Bending Torsional Axial Shoulder fillet-sharp (r/d = 0.02) 2.7 2.2 3.0 Shoulder fillet-well rounded (r/d = 0.1) 1.7 1.5 1.9 End-mill keyseat (r/d = 0.02) 2.14 3.0 Sled runner keyseat 1.7 | Retaining...

Extracted text: Bending Torsional Axial Shoulder fillet-sharp (r/d = 0.02) 2.7 2.2 3.0 Shoulder fillet-well rounded (r/d = 0.1) 1.7 1.5 1.9 End-mill keyseat (r/d = 0.02) 2.14 3.0 Sled runner keyseat 1.7 | Retaining ring groove 5.0 3.0 5.0


Extracted text: Obtain a preliminary design of the shaft by performing the following tasks. Note that forces T1=2880 N and T=432 N. The maximum bending moment is at x= 230 mm (point B), and it equals M= 698.3 N•m completely reversed, where the torque is constant at 612 N.m at the same point. The shaft material is AISI 1020 CD steel. Take the stress concentration conditions at B to be Shoulder fillet-sharp, with notch radius r=0.6 mm (Table 7-1). 230 mm T, 280 mm 30-mm dia. T, 300 mm 250-mm dia. 400-mm dia. 270 Nx 1800 N a) Sketch a general shaft layout in 2D (x – y axes), including all components and torques, then calculate all reactions. : b) Based on the current shaft dimensions and using only forces at B and C, find the lowest critical speed of the shaft. (; c) Determine the fatigue factor of safety of the rotating shaft with the current dimensions using the DE-Gerber criteria. Use Eqs. 6-8 and 6-18 to find the endurance limit, account only for ka and k, in Eq. 6-18 and assume all remaining factors as 1., Discard the indicated shaft diameter and use DE-Goodman criteria to determine the critical diameter of the shaft based on infinite fatigue life with a design factor n of 1.5. (Take the same value of endurance limit as that used in part e of this problem). (: