestressed beam chain can also include a roll support comprising a main, load bearing roller and a counter-roller for transporting the beam chain along a track. The track can include at least one movable segment, such as a half-moon, for adjusting for differences in the length of the track and the beam chain. As the beam chain travels along the track, the movable track segment can be adjusted to accommodate changes in the beam chain length, for example as a result of thermal loading. Moreover, the force exerted, the rate of changes in the force exerted, and/or the distance travelled by the movable segment on the beam chain can be monitored to determine whether problems are occurring in the caster. The methods of the present invention can include driving a beam chain along a track using an improved drive system, preferably a worm gear drive. The worm gear drive system can include a pair of worm gears positioned on either side of each beam chain in mesh with pivot rollers or the like mounted on the beam chain. The worm gear drives can be synchronized using an electrical or a mechanical synchronization system, but preferably an electrical synchronization system. In a preferred embodiment the methods of the present invention can comprise a method for continuously casting aluminum alloys, such as aluminum alloy container stock, for use in the manufacture of containers and the like. For example, molten aluminum can be provided to a moving mold of a block caster utilizing the improved track and drive systems of the present invention, solidifying the molten metal into a cast aluminum strip, and removing such cast strip from the casting region of a continuous block caster for use as container stock in the manufacture of aluminum containers and the like. While various embodiments of the present invention have been described in detail, it is apparent that further modifications and adaptations of the invention will occur to those skilled in the art. However, it is to be expressly understood that such modifications and adaptations are within the spirit and scope of the present invention.

Claims: What is claimed is: 1. A continuous block caster comprising: (a) a pre-stressed beam chain comprising a number of blocks mounted on interlinked support beams; (b) a track comprising: (i) a movable segment; (ii) a plurality of linear sections and a plurality of bends; and (iii) at least one polygon effect compensating curve; (c) means for transporting said pre-stressed beam chain along said track; and (d) means for driving said pre-stressed beam chain along said track. 2. The continuous block caster as claimed in Claim 1, wherein said support beams are interlinked using a tensioning device. 3. The continuous block caster as claimed in Claim 2, wherein said tensioning device comprises a spring and bolt apparatus pivotally connected to adjacent support beams. 4. The continuous block caster as claimed in Claim 1, wherein said track comprises an elongated, substantially oval shape. 5. The continuous block caster as claimed in Claim 1, wherein said movable segment comprises a half moon. 6. The continuous block caster as claimed in Claim 1, wherein said polygon effect compensating curve is located at the entrance to at least one of said bends in said track. 7. The continuous block caster as claimed in Claim 1, wherein said polygon effect compensating curve is located at the exit of at least one of said bends in said track. 8. The continuous block caster as claimed in Claim 7, wherein said polygon effect compensating curve is located at the exit of at least one of said bends of said track. 9. The continuous block caster as claimed in Claim 1, wherein said means for transporting said pre-stressed beam chain comprises a roll support. 10. The continuous block caster as claimed in Claim 9, wherein said roll support comprises a main roller and a counter-roller mounted on a supporting member extending from a flange on said support beam. 11. The continuous block caster as claimed in Claim 10, wherein said supporting member comprises means for adjusting the beam height. 12. The continuous block caster as claimed in Claim 10, wherein said supporting member comprises means for adjusting the beam surface angle. 13. The continuous block caster as claimed in Claim 10, wherein said supporting member comprises means for adjusting the beam pitch. 14. The continuous block caster as claimed in Claim 10, wherein said track has two opposed surfaces and said main roller can be in contact with one of said opposed surfaces and said counter-roller can be in contact with the other of said opposed surfaces. 15. The continuous block caster as claimed in Claim 9, wherein said roll support comprises means for meshing with said means for driving said pre-stressed beam chain. 16. The continuous block caster as claimed in Claim 15, wherein said means for meshing with said means for driving said pre-stressed beam chain comprises a pivot roller. 17. The continuous block caster as claimed in Claim 1 , wherein said means for driving said pre-stressed beam chain comprises a worm gear drive. 18. The continuous block caster as claimed in Claim 1, comprising two pre-stressed beam chains. 19. The continuous block caster as claimed in Claim 18, comprising two tracks. 20. The continuous block caster as claimed in Claim 19, comprising two means for driving said pre-stressed beam chains along said tracks. 21. The continuous block caster as claimed in Claim 20, comprising means for synchronizing the movement of said two beam chains along said tracks. 22. A continuous block caster comprising: (a) a track having a fixed portion and a movable segment; (b) a pre-stressed beam chain comprising a plurality of interlinked support beams, said beam chain disposed on said track; and (c) means for driving said pre-stressed beam chain along said track. 23. The continuous block caster as claimed in Claim 22, wherein said pre-stressed beam chain comprises a plurality blocks mounted on said interlinked support beams. 24. The continuous block caster as claimed in Claim 22, wherein said plurality of blocks in said beam chain comprises an uneven number. 25. The continuous block caster as claimed in Claim 22, wherein said track comprises a plurality of linear sections and a plurality of bends. 26. The continuous block caster as claimed in Claim 25, wherein the numerical sum of blocks in said bends is uneven. 27. The continuous block caster as claimed in Claim 25, wherein the numerical sum of blocks in said bends is uneven and said plurality of blocks in said beam chain comprises an uneven number. 28. The continuous block caster as claimed in Claim 22, wherein said movable segment comprises a half moon. 29. The continuous block caster as claimed in Claim 22, wherein said track comprises at least one polygon effect compensating curve located at the entrance to at least one of said bends. 30. The continuous block caster as claimed in Claim 22, wherein said track comprises at least one polygon effect compensating curve located at the exit of at least one of said bends. 31. The continuous block caster as claimed in Claim 22, wherein said means for driving said pre-stressed beam chain comprises a worm gear drive. 32. A continuous block caster comprising: (a) a track having at least two linear sections and at least two bends; (b) a beam chain disposed upon said track, said beam chain comprising an . uneven number of blocks mounted on interlinked support beams; and wherein the numerical sum of said chilling blocks capable of being in said bends of said track at any point in time is uneven. 33. The continuous block caster as claimed in Claim 32, wherein said track comprises a fixed portion and a movable segment. 34. The continuous block caster as claimed in Claim 32, wherein said interlinked support beams define fixed pitches (p) of said beam chain between pivot points and said pivot points have travel paths in said bends with radii (R) which can be determined by the formula: Where: m is in the range of about 0.5+2k and about 1.5+2k; and k = integer e {1,2,3,4,5,...} . 35. A pre-stressed beam chain having fixed pitches for use in a continuous block caster comprising: (a) a plurality of support beams; (b) a tensioning device pivotally connecting adjacent support beams; (c) blocks mounted on said support beams; and wherein said tensioning device is capable of holding adjacent support beams together and substantially preventing displacement of said adjacent support beams relative to one another while traveling through a casting cycle. 36. The pre-stressed beam chain as claimed in Claim 35, wherein said tensioning device comprises a spring retained around a bolt disposed within a sheath. 37. The pre-stressed beam chain as claimed in Claim 35, wherein said blocks comprise chilling blocks mounted on at least one block holding plate. 38. The pre-stressed beam chain as claimed in Claim 35, wherein said support beams comprise a needle bearing and a nose member. 39. The pre-stressed beam chain as claimed in Claim 38, wherein said nose member of one support beam contacts a needle bearing of an adjacent support beam. 40. The pre-stressed beam chain as claimed in Claim 35, wherein said blocks mounted on adjacent support beams when cold do not make contact with one another. 41. The pre-stressed beam chain as claimed in Claim 35, wherein said blocks mounted on adjacent support beams, when thermally loaded, exert little to no force against one another. 42. The pre-stressed beam chain as claimed in Claim 35, wherein said blocks mounted on adjacent support beams are substantially parallel to one another. 43. A roll support for use in transporting a support beam along a track having two opposed surfaces, comprising: (a) a main roller, said main roller in contact with one of said opposed surfaces of said track; (b) a counter-roller, said counter-roller in contact with another of said opposed surfaces of said track; and (c) a compression device for maintaining contact between said main roller and one of said opposed surfaces of said track and maintaining contact between said counter- roller and another of said opposed surfaces of said track as said support beam travels along said track. 44. The apparatus as claimed in Claim 43, wherein said compression device comprises a spring. 45. The apparatus as claimed in Claim 43, wherein said main roller and said counter-roller are mounted on a supporting member extending from said support beam. 46. The apparatus as claimed in Claim 45, wherein said supporting member comprises means for adjusting the beam height. 47. The apparatus as claimed in Claim 45, wherein said supporting member comprises means for adjusting the beam surface angle. 48. The apparatus as claimed in Claim 45, wherein said supporting member comprises means for adjusting the beam pitch. 49. The apparatus as claimed in Claim 45, wherein said roll support is mounted on a flange of said support beam. 50. The apparatus as claimed in Claim 43, wherein said roll support comprises means for meshing with a means for driving said support beam along said track. 51. The apparatus as claimed in Claim 50, wherein said means for meshing comprises a pivot roller. 52. The apparatus as claimed in Claim 50, wherein said means for driving said support beam along said track comprises a worm gear. 53. The apparatus as claimed in Claim 43, wherein said roll support comprises means for substantially preventing movement of said support beam in the y- direction. 54. The apparatus as claimed in Claim 43, wherein said means for substantially preventing movement on said support beam in said y-direction comprises a lateral guide roller. 55. The apparatus as claimed in Claim 54, wherein said track comprises a lateral guideway. 56. An apparatus for driving a beam chain along a track in a continuous block caster comprising: (a) a motor; (b) a worm gear connected to said motor, said worm gear disposed next to said beam chain; (c) means for meshing said beam chain with said worm gear; and wherein said motor is capable of energizing said worm gear such that said worm gear is capable of engaging said means for meshing said beam chain with said worm gear to cause said beam chain to move. 57. The apparatus as claimed in Claim 56, comprising multiple worm gears. 58. The apparatus as claimed in Claim 57, wherein said beam chain is in mesh with multiple worm gears. 59. The apparatus as claimed in Claim 58, wherein said beam chain is in mesh with two worm gears. 60. The apparatus as claimed in Claim 56, wherein said beam chain is capable of being moved by said worm gear in the casting direction. 61. The apparatus as claimed in Claim 56, wherein said beam chain is capable of being moved by said worm gear in a direction opposite to the casting direction. 62. The apparatus as claimed in Claim 56, wherein said motor and worm gear are capable of moving said beam chain at substantially constant speed along said track. 63. The apparatus as claimed in Claim 56, wherein said block caster comprises two beam chains disposed upon two tracks. 64. The apparatus as claimed in Claim 63, wherein said block caster comprises means for synchronizing movement of said beam chains along said tracks. 65. The apparatus as claimed in Claim 64, wherein said means for synchronizing movement of said beam chains along said tracks comprises mechanical synchronization. 66. The apparatus as claimed in Claim 63, wherein said block caster comprises two motors. 67. The apparatus as claimed in Claim 66, wherein said block caster comprises means for synchronizing movement of said beam chains along said tracks. 68. The apparatus as claimed in Claim 67, wherein said means for synchronizing movement of said beam chains along said tracks comprises electrical synchronization. 69. The apparatus as claimed in Claim 56, wherein said motor is connected to said worm gear using at least one universal gear and a shaft. 70. The apparatus as claimed in Claim 56, wherein said beam chain comprises interlinked support beams. 71. The apparatus as claimed in Claim 70, wherein said means for meshing said beam chain with said worm gear comprises pivot rollers mounted on said support beams. 72. The apparatus as claimed in Claim 56, wherein said worm gear comprises a cylindrical shaft having helical channels machined along the longitudinal axis of said shaft. 73. The apparatus as claimed in Claim 72, wherein said shaft is disposed in close proximity to said beam chain. 74. The apparatus as claimed in Claim 72, wherein said shaft is capable of being rotated about the longitudinal axis of said shaft by said motor. 75. The apparatus as claimed in Claim 72, wherein said means for meshing said beam chain with said worm gear comprises pivot rollers mounted on said support beams. 76. The apparatus as claimed in Claim 75, wherein said pivot rollers are capable of being engaged by said helical channels of said shaft. 77. An apparatus for reducing the rotational forces created by a beam chain traveling through a casting cycle in a continuous block caster comprising: (a) a track having a plurality of linear sections and a plurality of bends; (b) a beam chain disposed on said track, said beam chain comprising blocks mounted on interlinked support beams, wherein said track and said beam chain are designed to obey the following formulae: 1 = 1 + 2 i m = 1 + 2k wherein 1 = the total number of beams in said beam chain; m = the sum of the beams in said bends of said track; i = integer e {3,4,5,6,7,...}; k = integer e {1,2,3,4,5,...}; and i > k+2. 78. The apparatus as claimed in Claim 77, wherein said interlinked support beams define fixed pitches (p) of said beam chain and said bends of said track have radii (R) which can be determined by the formula: R = 2sιn Where m is in the range of about 0.5+2k and about 1.5+2k . 79. The apparatus as claimed in Claim 77, wherein said track comprises an elongated, substantially oval shape. 80. The apparatus as claimed in Claim 77, wherein said track comprises at least one polygon effect compensating curve located at the entrance to at least one of said bends. 81. The apparatus as claimed in Claim 77, wherein said track comprises at least one polygon effect compensating curve located at the exit of at least one of said bends. 82. An apparatus comprising: (a) a track having at least one linear section and at least one bend, said track comprising at least one polygon effect compensating curve; (b) a beam chain disposed upon said track, said beam chain comprising a plurality of interconnected support beams; and (c) means for driving said beam chain along said track. 83. The apparatus as claimed in Claim 82, wherein said track comprises at least one polygon effect compensating curve at the entrance of said at least one bend. 84. The apparatus as claimed in Claim 82, wherein said track comprises at least one polygon effect compensating curve at the exit of at least one bend. 85. The apparatus as claimed in Claim 82, wherein said polygon effect compensating curve comprises a sinusoidal track segment. 86. The apparatus as claimed in Claim 82, wherein said track comprises an elongated, substantially oval shape having two bends. 87. The apparatus as claimed in Claim 86, wherein said beam chain comprises a beam chain comprised of a plurality of fixed pitches. 88. The apparatus as claimed in Claim 87, wherein said polygon effect compensating curve comprises a curve defined as by changing the track bend radius a substantially equivalent amount to the calculated change ΔR. in pivot point travel path radius R, for a calculated bend angle φ ≥ l wherein both ΔR 2 and ø 2 can be calculated as a function of the relative position δ of a pivot point in a pivot point travel path, from the following formulae where the pitch (p) and the sum of pitches in both bends in the track (n) are known: 2-π Φ n R • s B) a = p • (1 - δ) + R- sin (φ • (1 + δ) ) b = R - R- cos (ø • (1 + δ) ) c = a 2 + b 2 = p • ( δ - 1) + d = R - e R 2 = f i 2- 2 ++ Z Z -2 - Φ = ifI x, = 0,0, atanl 2 Where: δ = AR = Φ . δ P Φ ' R = Radius of the pivot point travel path as the pivot point moves through a bend in a track; and ø = bend angle for one pitch of a bend in the track. 89. The apparatus as claimed in Claim 82, wherein said number of pitches in said bend comprises at least about 3. 90. An apparatus for compensating for the polygon effect comprising: (a) a track having at least two distinct sections; (b) a plurality of rollers disposed on said track, said rollers interconnected to one another at fixed pitch; (c) a compensating curve located in said track at about where one section meets another section; and wherein said compensating curve is capable of minimizing speed variations of said rollers as said rollers move from one section to another section of said track. 91. The apparatus as claimed in Claim 90, wherein said track comprises at least one linear section and at least one non-linear section. 92. The apparatus as claimed in Claim 91, wherein said track comprises an elongated, substantially oval shape having two bends. 93. The apparatus as claimed in Claim 92, wherein said compensating curve comprises a curve in said track defined as by changing the track bend radius a substantially equivalent amount to the calculated change AR. in roller axes travel radius R, for a calculated bend angle ø 2 , wherein both ΔR 2 and ø 2 can be calculated as a function of the relative position δ of a roller axis in a roller axis travel path, from the following formulae where the pitch (p) and the sum of pitches in both bends in the track (n)- are known: Φ = _ 2-π n 2-βin(i) p • (1 - δ) + R-sin (ø • (1 + δ) ) b - R - R-cos (ø • (l + δ) ) = v/a = p • {δ - 1) + d - R - e φ 2 = ifI x 2 == 0,0, atanj— )) ΔR j = R j - R Where: * _ Δp _ Δφ . ~ P ~ " T ' R = Radius of the roller axis travel path as the rollers move through a bend in a track; and ø = bend angle for one pitch of a bend in the track. 94. The apparatus as claimed in Claim 90, wherein said track comprises at least two linear sections. 95. An apparatus for accommodating the difference between beam chain length and track length in a continuous block caster comprising: (a) a track having a fixed portion and a moveable segment; and (b) an means for adjusting the position of said moveable track segment relative to said fixed portion of said track. 96. The apparatus as claimed in Claim 95, wherein said means for adjusting the position of said movable track segment comprises a hydraulic device. 97. The apparatus as claimed in Claim 95, wherein said means for adjusting the position of said movable track segment comprises a pneumatic device. 98. The apparatus as claimed in Claim 95, wherein said means for adjusting the position of said movable track segment comprises a mechanical device. 99. The apparatus as claimed in Claim 95, wherein said means for adjusting the position of said movable track segment comprises an electrical device. 100. The apparatus as claimed in Claim 95, wherein said electrical device comprises an electromagnetic device. 101. The apparatus as claimed in Claim 95, wherein said track comprises a plurality of bends. 102. The apparatus as claimed in Claim 101, wherein said moveable segment comprises a bend in said track. 103. The apparatus as claimed in Claim 95, wherein said track comprises means for monitoring the force applied by said movable segment on said beam chain. 104. The apparatus as claimed in Claim 103, wherein said track comprises means for monitoring changes in said force applied by said movable segment on said beam chain. 105. The apparatus as claimed in Claim 95, wherein said track comprises means for monitoring changes in the position of said movable segment relative to said fixed portion of said track. 106. The apparatus as claimed in Claim 105, wherein said track comprises means for monitoring the rate of changes in the position of said movable segment. 107. A method for reducing forces which have a deleterious effect upon the quality of a cast in a continuous block caster, comprising the steps of: (a) providing molten metal to a moving mold, said mold comprising at least one beam chain disposed on a track; (b) driving said beam chain along said track, said track comprising a fixed portion and a movable segment; (c) cooling said molten metal; (d) removing solidified metal from said continuously moving mold. 108. The method as claimed in Claim 107, comprising the step of monitoring the force applied by said movable segment on said beam chain. 109. The method as claimed in Claim 108, comprising the step of monitoring changes in said force applied by said movable segment on said beam chain. 110. The method as claimed in Claim 107, comprising the step of monitoring changes in the position of said movable segment relative to said fixed portion of said track. 111. The method as claimed in Claim 110, comprising the step of monitoring the rate of changes in the position of said movable segment. -63- x 2 - P " (S - 1) + d = R - e Where: 5 - Δp _ Δφ P Φ R = Radius of the roller axis travel path as the rollers move through a bend in a track; and ø = bend angle for one pitch of a bend in the track; and (c) changing the track bend radius a substantially equivalent amount to the change AR. in pivot point travel radius R, for a calculated bend angle ø 2 .

Inventors: LUGINBUEHL ERICH, MEYER MICHEL, RODER RUDOLF, WITSCHI MARCEL, ZUERCHER ERNST, LUGINBUEHL, ERICH, MEYER, MICHEL, RODER, RUDOLF, WITSCHI, MARCEL, ZUERCHER, ERNST
Applicants: LAUENER ENG LTD, LAUENER ENGINEERING, LTD.
Application year: 1995
Main classification: B22D11
IPC codes: B22D11, F16H7