Mechanical Engineers Handbook Episode 14 pps

... combination y   n i1 c i y i 1X146 of n linearly independent (on the same interval) partial solutions y i i  1Y 2Y FFFY n with arbitrary constant coef®cients. m THEOREM 1 .14 If a homogeneous linear ... two equations have the form y n  a 1 xy nÀ1 ÁÁÁa n xy  0 1X148 y n  b 1 xy nÀ1 ÁÁÁb n xy  0Y 1X149 where the functions a i x and b i xY i  1Y 2Y FFFY...

Ngày tải lên: 13/08/2014, 16:21

... Differential Equations of Mechanical Systems 703 A.2 The Laplace Transform 707 A.3 Mapping Contours in the s -Plane 707 A.4 The Signal Flow Diagram 712 References 714 Figure 1.1 Plant. 612 Control Control assume ... represents a disturbance of the system. If the water level increases, the ¯oat moves up and, by a mechanical system representing the controller, initiates the opening of the...

Ngày tải lên: 13/08/2014, 16:21

... 2-1/2 0.66 102.00 0.10 $89.00 3 0.66 114. 00 0 .14 96.00 4 1.32 143 .00 0.20 120.00 5 1.53 207.00 0.23 171.00 6 1.61 244.00 0.31 209.00 8 1.77 338.00 0.48 314. 00 10 2.69 475.00 0.71 434.00 12 ... 2,561 1.89 4 ,148 2 2.29 4,357 2.25 4,707 2-1/2 — — 3.46 5,111 3 — — 3.55 6,826 4 — — 5.52 9,995 6 — — 8.33 17,156 8 — — 8.60 37,151 10 — — 9.93 45, 314 12 — — 10.56 54,180 14 —...

Ngày tải lên: 13/08/2014, 09:21

... of mechanical systems. This handbook& apos;s special features include authoritative contributions, chapters on mechanical design, useful formulas, charts, tables, and illustra- tions. With this handbook ... Craciunoiu, (243, 559) Department of Mechanical Engineering, Auburn University, Auburn, Alabama 36849 Cristian I. Diaconescu, (1, 51, 119, 243) Department of Mechanical Engineer...

Ngày tải lên: 13/08/2014, 16:21

... velocities v A and v B before their impact (Fig. 3.14a). The magnitude of the force the particles exert on each other during the impact is R (Fig. 3.14b). The impact force is parallel to the line ... (Fig. 3.14a). As a result of the impact, the objects will deform. At the time t m the particles will have reached the maximum compression (period of compression, t 1 ` t ` t m ; Fig. 3.14b). At ....

Ngày tải lên: 13/08/2014, 16:21

... 139 1.11 Shear Stresses in Beams 140 1.12 Shear Stresses in Rectangular Section Beams 142 1.13 Torsion 143 1 .14 Contact Stresses 147 2. De¯ection and Stiffness 149 2.1 Springs 150 2.2 Spring Rates ... 0.96 0.54 0 Source: J. E. Shigley and C. R. Mischke, Mechanical Engineering Design. McGraw-Hill, New York, 1989. Used with permission. 1. Stress 143 Mechanics The moment of this...

Ngày tải lên: 13/08/2014, 16:21

... (kpsi) H B K f 20 22 83 26 9.6 14 3.9±5.6 10 156 1.00 25 26 97 32 11.5 14. 8 4.6±6.0 11.5 174 1.05 30 31 109 40 13±16.4 5.2±6.6 14 201 1.10 35 36.5 124 48.5 14. 5±17.2 5.8±6.9 16 212 1.15 40 42.5 140 57 16±20 6.4±7.8 ... Mischke 1 predicted the following relationships S H e  0X504S ut , S ut 200 kpsi (140 0 MPa) 100 kpsi, S ut b 200 kpsi 700 MPa, S ut b 140 0 MPa, V ` X 3X1 where S...

Ngày tải lên: 13/08/2014, 16:21

... frictional terms must be divided by cos a : T r  Fd m 2 l  pmd m sec a pd m À ml sec a  X 1X14 Equation (1 .14) is an approximation because the effect of the lead angle has been neglected. For power ... used, with both English and SI units, is 20  . In the United States 25  is also standard, and 14. 5  was formerly an alternative standard value. Pressure angle affects the force that...

Ngày tải lên: 13/08/2014, 16:21

... 0.0062 140 ,400 117,940 0.1300 0.0929 0.0260 0.0060 169,060 145 ,390 0.1500 0.0698 0.0255 0.0055 198,680 176,830 0.1800 0.0485 0.0234 0.0050 242,750 220,910 0.2000 0.0393 0.0220 0.0047 272 ,140 253,090 0.2200 ... 9.90 13.2 7.20 11.1 16.5 45 5.80 9.10 14. 8 6.30 10.4 16.4 7.40 12.2 20.9 50 6.10 9.70 15.8 6.60 11.0 19.2 12.5 24.5 55 8.20 12.0 18.0 9.00 13.6 21.5 11.3 14. 9 27.1 60 8.70 13.6...

Ngày tải lên: 13/08/2014, 16:21

... tdt X 2X142 If we use the identity sinot  ot sin ot cos ot  cos ot sin otY 2X143 Eq. (2 .142 ) becomes x 0  1 mo sin ot  t 0 F t cos otdt cos ot  t 0 F t sin otdt ! X 2X144 One ...  1 mo  t 0 F t sin odt Y 2X145 and Eq. (2 .142 ) can be rewritten as x  v 0 o sin ot  x 0 cos ot  A sin ot  B cos otX 2X146 If F t F 0 sin ptY 2X147 one can obtain the results...

Ngày tải lên: 13/08/2014, 16:21