Elevated cableway system

Abstract: An improved cableway system for providing a track over which a vehicle traverses is disclosed. The improved system includes a catenary cable system (16) and a pair of track cable systems (14). The track cable systems (14) are hung from the catenary cable system (16) and support tracks over which a vehicle (12) traverses. A plurality of hangers (27) is employed to suspend the track cable systems (14) from the catenary cable system (16). A plurality of pylons (17) support the catenary and track cable systems (14,16). A pylon (17) includes a base pylon (21), a lower saddle (200), and an upper saddle (30). The lower saddle (200) is pivotally mounted to the base pylon (21) and supports the track cable systems (14). Preferred embodiments of the lower saddle (200) include apparatuses that dampen the application of loads to the pylon (17) by the vehicle (12) traversing the system. The upper saddle (30) is supported by the base pylon (21) and supports the catenary cable system (16) while providing for deflection of the catenary cable system (16) in response to forces applied to the cableway system. A preferred embodiment of the cableway system includes a force-equalizing assembly (300) for joining the catenary cable system (16) to the track cable system (14) at points between support pylons (17) to equalize the tension in the cables among the various cables.

Description: Field of the Invention This invention pertains to elevated cableway systems used in mass transit systems and the like, and, more particularly, to an improved cableway for such systems. Description of the Prior Art Many types of elevated cableway systems have been used in or proposed for mass transit systems. One such system is disclosed and claimed in United States Letters Patent 4,069,765 issued January 24, 1978 to Gerhard Müller. This system is neither a suspension, or cable stayed bridge nor an aerial tramway. Consequently, not all standard design criteria are necessarily applicable to the system in the Müller '765 patent. Thus the Müller '765 patent discloses a non-standard approach and Figures 1-5 of the present application correspond to Figures 3-7 of the Müller '765 patent. Figure 1 illustrates in gross an elevated cableway system 10 in which vehicle 12 travels along track cable systems 14 suspended from catenary, or support cable 16. As shown in Figures 2-3 and 5, track cable systems 14 comprises locked-coil steel cables 14a-d and catenary cable system 16 comprises locked-coil steel cables 16a-b. Returning to Figure 1, a plurality of pylons 18 elevate and support track cable systems 14 and catenary cable system 16 between the termini 20 of system 10. Track cable systems 14 and catenary cable system 16 are preferably anchored to ground 19 to sustain horizontal cable forces and transmit them to ground 19. One of Müller's basic approaches is illustrated in Figures 1-2. Stress loads associated with the "sag" in track cable systems 14 and catenary cable system 16 caused by the weight of vehicle 12 were a problem for cableway systems at the time Müller filed the '765 patent application as shown in Figure 1. Müller proposed, as disclosed in the '765 patent, to address these problems by pre-tensioning, or pre-stressing, track cable systems 14 so that track cable systems 14 levelled under the weight of vehicle 12 as shown in Figure 1. Part of Müller's proposed design included new cross-ties 15 and hangers, or spacers, 7 for suspending track cable systems 14 from catenary cable system 16. These cross-ties 15 and hangers 7, which were new at the time, are illustrated in Figures 2-3. Through this suspension system, track cable systems 14 were tensioned as described above and, consequently, "bowed" upward when not weighted by vehicle 12. This approach has worked well and is incorporated in the present invention as set forth below. Müller also proposed tying track cable systems 14 and catenary cable system 16 together between pylons 18 at points 22 as shown in Figure 4. Müller tied the cables with force equalization plate 24, in cooperation with clamping plate 26 and wedges 28. Force equalization plate 24 also improved the distribution of load stresses in the cableway system and, in combination with tensioning track cable systems 14, substantially advanced the art. Müller also adopted the pylon structure earlier disclosed in United States Letters Patent 3,753,406. As set forth in column 1, line 65 to column 2, line 3 of the '765 patent, it was thought the pylons in such a system must be "stiff". It was though that "self-aligning" or "self-adjusting" pylons would introduce undesirable longitudinal shifting between the catenary and track cables. However, we now know that "self-aligning" or "self-adjusting" pylons produce substantial design benefits provided measures are taken to minimize or eliminate longitudinal shifting. Some problems also appeared in implementing Müller's design despite its great advance over the art. For instance: (1) catenary cable system 16 was strung over rollers on the top of pylons 18 and began to wear from the movement across the rollers as vehicle 12 traversed the cableway; (2) the design of the equalizer plate 24 could also cause problems by kinking cable elements 16a-b, and 14a-d, under some circumstances; and (3) cable elements 14a-d were required to have upper surfaces engageable by the wheels of the vehicle because the equalizer plate did not provide for such engagement. It further came to be realized that load stresses could be better distributed through redesign of the force equalizing assembly as well as the hangers and cross-ties, particularly in light of the new pylon designs. United States Pat. No. 4,264,996 by Baltensperger and Pfister describes a suspended railway system with towers that support a catenary cable atop the towers and support track cables with a "stressing beam" that is pivotally connected to the towers. The '996 system is, however, distinguishably less capable than the present invention. For instance, the '996 patent fails to grasp the catenary cable at the support on top of the tower. Therefore, as described in the '996 patent, the cable is allowed to slip in the notches of the support. This slippage will inevitably cause wear on the cables. Additionally, while the stressing beam gives some measure of weight redistribution at the track cable support, the fact that there is only one beam and the fact that the beam merely pivots about a single point ensures that the impact with the support of a vehicle passing over the support will not be substantially lessened. When weight is applied to one end of the beam, the other end of the beam necessarily must tilt upwardly thereby creating a ramp for a vehicle traversing the track to climb. With only a single beam, the tilt of the beam cannot be lessened until the vehicle passes each point along the beam. If the beam had secondary and tertiary beams connected to it as the present invention does, the moment about the central pivot point could be lessened in advance of the vehicle. With secondary and tertiary beams, the point of applied load is the point where the secondary beam attaches to the main beam, not the point the vehicle is passing. It is therefore a feature of this invention that it provides an improved pylon design for elevated cableway systems. It is furthermore a feature of this invention that the improved pylon design reduces wear on the catenary cable system by not allowing the catenary cable system to slide or roll directly on the top of the pylon. It is a further feature that the improved pylon includes a new, deflecting upper saddle to support the catenary cable system while relieving stresses imposed on the catenary cable system by deflecting under load applied by the vehicle traversing the track cable system. It is a still further feature that the improved pylon includes an improved, pivotable lower saddle to better transmit forces and distribute load stresses through the cableway system as the vehicle traverses the cableway. It is furthermore a feature that load stresses are distributed through improved hanger and spacer designs. It is still furthermore a feature that it provides an improved cableway system with greater lateral support for the union between the catenary and track cable systems by providing improved force equalizing assemblies. It is still furthermore a feature that it provides an alternate force equalizing assembly that reduces wear on the catenary cable system and the track cable systems by allowing the cables to controllably yield relative to one another as force is transferred between them. SUMMARY OF THE INVENTION The features described above, as well as other features and advantages, are provided by an improved cableway system that includes a pylon, an upper saddle, and a lower saddled as defined by appended claim 1. The pylon includes a base pylon, and the lower saddle is mounted to the base pylon from which a track cable may be strung. The upper saddle, from which a catenary cable system may be strung, is movably mounted to the base pylon to deflect in response to the weight of a vehicle traversing the track cable systems. BRIEF DESCRIPTION OF THE DRAWINGS A more particular description of the invention briefly summarized above can be had by reference to the preferred embodiments illustrated in the drawings in this specification so that the manner in which the above cited features, as well as others that will become apparent, are obtained and can be understood in detail. The drawings illustrate only preferred embodiments of the invention and are not to be considered limiting of its scope as the invention will admit to other equally effective embodiments. In the drawings: Figures 1-5 illustrate a prior art cableway system disclosed and claimed in United States Letters Patent 4,069,765 issued January 24, 1978 to Gerhard Müller and correspond to Figures 3-7 therein. Figure 6 illustrates the pylon of the inventive cableway system described herein, including an upper saddle and a lower saddle, in elevation. Figures 7A-G illustrate the upper saddle of the new pylon; Figure 7A is a side, elevation view; Figure 7B is a broken isometric view; Figures 7C-D are elevation and plan views, respectively, of the base of the upper saddle in partial section. Figure 7H illustrates an elevation view of the lower saddle of the pylon in Figure 6; Figure 7I is a plan view of Figure 7H; Figure 7J is a plan view taken along section 7J-7J in Figure 7H; Figure 7K is an elevation view taken along section 7K-7K in Figure 7H; Figure 7L is an elevation view taken along 7L-7L in Figure 7H. Figures 7M-N and 7P illustrate the transverse connecting frame and main beam of the lower saddle; Figure 7M is a partial elevation view; Figure 7N is a side elevation view taken along section 7N-7N in Figure 7M; Figure 7P is a partial plan view of Figure 7M; and Figure 7Q is an elevation view taken along section line 7Q-7Q of Figure 7M. Figures 7R-7U illustrate the tertiary beams and suspension rod/cross tie assemblies of the lower saddle; Figure 7R is an elevation view; Figure 7S is a side elevation view taken along section 7S-7S in Figure 7R; Figure 7T is a side elevation view taken along section 7T-7T in Figure 7R; Figure 7U is a plan view taken along section 7U-7U in Figure 7R. Figures 7V-7X illustrate the equalizing beam of the lower saddle; Figure 7V is an elevation view; Figure 7W is a plan view of Figure 7V; Figure 7X is a side elevation view taken along section 7X-7X in Figure 7W. Figure 7Y is a side elevation view of an alternate embodiment of the lower saddle connected to a tubular pylon support beam with stabilizing shock absorber and bracing rods added. Figure 7Z is a partial isometric view of the alternate embodiment of the lower saddle connected to a tubular pylon support beam. Figure 7AA is a side elevation view of a support pylon showing an upper saddle supported by a tubular base pylon that has an opening in an upper end through which a lower end of an upright extends. Figures 7AB-7AE illustrate an alternate upper saddle that supports a catenary cable on top of a base pylon through a set of cable clamping wheel assemblies; Figure 7AB is a side elevation view of the alternate upper saddle mounted on top of a base pylon; Figure 7AC is an end elevation view of one of the cable clamping wheel assemblies supported atop a roller base and wheel bearing members; Figure 7AD is a plan view of one of the cable clamping wheel assemblies; Figure 7AE is a side elevation view of one of the cable clamping wheel assemblies. Figures 8A-B illustrate the hangers, cross-ties, and rails of the track cable systems in the new system in an isometric view; Figure 8A in partially exploded perspective and Figure 8B is in elevation. Figures 9A-B illustrate the hangers, cross-ties, and power rail of the new system in section along line 9A-9A of Figure 8B and in partial cutaway; Figure 9A shows a horizontal section of the catenary cable system; and Figure 9B shows an inclined section of the catenary cable system. Figures 10A-C illustrate the cross-ties, cables, and rails of the track cable systems in the new system; Figure 10A in a top view with ghosted lines; Figure 10B in section along line 10B-10B in Figure 10A and in partial cutaway; and Figure 10C in an end view. Figures 11A-D illustrate a force equalizing assembly tying the catenary and track cable systems at intermediate points in the span. Figure 11E shows an isometric view of an alternate force equalizing assembly. Figures 11F-11L show a second alternate force equalizing assembly; Figure 11F shows an isometric view of the second alternate force equalizing assembly; Figure 11G shows a cross-section through a middle portion of the force equalizing assembly; Figure 11H is a cross-section taken along line A-A as shown in Figure 11G; Figure 11I is a cross-section taken along line B-B as shown in Figure 11G; Figure 11J is a plan view of a portion of the force equalizing assembly; Figure 11K is a cross-section taken along line C-C as shown in Figure 11J; Figure 11L shows an end elevation view of the second alternate force equalizing assembly. DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 6 illustrates one of pylons 17 in a preferred embodiment of the elevated cableway system, including upper saddle 30 from which catenary cable system 16 is strung, lower saddle 200 from which track cable systems 14 are strung, and base pylon 21 on which lower saddle 200 is mounted. Hangers 27 suspend track cable systems 14 from catenary cable system 16 and pre-tension track cable systems 14, as described above. Pylon 17 is attached to ground 19 by any suitable technique known to the art. The precise dimensions of pylon 17 such as height and width will be matters of engineering design predicated on well known structural principles to account for structural loads, such as vehicle and cable weight, and for loads arising from environmental conditions such as wind, seismic activity, precipitation and temperature. Upper saddle 30, shown in greater detail in Figures 7A-C, permits relatively free motion at the top of pylon 17, and transmits vertical loads from vehicle 12 and pre-tensioning forces to pylon 17. Upper saddle 30 lessens fatigue of catenary cable system 16, requires only limited maintenance, and eases implementation of a desired 7° deviation of pylon 17. Upper saddle 30 comprises upright 32 pivotably mounted to base 34 and'is capped by coupling 40, which is engaged with cable connector 42. Turning now to Figure 7B, coupling 40, cable connector 42, and pin 44 atop upper saddle 30 are shown in an enlarged, partially cutaway view. Supports 50 help bear and distribute the load on coupling 40 to upright 32. Cover 52 provides some protection for coupling 40 and connector 42 from the elements. The socketing and pinned connection of coupling 40 engaged with cable connector 42 reduces the risk of fatigue to catenary cable system 16 caused by the shifting of catenary cable system 16 across pylon 18 of the system in the Müller '765 patent. The embodiment of Figures 7A-C thereby reduces the risk of fatigue failure in catenary cable system 16 by precluding bending fatigue stresses, thus leaving only tension-tension fatigue stress on catenary cable system 16. This connection also permits shorter cable lengths to facilitate transportation, handling and construction of the system. Coupling 40 in the preferred embodiment is a welded plate assembly including base plate 46 and at least two member plates 48 extending substantially perpendicularly from base plate 46 as shown in Figure 7B. Cable connector 42 is socketed on one end to engage coupling 40. Pin 44 joins cable connector 42 to coupling 40 through co-aligned holes in tines 43 of forked connector 42 and coupling 40 when cable connector 42 and coupling 40 are engaged. The socket and pin connection provided by cable connector 42 must be strong enough to sustain the load on catenary cable system 16 and the loads from environmental conditions. Cables 16a-b are strung in a first direction from the non-connected end of cable connector 42. Coupling 40 is also joined to a second cable connector 42 that provides cable connection to cables 16a-b in a second direction, as shown in Figure 7B. Cables 16a-b are preferably clamped together as shown in Figure 7E at predetermined intervals using clamps 49 between cable connector 42 and the first one of hangers 27. Clamps 49 are better illustrated in Figures 7F-G and comprise pins 51 joining clamp members 53a-d. Clamp members 53a-d define passages 55a-b through which cable members 16a-b pass. Passages 55a-b may include flared openings on one or both ends thereof as are discussed in connection with catenary cable clamp 85 and equalizing lock 300. The flared openings of passages 55a-b are best shown in Figure 10C, wherein the lesser diameter at point 57 of passages 55a-b forms the throat of the opening and the greater diameter at point 59 forms the flare. These flared openings minimize the "beam effect" wherein a clamped cable behaves structurally as a beam. Still referring to the Figure 7B, upright 32 is pivotably mounted to double V-shaped base 34. Base 34, like coupling 40, in the preferred embodiment is a welded plate assembly and comprises bottom plate 54 and side plates 56. Side plates 56 are attached in slotted channels at each end of bottom plate 54, as shown in Figure 7C to define slots into which tongues 58 extend from the bottom of upright 32. Pins 60, preferably constructed from brass to reduce friction, run through co-aligned holes in side plates 56 and tongues 58. Upright 32 supports forces received through coupling 40 and transmits them to pins 60 about which upright 32 rotates. Base 34 also includes additional means for bearing the load of upright 32. Each of these means includes a bearing pin 62 extending through a split flanged sleeve 64 and 66. Flanged sleeves 64 extend from tongues 58, and flanged sleeves 66 are welded to the interior surfaces of paired side plates 56. Bearing pin 62 is held in place by threaded nuts about pin 62 both above and below sleeve 64, and reciprocates in sleeve 66. The design of upper saddle 30 described above essentially implements a "pulley". Pins 60 are the center of rotation for this "pulley" and the length of upright 32 defines its radius. The "pulley" diameter may be variable and, in the preferred embodiment, is 150 times the diameter of catenary cable system 16. Although the design handles forces conceptually as does a pulley, there are obvious structural differences. For instance, rotation of upright 32 about pins 60 is constrained to a 7° deviation from the vertical norm. This rotation in upper saddle 30 prevents the introduction of high moments to pylon that are 17 present for the rigid pylons 18 of the system disclosed in the Müller '765 patent. In the preferred embodiment, lower saddle 200 is designed to accommodate deflection of upright 32, and transmit the vertical and lateral loads applied across a portion of track cable systems 14 to pylon 17, which ultimately transmits the loads to the ground. In this manner, the lower saddle transmits loads developed by vehicle 12, cables 14, the environmental conditions, and deviation of upper saddle 30 (up to 7 degrees each direction). Furthermore, lower saddle 200 provides for a smoother transition from one pylon span to another than previously available, and increases the comfort of the vehicle's passengers by reducing the curvature of track cable systems 14. Lower saddle 200, represented in detail by Figures 7H-7X, is connected to pylon base 21 beneath pylon upright 32 by way of transverse pylon beam 202, that is mounted transversely to and extends outwardly from either side of base pylon 21. This connection between the lower saddle and pylon base 21 is also illustrated in Figure 6. U-shaped transverse connecting frame 204 is connected to one end of transverse pylon beam 202 and extends downwardly therefrom to accept and transmit lateral and vertical forces to pylon 17. A second identical transverse connecting frame extends downwardly from the other end of transverse pylon beam 202, providing a second guideway on the other side of each pylon, but only one such frame 204 will be discussed herein to avoid redundancy. With reference to Figures 7M and 7N, transverse connecting frame 204 includes two vertical suspension beams 206A, 206B connected to transverse pylon beam 202 and extending downwardly therefrom. Suspension beams 206A and 206B are connected by horizontally positioned transverse beam 208 by way of bolted connections 208A. Webs 210 are welded to and extend vertically across transverse support beam 208 for added stability. Bearing plates 212A and 212B are welded to and extend upwardly from transverse support beam 208. The assembly of the horizontal and vertical beams, and other associated hardware thus forms the structural skeleton of transverse connecting frame 204. An alternate means of connecting a lower saddle to a base pylon beam 201, functionally similar to support beam 208 described above, is illustrated in Figures 7Y and 7Z. At least one pair of connecting plates 203 is attached to the base pylon beam to substantially encase the base pylon beam. Cap plate 207 is connected to the top of connecting plates 203. An upper attachment plate 209 is removably connected to cap plate 207 by a plurality of bolts. The attachment plate is fixed to bearing plates 212A and 212B in a manner similar to the attachment of bearing plates 212A and 212B to the transverse support beam described above. A hanger plate 211 is connected to the bottom of connecting plates 203. The hanger plate is fitted with holes to accept bolts to removably connect additional structure as described below. A vertical load transmission system is pivotally connected to transverse connecting frame 204, shown in Figure 7M, or alternatively to base pylon beam 201, shown in Figure 7Y, for transmitting vertical loads developed by the vehicle and cables, as well as those loads developed by deflection of the upper saddle, to base pylon 21. A primary requirement of the vertical load transmission system is that vertical loads transmitted by the system should be well distributed over a portion of the track cable systems to avoid damaging curvilinear deflections in the cables. Accordingly, the vertical load transmission system is preferably an isostatic system of interconnected beams and bars arranged in a hierarchical manner. More specifically, with reference to Figures 7H and 7L, main beam 214 is a welded plate assembly formed in rectangular cross-section, and is pivotally mounted through its side walls at the center of its longitudinal axis to bearing plates 212A and 212B for rotation in a vertical plane. Main beam 214 is bi-symmetrical and has a variable height defined by a sloped upper surface that peaks at its center directly above its pivotal mounting point and slopes downwardly towards its ends 214E. Lower surface 214L of the main beam is flat and extends horizontally between ends 214E. Dumbbell-shaped collar 216 is mounted at its disc-like ends 216A and 216B across the sides of the main beam in circular openings 218A and 218B, respectively, as shown in Figures 7N. Shaft 220 is mounted through the longitudinal axis of collar 216 and extends out of ends 216A, 216B through cylindrical openings 220A and 220B therein, respectively. The ends of shaft 220 further extend through openings 222 and associated radial bearings 222A in bearing plates 212A and 212B of the transverse connecting frame, as indicated in Figures 7H and 7N, thereby supporting the main beam for rotation relative to the pylon. Bearings 222A are bronze to reduce friction. A pair of secondary beams 224 are pivotally mounted at the centers of their respective longitudinal axes to flanges 226 connected to and extending downwardly from locations near the respective ends 214E of the main beam, enabling rotation of the secondary beams relative to the main beam in the same vertical plane that the main beam is rotatable within. Flanges 226 are equipped with openings 232A and 232B, respectively, for mounting shafts 234 therein, as displayed in Figures 7L and 7Q. Shafts 234 pass through discs 236A and 236B mounted within circular openings in respective secondary beams 224, pivotally connecting the secondary beams to flanges 226 near each end of the main beam. Rings 230 retain shafts 234 in place. Like main beam 214, the secondary beams are formed of a welded plate assembly that results in a variable height and a rectangular cross-section. Four tertiary beams 238 are each pivotally mounted at the center of its longitudinal axis to one of respective secondary beams 224 substantially at a respective end of the secondary beam for rotation in the same vertical plane that the main and secondary beams are rotatable within. Referring to Figures 7S and 7U, tertiary beams 238 carry collars 240 in circular openings 240A. These collars are aligned with two respective sets of complementary discs 242A and 242B, one set of discs 242A, 242B being mounted in circular openings near each end of secondary beams 224. Shafts 244 extend through aligned openings in the respective disc-collar-disc assembly 242A, 240, and 242B to pivotally connect the centers of tertiary beams 238 to the respective ends of secondary beams 224 in a conventional manner. The end portions of the upper and lower faces of secondary beams 224 are cut open somewhat to permit unimpeded movement of tertiary beams 238. Eight suspension rods 246 are each pivotally mounted at their upper ends to each of respective ends 238E of the tertiary beams for rotation in the vertical plane. Bolts 248 pass through circular openings in each of the suspension rod halves 246A, 246B as well as a circular opening in each of the ends of tertiary beams 238. Cylindrical bearings 250 are positioned about bolt 248 to facilitate relative rotation between the suspension rods and the tertiary beams, and to maintain the spacing between the suspension rod halves. Similar bearings are provided at other interfaces where components rotate relative to one another throughout the lower saddle, in conventional fashion. The other end of each suspension rod 246 is pivotally connected to a cross-tie 256 by way of flange 258 that extends upwardly from connecting plate 259. Cross-ties 256 function to transmit vertical and lateral vehicle loads to the vertical and lateral load transmission systems, via the engagement of the vehicle wheels with the rails carried by the cross-ties. Connecting plate 259 is bolted via four bolts 259A about the intersection of the cross-tie's longitudinal axis with the axis of an equalizing beam (described below), enabling rotation of cross-ties 256 in the vertical plane relative to the suspension rods. As shown in Figure 7H, bolts 259A actually consist of four sets of bolts of varying lengths to accommodate the differing thicknesses of the equalizing beam across lower saddle 200. Bolts 252 pass through circular openings at the bottom of suspension rod halves 246A, 246B and openings through flanges 258. The suspension rod halves are connected with welded web 257 that effectively provides an I-section to minimize the risk of instability in the suspension rods. Cylindrical bearings 254 again facilitate relative rotation and maintain the spacing between the suspension rod halves. Rod halves 246A, 246B are enlarged at each of their ends for the pivotal connections to the tertiary beams and the cross-ties, respectively, as shown in Figure 7R. This rotation of the suspension rods at both ends prevents the rods from taking any moment due to lateral forces which, as explained below, are devoted to the equalizing beam. In another preferred embodiment of the vertical load transmission means of the lower saddle, shown in Figures 7Y and 7Z, bracing rod pairs 247 and shock absorbers 249 are added to alternate tertiary beams 239 and suspension rods 246 to further dampen the impact of vertical loads applied to the track cable systems by dampening the rate at which the suspension rods and the tertiary beams rotate relative to one another. The figures disclose an embodiment wherein the secondary and tertiary beams have hanger plates being used to connect lower members to higher members. Secondary hanger plate 229 is shown suspended from alternate secondary beam 225 to support alternate tertiary beam 239. Tertiary hanger plates 241 are shown suspended from alternate tertiary beam 239 to support suspension rods 246. Additionally, sets of suspension rods 246 are used rather than single suspension rods 246 at each end of each tertiary beam. Bracing rod pairs 247 have holes at either end through which bolts 253 pass, thereby pivotally connecting the bracing rods to the rest of the assembly. The end of shock absorber 249 adjacent to the lower end of the suspension rods is also pinned by bolt 253 to pivotally connect the shock absorber to the suspension rods 246, bracing rod pair 247, and alternate cross-ties 255. The alternate cross-ties are substantially similar to cross-ties 256 described below, but have two flanges 258 rather than one, as shown in Figure 7T. The additional flange enables attachment of a shock absorber between the flanges, as seen in Figure 7Z. The opposite end of the shock absorber, i.e. the upper end, is pivotally connected to the adjacent tertiary beam by pinning the shock absorber with bolt 251 through tertiary hanger plates 241 and suspension rods 246. Those skilled in the art will appreciate that bracing rod pairs 247 and shock absorbers 249 could be appended to the first disclosed beam and hanger arrangement. Cross-ties 256 are different from cross-ties 25 on the pylon spans, which are described below. Cross-ties 256 transmit an upward vertical force to the track cable systems to support them at intermediate points between pylons. Cross-ties 25 transmit an upward vertical force to the track cable systems to support them from the lower saddle 200. Referring to Figure 7X, cross-ties 256 include flat plates 257 to which grooved blocks 257A are welded to serve as a bearing for track cable systems 14. A rail is provided in the form of a second grooved block R that is used to clamp the carrier cables to cross-ties 256. Three rows of bolts are used to secure grooved blocks R to flat plate 257, as shown in Figure 7W. Interim cable track support sections 257A' are provided between cross-ties 256 and are connected to grooved blocks 257A to form a continuous bearing cradle for track cable systems 14. Grooved blocks R are butterfly shaped, as viewed in Figure 7I, resulting from symmetrical grooves cut into each end. Interim rail sections, not shown, having tongued ends for engaging the grooved ends of the blocks R and are connected thereto to form a continuous rail for supporting the vehicle wheels along the length of the lower saddle. Lower saddle 200 further includes a lateral load transmission system that contains equalizing beam 260 carried across the cross-ties 256, and lateral support stud 282 carried by transverse connecting frame 204, as shown in Figures 7H and 7V. Thus, equalizing beam 260 spans transversely across the lower saddle's cross-ties 256 to transmit lateral forces to lateral support stud 282. The equalizing beam further serves to stabilize suspension rods 246 in the face of lateral forces. The equalizing beam must be flexible in the vertical direction so that the vertical load transmission system operates effectively as an isostatic system, but also must be reasonably stiff in the lateral direction to transmit lateral forces. To meet these seemingly contradictory requirements, equalizing beam 260 includes superimposed plates 264, 266, 268, and 270 of different lengths and thicknesses, as displayed in Figures 7V and 7W. Thus, plate 264 is shorter than plate 266, which is shorter than plate 268, and so forth. Also, as particularly shown in Figure 7W, the widths of the plates are greatest at the center of their longitudinal axes and decrease along the lengths of the plates towards each of their ends. This variable width, plus the variable thickness of the super-imposed plate stack, decreases the lateral and vertical moments of inertia of the equalizing beam at its end where bending strength is least needed. Lateral and vertical loads are transmitted at cross-ties 256 by four bolts 259A that connect the cross-ties to both the vertical and lateral load transmission systems, which operate independently from one another. Thus, as explained above, cross-ties 256 are connected to suspension rods 246 and equalizing beam 260 using bolts 259A. Referring to Figures 7R and 7T, the bolts are fixed in threaded holes 259B in the cross-ties for better transmission of lateral forces than if secured with nuts. The plates of equalizing beam 260 are joined together near their centers by bolting the plates together along with the center-most cross-ties 256 and suspension rods 246 using bolts 259A, as displayed in the left-most equalizing beam 256 of Figure 7W. The plates of the equalizing beam should otherwise, i.e., outside of the center, be free to move longitudinally. This freedom of movement is realized by using a teflon coating between the plates that provides for maximum vertical flexibility, and by making the bolt holes in the plates that are aligned with the other cross-ties slotted in the longitudinal direction. Bolt sleeves 259B are provided in these slotted bolt holes that are slightly taller than the equalizing beam's plate stack to avoid clamping the plates outside of their centers, as shown in the lower portion of Figure 7R. This allows vertical loads that are transmitted from cross-ties 256 to suspension rods 246 to effectively bypass equalizing beam 260. Referring to Figure 7N, the lateral load transmission system is further connected to transverse connecting frame 204 and extends downwardly therefrom in the form of lateral support stud 282 to provide for lateral rigidity of the track cable systems and to sustain loads due to environmental conditions. Lateral support housing 276 is connected to and extends downwardly beneath transverse support beam 208. Lateral support stud 282 is encased within housing 276 and extends downwardly through the center thereof. The lower portion of steel lateral support stud 282 is tapered and extends downwardly through respective aligned grooves 286 formed through clamping plates 262 as well as each of the plates of the equalizing beam, as shown in Figures 7J and 7K. External contact faces of the stud are chromium plated, and are capped with plates 282A made of a hardened steel material, e.g., quenched and tempered steel. Clamping plates 262 are provided with guide blocks 284 for engaging lateral support stud plates 282A and limiting the motion of stud 282 within groove 286 to linear motion along the axis of the equalizing beam. Guide blocks 284 are also made of a hardened steel material in order to sustain the high contact pressure at the lateral support stud plates. A plurality of bolts 286A are positioned in aligned bores through the assembly of clamping plates 262, guide block 284, and equalizing beam 260 about grooves 286 and secured with nuts to clamp the assembly. In this manner, lateral movement of the cross-ties, as well as track cable systems 14 supported at each of the ends thereof, is controlled. Thus, lateral loads resulting from environmental conditions and deviation (up to 7 degrees either direction) of the upper saddle are applied through cross-ties 256 and equalizing beam 260 to lateral support stud 282. The lateral forces are then transmitted through transverse connecting frame 204 or alternatively to base pylon beam 201, which carries the lateral support stud, to the base pylon. In the alternate means of connecting a lower saddle to a base pylon beam 201 as describe above in association with Figures 7Y and 7Z, the support stud 282 is also employed. The support stud is fixed to a lower attachment plate 281. The lower attachment plate has holes to align with the holes in hanger plate 211, and by receiving bolts through those holes is removably affixed to the hanger plate and thus to pylon beam 201. As in the first described attachment of the lower saddle, housing 276 is used to provide lateral support to support stud 282. Referring again to Figures 6 and 7B, upper saddle 30, which is pivotable on pins 60 and includes upright 32, constitutes a yieldable leg deviating from a strict vertical orientation in response to loads on catenary cable system 16 up to 7° either direction. When engaged with coupling 40 and joined by pin 44, cable connectors 42 can rotate relative to coupling 40. The relative rotation of cable connectors 42 and coupling 40 is a response to loads on upper saddle 30 received via catenary cable system 16, and permits deviation of the yieldable leg. As stated above, bottom saddle 200 is designed to accommodate this deviation and, through equalizing beam 260, to: (1) minimize in-plane rigidity; and (2) provide lateral rigidity to sustain environmental loads and forces of pylon 17's deviation from the strict vertical orientation. Through this yieldable leg and bottom saddle described above, the present invention contravenes the art by providing self-adjusting pylons 17, and provides for a smooth transit of vehicle 12 across the system in accordance with regulatory guidelines. The present invention also contemplates two additional embodiments of the upper saddle and base pylon combination. Figure 7AA shows one alternate embodiment. Therein, tubular upright 33 is supported by tubular base pylon 23 that has an opening in its upper end through which a lower end 35 of the upright extends. The arrangement permits rotation of upper saddle 31 in response to forces applied to the catenary cable system, but limits the rotation by interference of lower end 35 of upright 33 against the inside of tubular base pylon 23. Coupling 41 is substantially similar to coupling 40 disclosed above. Figures 7AB-7AE illustrate a second alternate embodiment of the upper saddle and base pylon. As shown in Figure 7AB, a base pylon 29 supports an upper saddle composed of a bearing assembly 135 and cable attachment assemblies 140. Bearihg assembly 135 is composed of base plate 136 that provides holes for receiving bolts to connect to base pylon 29 below, and a platform for connection of additional components above. Support member 137 extends vertically from base plate 136 to provide vertical separation between the base plate and catenary cable system 16 supported above. Roller base 138 is supported on top of support member 137 to provide a surface that defines a pattern of travel of cable attachment assemblies 140 above. In the embodiment shown, the pattern of travel defined is a curvlinear pattern approximating the natural curve of catenary cable system 16 under a given load. Figure 7AC shows two crane rails 139 supported on top of roller base 138 to provide wheel-bearing surfaces on which cable attachment assemblies 140 can travel. The components of cable attachment assemblies 140 are illustrated in Figs. 7AC-7AE. Each cable attachment assembly is supported on crane rails 139 by wheels 141 which are coaxially attached to axle 142. Axle 142 is attached to additional components used to clamp the catenary cable system by axle retainers 143. Axle retainers 143 are bolted to upper channel members 144. Upper channel members 144 are welded to a plate 146 and angles 147 to make up the upper one half of the components used to clamp the catenary cable system. Lower channel members 145 are similarly welded to a plate 146 and angles 147 to form the lower half of the components used to clamp the catenary cable system. The upper and lower halves are bolted together through angles 147 at their ends and through plates 146 near their centers. Teflon linings 148 are fitted around the catenary cable system 16 (cable 16a and 16b) between the two halves so that when the bolts connecting the two halves are tightened, adequate pressure will be exerted on the catenary cables to connect the cables to the cable clamping assemblies. However, the flexibility of the teflon will be relied upon to ensure that the applied pressure will not be so great as to crush or damage the cables. The cables, rails, and cross-ties of the elevated cableway system are illustrated in Figures 8A-10C. Figure 8A is an isometric, partially exploded view of hangers 27a-b, cross-ties 25, and carrier rail 14 of the present invention that replace the counterparts in the Müller '765 patent depicted in Figure 2. Figure 8B is a frontal, elevation view of long hanger 27a and cross-tie 25 and shows the relationship of vehicle 12 to one such hanger/cross-tie combination in ghosted lines. Figures 9A and 9B provide additional views of hanger 27a: Figure 9A in section and partial cutaway along line 9A-9A of Figure 8B; and Figure 9B in section along line 9B-9B of Figure 9A. Figures 10A-C depict rail 100, cables 14c-d, and cross-tie 25. Figure 10A is a partial top view, Figure 10B is a section taken along line 10B-10B of Figure 10A in partial cutaway, and Figure 10C in a front view of rail 100 and bottom guide 102. Returning to Figure 8A, two alternative embodiments for hanger 27 are shown: long hanger 27a and short hanger 27b. As is shown in Figures 2 and 4, both long and short hangers are used depending on the hanger's distance from pylon 17 and span midpoint 22. In addition to differing lengths, hangers 27a-b differ in that hanger member 91 of hanger 27a is a locked-coil steel cable but in hanger 27b is a rod. Furthermore, short hanger 27b can be used in different lengths using the same construction. Two different lengths are used for short hanger 27b in a single 600m span in the preferred embodiment. The length of hangers 27a-b is calculated to pre-tension track cable systems 14 as described above, to transmit vertical, pre-tensioning forces to pylon 17, and to ensure clearance between catenary cable clamp 85 and vehicle 12 in high winds, and so the length thereof will depend on the particular application for a given embodiment. The effective length of hangers 27a-b can be adjusted by tightening and loosening nuts 70 and 72 on threaded end 68 of hanger member 91 described below to adjust the pre-tensioning forces. The length of the threads on threaded end 68 must consequently be sufficient to accommodate the desirable range of tensions. In long hanger 27a, this will nominally be a 0-300mm and in short hanger 27B the length will vary but be at least greater than 50mm. Hangers 27a-b are suspended from catenary cable system 16 by clamping cables 16a-b in openings 87a-b of suspension clamp 85 shown in Figure 8A. Suspension clamp 85 is pivotably mounted to hanger member 91 at pivot 76. Suspension clamp 85 comprises first guide member 86 bolted to lower guide member 88 as shown in Figures 9A-B. Suspension clamp 85 includes passage 106 through which threaded end 68 of hanger member 91 extends, and block 78 joined to first guide member 86 at pivot 76 such that catenary cable system 16 and suspension clamp 85 may pivot relative to hanger member 91 16° relative to the horizontal normal as shown in Figure 9D. Block 78 includes a bore through which threaded end 68 of hanger member 91 extends. Block 78 rests on a shoulder formed on threaded end 68 and is secured thereagainst by nuts 70 and 72 and washer 74. Disadvantages to the clamping of cable 16 typically include cable fatigue and the "beam effect", in which cable behaves structurally as a beam. Suspension clamp 85 minimizes these disadvantages by including flared openings 89 in grooves 87a-b as shown in Figures 9A-9B. Flared openings are also employed in equalizing locks 300 discussed below and shown in Figures 11A-D. Hanger member 91, as shown in Figures 8A-B, of long hanger 27a is jointed and includes upper piece 92, essentially a threaded fork member, and lower piece 94, a steel cable, moving relative to one another at joint 96; hanger member 91 of short hanger 27b is not jointed. The articulation provided by joint 96 and pivot 76 provides flexibility in hanger 27a that will reduce bending moments therein resulting from the loads of power rail 90 and vehicle 12, as well as other forces. Hence, the elimination of joint 96 in hanger 27b, in which bending moments are of less concern because of the shorter length of hanger member 91, and the inclusion of pivot 76, permit the suspending of hanger 27b from catenary cable system 16. Referring still to Figures 8A-B, cross-tie 25 is an asymmetric I-beam mounted to the hanger member 91 at pivot 98 at collar 93 of hanger member 91 distal to catenary cable system 16 in both long hanger 27a and short hanger 27b. Pivot 98 is a cylindrical plain bearing providing flexibility and thereby reducing flexural effects in cables 14 and 16. Cross-tie 25 is preferably constructed from cast steel and is I-shaped in cross-section as shown in the isometric view of Figure 8A and in the cross-sectional view of Figure 10B. Openings 95 are either cast or milled in cross-tie 25 to reduce weight and, consequently, the load on catenary cable system 16. Cables 14a-d of track cable systems 14 are shown in ghosted lines in Figure 8A. Track cable guides 102 comprising bottom guide members 104 and rails 100, joined as shown more fully in Figures 10A-C, are mounted to opposite ends of cross-tie 25 as shown in Figures 8A-B. Guide members 104 may be either formed integrally with or bolted to cross-tie 25 as best shown in Figures 10B and 10C by bolts 114 extending through bores 116 and secured by nut and washer combinations 118. Still referring to Figures 10A-C, rails 100 are then mounted by mating bolts 114 with slot 120 in rail 100 and sliding rails 100 until properly positioned as shown in Figure 10C. When rails 100 are properly positioned relative to guides 104, rails 100 and guides 104 define grooves 122 shown in Figure 10C through which cables 14a-d are strung as shown best in Figures 10A-B and in ghosted lines in Figure 8A. Rails 100 constructed of aluminum comprise modular segments that typically are sufficiently large to span the entire distance between hangers 27. Although one end of each segment will be relatively fixed in position by the mating of bolts 114 to slot 120 as discussed above, the other end will be softly, rather than rigidly, fixed by the mating of grooves 122 with cables 14a-d. The movement thereby permitted accommodates thermal expansion of the segments and is therefor desirable. Thus, thermal expansion joints 127 are created between rail segments such as joint 127 between segments 129 shown in Figures 8A, and 10A-B. Joints 127 are preferably angled at 45° relative to the longitudinal axis of rails 100. Rails 100 also include upper surfaces 132 and sides 134 providing a smooth and gliding surface for vehicle 12 in the preferred embodiment as discussed below. Although not shown, the preferred embodiment includes a layer of insulation between rails 100 and cables 14a-d to avoid corrosion and reduce noise. Other modifications may be employed in the design of rails 100. For instance, holes 124 are milled into individual segments of rails 100 to decrease weight and the heads of bolts 114 need not be of uniform height above cross-tie 25 if it is desirable to incline segments of rails 100. One may furthermore provide some means for heating rails 100 for use in particularly cold climates. These and other such modifications are contemplated by and are within the scope of the invention. As is known to those in the art, vehicle 12 must be powered as it traverses the system and so provision must be made for power rail 90 as shown in Figures 8B and 10B. Power rail 90 may be mounted to cross-tie 25 as shown in ghosted lines in Figures 8B and 10B. Power rail 90 is grasped by power rail guide 84 bolted to plate 112, which in turn is bolted to the bottom of cross-tie 25. As shown in Figure 8B, a power rail 90 and power rail guide 84 are preferably mounted to each end of cross-tie 25 in this embodiment. Also as is known in the art, power rail 90 must be electrically insulated from all other parts of the system for safety reasons. The relation of vehicle 12 to the combination of hanger 27, cross-tie 25, and track cable systems 14 is best illustrated in Figure 8B. Carrier wheels 126 mounted on either side of the vehicle above its roof 128 in any convenient manner rotate in the vertical plane, ride on the upper surface 132 of rails 100, and carry the weight of vehicle 12. Guide wheels 130 rotate in the horizontal plane, contact sides 134 of rails 100, and maintain the lateral position of vehicle 12 vis-a-vis the carrier rails. Referring now to Figures 11A-D, force equalizing assembly 300, also known as an equalizing lock, is provided for joining catenary cable system 16 to track cable systems 14 between the pylons to equalize the tension between the catenary and track cable systems. Force equalizing assembly 300 substantially prevents relative movement between catenary cable system 16 and track cable systems 14 and distributes forces therebetween through friction on the cables. As such, the force equalizing assembly reduces the maximum deflection of the guideway by impeding relative movement between the cables. Force equalizing assembly 300 includes force equalization plate 302 having three sets of parallel channels formed along the length of the upper surface thereof for accepting catenary cable system 16 in the center two channels 302B and track cable systems 14 in the outer four channels 302A. Thus, the channels are shaped to approximate one-half of the respective cable circumferences except that the ends of the channels are flared outwardly, as illustrated in Figures 11C and 11D. Clamping plate 304 also has three sets of parallel channels that are formed along the length of the lower surface thereof for accepting catenary cable system 16 in center channels 304B and track cable systems 14 in outer channels 304A. Like the channels of the force equalization plates, the channels of the clamping plates are shaped to approximate one-half of the respective cable circumferences except that the ends of the channels are flared outwardly. As shown in Figures 11C and 11D, the channeled surfaces of respective force equalization plates 302 and the clamping plates 304 are complementary such that the plates may be assembled about the cables for frictionally locking the cables within the respective channels to equalize the tension in the catenary and track cable systems. The respective flared ends of the channels in the assembled plates form a frusto-conical cavity in each end of the assembly about each of the cables for reducing wear on the cables by limiting engagement, and therefore bending stresses, with the ends of the plates, a feature lacking in the Müller disclosure. The flared ends are defined by narrower diameter 307 and greater diameter 309 in the opening of the channel through the assembly as best shown in Figure 11D. Plates 302, 304 are assembled by the insertion of a plurality of bolts 306 through a respective plurality of complementary bores 308 formed in the plates along the sides of the channels. Bolts 306 are high strength bolts to assure the proper tightening force, and are countersunk such that their heads are flush with the upper surface of clamping plates 304. Bolts 306 are retained by respective nuts 310. Flush mounting of the bolts prevents the possibility of the vehicle wheels colliding with one of them. Clamping plate 304 may have an upper surface that is elevated at its center (not shown) above the two center channels 304B to provide a greater cross-sectional area at the areas of greatest stress. The upper surfaces of plate 304 are further adapted for engagement by the wheels of the cable car. The force equalizing assembly interfaces with the rail profile to assure a continuous running track. The rail profile must therefore accommodate the profile, i.e., shape of equalizing lock 300. It follows that the 45° expansion gap in the rail cannot be used at the rail's engagement with the force equalizing assembly. The present invention further contemplates two alternate embodiments of the force equalizing assembly of cable encasing members for connecting and distributing forces between the catenary cable system and the track cable systems. The first alternate force equalizing assembly, or equalizing lock is illustrated in Figure 11E. Several wheel support rails, 350 and 354, have been removed in the figure in order to clearly illustrate the components below the rails. The assembly of cable encasing members is made up of frame 333 with connections thereto. The connections of the cables are made with spelter sockets 334, as shown in the figure, or by any other cable encasing connection known to those in the art. Frame 333 is made up of base frame 336 which is an elongated plate with U-shaped ends 338. U-shaped ends 338 of the embodiment shown consist of legs 340 and 342 which are of different lengths. Because legs 340 and 342 are of different lengths, clearance is created between the connections to allow for less moment stress development at the base of the "U" for a given tensile load on the cables. That is, if the legs were not of different lengths, the connections would be side by side. In order for the side by side connections not to interfere with one another, legs 340 and 342 would have to be farther apart. Because the legs would be farther apart, a greater moment would be created near their respective connections to the rest of the frame. The different length legs avoid this condition. A plurality of askew connection plates 344 extend from the vertical faces of base frame 336 at acute angles to the longitudinal axis of the base frame and provide points of connection for track cable systems 14. On both sides of base frame 336, cross members 346 extend from the face of base frame 336 to carry spacer plates 348 and wheel support rails 350. Bracing bars 352 extend perpendicularly from cross members 346 to provide lateral support for the cross members. Wheel support rails 350 span between cross members 346 and may have spacer plates 348 between the rails and the cross members to give additional elevation to the rails. Wheel support rails 350 typically do not have track cables running underneath them. However, wheel support rails near the transition points where the track cables must pass underneath and into the support rails must be altered to avoid interfering with the track cables. Thus, transition wheel support rails 354 have channels cut in their lower faces and sides to allow passage of the cable of the track cable systems 14 through the sides of the wheel support rails. The second alternate force equalizing assembly is illustrated in Figures 11F-L. As illustrated in Figures 11F and 11G, the assembly of cable encasing members is made up of an assembly body 367, a catenary cable system clamp 370, and a pair of track cable system clamps 368. In a preferred embodiment, assembly body 367 includes of a pair of parallel tubular beams 372 extending the length of the force equalizing assembly that support a plurality of cross extensions that in turn support catenary cable system clamp 370 and track cable system clamps 368. The cross extensions are made up of tubular columns 374, lateral bracing plates 376, span plates 378a-b, and wing plates 380, as shown in Figures 11G and 11I. A plurality of tubular columns 374 extend vertically from tubular beams 372 to support span plates 378a-b. Lateral bracing plates 376 are provided between consecutive tubular columns 374 to provide support to the columns. Span plates 378a-b are connected between laterally adjacent tubular columns 374 to support catenary cable system clamp 370. Span plates 378a are notched to sit on top of tubular columns 374. Span plates 378b are not notched and are attached to the sides of every other laterally adjacent set of tubular columns 374. Span plates 378a are attached to the tubular columns 374 at either end of the force equalizing assembly. Pairs of span plates 378b are therebetween attached to every other laterally adjacent set of tubular columns 374. Pairs of span plates 378a are attached to every other laterally adjacent set of tubular columns not connected by span plates 378b. Catenary cable system clamp 370 slides in catenary clamp grooves 379 between catenary cable reaction plates 382. Catenary cable reaction plates 382 are attached between alternating pairs of adjacent span plates 378a. Therefore, each catenary cable system clamp 370 slides in grooves 379 between every other pair of span plates 378a. Catenary cable springs 384 are placed between catenary cable system clamp 370 and reaction plates 382 to yieldably transfer forces between catenary cable system clamp 370 and reaction plates 382. As illustrated in Figures 11J and 11K, catenary cable reaction plate 382 is made up of inverted T-shaped body 385 and insertable inverted T-shaped wedge 386, each connected to the other by bolts through both of their respective wings. Inverted T-shaped wedge 386 is used to facilitate assembly of the force equalizing assembly. After all of catenary cable system clamps 370 have been put in place about catenary cable system 16 and within assembly body 367, inverted T-shaped wedges 386 are inserted into inverted T-shaped bodies 385 and bolted in place. The function of the wedges is to energize catenary cable springs 384. Those skilled in the art will appreciate that it would not be possible to assemble and adjust catenary cable system clamps 370 about cables 16 if the springs were energized or compressed to workable loads during the assembly process. Therefore, by inserting wedges 386 between catenary cable springs 384 after all of catenary cable system clamps 370 have been put in place in assembly body 367, the force equalizing assembly can be successfully assembled. Continuing now with the description of assembly body 367, wing plates 380 are attached to tubular beams 372 on both sides of the force equalizing assembly to provide support for track cable system clamps 368. Track cable system clamps 368 slides in track cable clamp grooves 381 between track cable reaction plates 388. Track cable reaction plates 388 are attached between alternating pairs of wing plates 380, as seen in Figure 11H. Therefore, each track cable system clamp 368 slides in grooves 381 between every other pair of wing plates 380. Track cable springs 390 are placed between track cable system clamps 368 and reaction plates 388 to yieldably transfer forces between track cable system clamp 368 and reaction plates 388. As illustrated in Figures 11J and 11K, track cable reaction plate 388 is made up of a T-shaped body 391 and an insertable T-shaped wedge 392, each connected to the other by bolts through both of their respective wings. In a manner essentially identical to inverted T-shaped wedge 386 of the catenary cable clamp described above, T-shaped wedge 392 of the track cable clamp is used to facilitate assembly of the force equalizing assembly. As illustrated in Figures 11G and 11I, each catenary cable system clamp 370 is formed by a clamp sliding body 394 and a catenary clamping plate 396. Clamp sliding body 394 and clamping plate 396 have complementary channels in which cables of catenary cable system 16 are secured by bolting body 394 and plate 396 together. Figure 11I also shows a cross-section of catenary reaction plate 382 as formed by inverted T-shaped wedge 386 inserted into inverted T-shaped body 385. Energized catenary cable springs 384 between wedge 386 and catenary cable system clamp 370 are also illustrated. Similarly, as illustrated in Figures 11G and 11H, track cable system clamps 368 are formed by a clamp sliding body 398 and a clamping plate 399. Clamp sliding body 398 and a track clamping plate 399 have complementary channels in which cables of track cable systems 14 are secured by bolting body 398 and plate 399 together. Similar to Figure 11I above, Figure 11H shows arrangements of track reaction plates 388 and track springs 390. With a large cable clamping mechanism such as the force equalizing assembly of the present embodiment, it is problematic that unless the cable slips near the end of a clamp closest to the application of load, the clamping pressure near the farthest end of a clamp cannot be fully utilized. That is, if the clamping pressure near the end of a clamp closest to an applied force is great enough to hold a cable without slipping, the clamping pressure at the end of the clamp farthest from the applied force is not utilized. In the preferred embodiment described here, this limitation is overcome by using a plurality of clamps that intermittently grasp the cables, but are allowed to deflect relative to one another and a fixed body, specifically assembly body 367. The means for accomplishing controlled relative movement among clamps is to place springs between the clamps and the cross extensions of the assembly body. By using springs with different spring constants, different amounts of resistance can be generated between selected clamps. By placing springs with lower spring constants closest to the end of the cable to which load is applied, these clamps will be allowed to deflect more under a given load. Since the clamps on the closest end are allowed to deflect more, more load is passed on to the farther clamps. By'this mechanism the clamping pressures required by the respective clamps are equalized. The arrangement described above is employed both with catenary cable springs 384 and catenary cable system clamps 370, and with track cable springs 390 and track cable system clamps 368. The numbers and spring constants of the various springs would be a matter left to the discretion of the designer for a given set of loadings. A basic problem with clamping cables is that large stresses tend to be generated near the point where a cable exits a clamp. Furthermore, the stress is accentuated if the cable is subjected to lateral loadings that additionally strain the cable at the exit point due to bending induced by the lateral loading. In a preferred embodiment of the present invention, as illustrated in Figures 11F and 11L, an extension member guide 400 is added to the force equalizing assembly to address this problem. Extension member guide 400 is bolted to assembly body 367 at the entry and exit ends of catenary cable system 16. Extension member guide' 400 guides catenary cable system 16 into catenary cable system clamp 370 to reduce the wear on catenary cable system 16 due to combined tension and bending of catenary cable system 16 at the point of entry into catenary cable system clamp 370. In a preferred embodiment, extension member guide 400 is formed by an upper guide 402 and a lower guide 404, the combined profile of the guides fitting around catenary cable system 16. Upper guide 402 and lower guide 404 are formed with complementary holes so that they may be clamped together by a plurality of bolts. The holes formed for catenary cable system 16 through extension member guide 400 are slightly larger than the cables of catenary cable system 16. The purpose of the enlarged holes is to provide for limited clamping of catenary cable system 16 without generating the unwanted stress at the outer ends of the clamp. Extension member guide 400 essentially guides catenary cable system 16 more squarely into catenary cable assembly clamp 370. Thereby, the more extreme stresses developed by combined tension and bending of the cable are not experienced. In a preferred embodiment of extension member guide 400, linings 406 are fitted between guide 400 and cable system 16 to provide limited clamping friction therebetween without inducing wear therebetween. ' It is therefore evident that the invention claimed herein includes many alternative and equally satisfactory embodiments within the scope of the appendent claims. Those of ordinary skill in the art having the benefits of the teachings herein will quickly realize beneficial variations and modifications on the preferred embodiments disclosed herein such as that discussed in the above paragraph. For instance, all cables in the preferred embodiment are locked-coil steel cables because of their high corrosion resistance, density, and moduli of elasticity as well as their lower sensitivity to bearing pressure. However, other types of cables may also be suitable in some embodiments. The preferred embodiments disclosed above must consequently be considered illustrative.

Claims: A system comprising in combination an upper saddle (30,31) and a base pylon (21) for supporting a catenary cable system (16) in an elevated cableway system and providing for deflection of the catenary cable system in response to forces applied by a vehicle (12) traversing a pair of track cable systems supported from the catenary cable system, said pylon being connected to a lower saddle for supporting said pair of track cable systems, the upper saddle comprising a bearing assembly (35,60) affixed to the base pylon (21); and a cable attachment assembly (32,33,40,42) affixed to said bearing assembly to pivot about the base pylon for supporting the catenary cable system yieldably in relation to said bearing assembly. The system of Claim 1, wherein said cable attachment assembly (32, 33, 40,42) comprises: an upright (32,33) pivotably mounted to said bearing assembly (35,60); and a coupling (40,42) mounted to and capping the upright (32,33) for supporting the catenary cable system. The system of Claim 2, further comprising a bearing member (66) for bearing the dynamic loads developed in the upright (32,33) as it deflects in response to forces applied by a vehicle (12) traversing the track cable system (14). The system of Claim 2, wherein said upright (32,33) includes a bearing member (66) for bearing the dynamic loads developed in the upright (32,33) as it deflects in response to forces applied by a vehicle (12) traversing the track cable systems (14). The system of any one of Claims 2 to 4, wherein said coupling (40,42) comprises: a coupling base (46); at least two support members (48) affixed to the coupling base (46) and extending substantially perpendicular from the coupling base (46), the members (48) being spaced apart; a cable connector (42) socketed on one end to engage the support members (48) and pivot relative to said coupling and having a second end adapted to receive the cable. The system of any one of Claims 2 to 6, wherein the upper saddle (31) is supported by a tubular base pylon (23) having an opening in an upper end through which a lower end of the upright (33) extends, and the mounting assembly permits rotation of the upright (33) about a pivot point within the base pylon (23) in response to forces applied by a vehicle (12) traversing the track cable systems (14). A system comprising in combination an upper saddle (135) and a base pylon (29) for supporting a catenary cable system (16) in an elevated cableway system and providing for deflection of the catenary cable system in response to forces applied by a vehicle (12) traversing a pair of track cable systems supported from the catenary cable system, said pylon being connected to a lower saddle for supporting said pair of track cable systems, wherein said upper saddle comprises a bearing assembly (135) and a cable attachment assembly (140); and wherein said bearing assembly comprises: a base plate (136) for connection to an upper portion of the base pylon (29), said base plate (136) providing a platform supporting additional components of the bearing assembly (135); a support member (137) extending vertically from said base plate (136) for providing vertical separation between said base plate (136) and the supported catenary cable system (16); a roller base (138) supported atop said vertical support member (137) for providing a base surface, the top of that defining a pattern of travel of said cable attachment assembly (140) that secures the catenary cable system (16); and at least one wheel-bearing member (139) support atop said roller base (138) for providing a surface on which said cable attachment assembly (140) travels. The system of Claim 7, wherein said cable attachment assembly (140) comprises a plurality of cable clamping wheel assemblies (141,144,145) for clamping onto the catenary cable system (16) relative to said at least one wheel-bearing member (139). The system of Claim 8, wherein said support member (137) extending vertically has an arcuate upper surface for supporting an arcuate roller base (138). The system of Claim 9, wherein said roller base (138) is a plate bent to a curvature complementary with the curvature of said support member (137) to fit atop said support member (137). The system of Claim 10, wherein said at least one wheel-bearing member (139) is a crane rail bent about its major axes to a curvature complementary with the curvature of said arcuate roller base (138) to fit atop said arcuate roller base (138). The system of any one of Claims 8 to 11, wherein each of said cable clamping wheel assembles (141,144,145) for enabling deflection of the catenary cable system (16) relative to at least one wheel-bearing surface comprises: at least one wheel (141); an axle (142) attached to said at least one wheel (141); a cable clamping member (144,145) disposed adjacent to said axle (142); at least one axle retainer (143) attached to said cable clamping member (144,145) and capturing said axle (142) in rotable rotation with said cable clamping member (144,145); and at least one teflon lining (148) that is fitted within said cable clamping member (144,145) and around the catenary cable system (16) that upon completion of said cable clamping member (144,145) provides adequate friction between said teflon lining (148) and the catenary cable system (16) to connect said cable clamping member (144,145) to the catenary cable system (16), without crushing the catenary cable system (16). The system of Claim 12, wherein each cable clamping member (144,145) is constructed of channels, angles, and plates. The system of any preceding claim, wherein the lower saddle (200) is intended for dampening loads applied to the catenary cable system (16) by a vehicle (12) traversing the catenary cable system.

Inventors: AASHEIM PER, LAMOREAUX BEN, PUGIN ANDRE O, WETTSTEIN HANS, AASHEIM, PER, LAMOREAUX, BEN, PUGIN, ANDRE O., WETTSTEIN, HANS
Applicants: AEROBUS INTERNATIONAL INC, AEROBUS INTERNATIONAL, INC.
Application year: 1997
Main classification: E01B25
IPC codes: E01B25