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Design Moment Total HL-93 moment Impact factor Applicable distribution factor for single lane Dynamic load allowance (impact factors) 133 applicable to truckloads only For reduced posted speed, a lower factor may be used For multiple lane live loads, a reduction in total live load is applicable Fatigue dynamic load allowance (for fatigue analysis) 115 applicable to truckloads only Comparison of maximum live load moments for internal beam For truck load versus tandem load a comparative study is shown in Table 45

0 0 5 10 15 h



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Table 44 Comparative study of single span HS-20 moments and shear forcesAASHTO and simpli ed formula developed by the author HS-20 LL Moments Span Length (Feet) 20 AASHTO LL Moment (Kip-Ft) 160 Mmax = 18(L-155) (L-14)/L (Kip-Ft) 28 distance between outer axles > 20 formula N/A 27312 44987 62791 80661 98568 116498 134444 152401 170365 188336 206310 224289 2422704 260254 278240 296227 314216 332205 350196 368188 386180 404173 HS-20 LL Shear AASHTO Reaction/Shear Force (Kips) 416 > 36 k vehicle, not correct 496 552 585 608 624 636 645 653 659 664 676 708 4960 5520 5856 6080 6240 6360 6453 6528 6589 6640 6683 6720 6752 678 6806 6827 6846 6864 688 6895 6908 692 Vmax = 24(3L-28)/L (Kips)

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30 2821 40 4498 2 Medium spans 50 6279 60 8065 70 9856 80 11649 90 13444 100 15240 110 17036 120 18833 3 Long spans 130 20631 140 22428 150 160 170 Lane load with 180 18 kips 190 concentrated 200 load for bending 210 governs 220 230 240

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Figures 1214 through 1217 are the contour plots of bm and gn for the harmonic and cycloidal curve investigation of this system These charts also allow one to compare the performance of the harmonic and cycloidal cam rises When looking at the follower system for a constant cam speed, cycloidal motion has de nitely better dynamic characteristics However, for this drive system vibration problem, the harmonic rise has lower drive system windups and lower radial follower forces than the cycloidal rise This is true for both the closed-track cam system and the open-track cam system with a return spring The difference is even greater than appears in a direct chart comparison because the harmonic rise has a lower maximum slope than the cycloidal rise for the same endpoints These charts may be used by a designer to determine at an early point in the design whether drive system windup will be a problem Given design estimates for qf, xf, qs, Ic, M, and ks one can quickly estimate the maximum windup, dynamic drive system torque, and radial follower force for a harmonic or cycloidal cam Also, other high-speed curves such as modi ed sine and modi ed trapezoidal offer better performance characteristics than the two basic curves studied in this section Thus for well-designed, stiff systems, a moderate spring size will keep the follower in contact However, for a more exible system (low h) with a degree of nonlinearity (nonzero Qm), follower separation is to be expected along with the other ills of vibration Comparing the performance of the open-track cams below the point of follower separation to the closed-track cams, the addition of the return spring affects the vibration It increases the minimum radial force ratio but removes the effects of the re ected inertia ratio on the radial force if separation does not occur It also increases the drive system windup at higher frequency ratios (h) while decreasing the drive system windup at lower.

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