Design of Shaft

IAEME PUBLICATION, 2019

In material engineering it is important to determine the cause of the failure & prevention of the failure .In present day the failure of the machine component is about 90% of the failure is because of the fatigue. In present study the failure of the shaft in the yaw gear box is analyzed .As we the shaft is rotating part of the engine it transmit the power from the one part of the engine to another part. It holds the maximum stress. In this case shaft of heat treated component with ultimate tensile strength Su= 2100Mpa is analysis done with ANSYS (FEA) software & compared with the theoretical calculation. There are dif erent methods which are used to predict fatigue life include stress life(S-N), strain Life (E-N) and Linear Elastic Fracture Mechanics (LEFM). In this project study, S-N approach is used to predict fatigue life for out-put shaft.

The main objective of this analysis is to investigate the stresses& deflections of drive shaft subjected to combine bending & torsion. Then checking for fatigue life as well as comparing the results with analytical calculations to verify accuracy of the results. Drive shaft is a critical component used in paper converting machines. It carries a load of two vacuum rollers weighing around 1471N and rotates at 1000 rpm, also subjected to reaction force of knife cutter and gears. This shaft has key slots and at the area of change in cross sections giving rise to localize stress concentration. Hence there is a scope of analyzing this part to predict its fatigue life and damage. Keywords: Fatigue Analysis, Shaft stress analysis, FEM analysis, shaft failure analysis

MP MATERIALPRUEFUNG - MP MATERIALS TESTING, 2019

of two types of notched bars (see Figure 1) and three types of loading: • Circular shaft with shoulder fillet (F) and three SCFs depending on the load case: The SCF for bending load α F,b , the SCF for torsion α F,t and the SCF for tension/ compression loading α F,z • Circular shaft with U-shaped groove (G) and three SCFs depending on the load case: The SCF for bending load α G,b , the SCF for torsion α G,t and the SCF for tension/compression loading α G,z .

International Journal for Research in Applied Science & Engineering Technology (IJRASET), 2021

This work aims towards the design and optimization of the drive shaft as there is increasing demand for weight reduction in an automobile vehicle. The drive shaft is basically a torque transmitting element which transmit the torque from the differential gearbox to the respective wheels. In general, the drive shafts are subjected to fluctuating loads as the torque requirement changes according to the road conditions. Due to this, the drive shaft should be designed considering fatigue failure. The Maruti Suzuki Ertiga model is chosen for design and optimization of the drive shaft. For the fatigue life predicting of the drive shaft, the S-N curve approach is used. Furthermore, the inner diameter of the shaft is varied to obtain the optimized diameter of a hollow shaft which can withstand these fluctuating loads without failure. Along with fatigue life prediction, the natural frequency of the hollow shaft is also calculated. Furthermore, the parametric analysis is carried out of fatigue FOS, Von mises stress, weight and natural frequency of the shaft by varying the diameter ratio of the hollow shaft, and the nature of variation of these parameters are plotted in their respective graphs. The design is validated by performing FEA analysis for each case of a hollow shaft using Ansys software. Finally, from the FEA analysis we conclude that the optimized dimensions of the hollow drive shaft are safe.

International Journal of Mechanical Sciences, 1986

This paper presents a calculation of the stress distribution in a shaft with a press-fitted hub subjected to axial fretting fatigue. Both normal contact stresses and frictional shear stresses at the shaft-hub interface are included in the model. The solution of Airy's function is obtained by means of Fourier integrals. The results are presented for different combinations of hub length, shaft radius and non-slip area and for various values of the coefficient of friction. Special consideration was given to the axial component of the stress, az, as this is the most important stress component in the initiation and propagation of fatigue cracks. Finally, the paper deduces the implications arising from the stress analysis on the fretting fatigue of the junction studied. NOTATION 2a hub length ao, at constants in solution for 2c length of non-slip area i =x/-1 Io modified Bessel function of zero order and first kind Jo{i~/ defined by Io {2r} = i" It modified Bessel function of first order and first kind Jl {i~r} defined by It {2r} = i" Jo Bessel function of zero order and first kind J1 Bessel function of first order and first kind K o Bessel function of zero order and second kind K1 Bessel function of first order and second kind p normal contact stresses at the shaft-hub interface ro shaft radius r, z coordinates of points at which stresses are calculated fl coefficient in stress equations, see equation (14) ? coefficient in stress equations, see equation (13) 2 integration variable of no physical significance which disappears when the integration is completed v Poisson's ratio. Value of 0.30 was used in all numerical calculations a, radial stress as tangential stress a, axial stress z,~ shear stress r, frictional shear stresses at the shaft-hub interface t o coefficient of friction defined as zJp Airy's stress function by means of which all components of stress are being evaluated

In this paper, shaft employed in an Inertia dynamometer rotated at 1000rpm is studied. Considering the system, forces, torque acting on a shaft is used to calculate the stresses induced. Stress analysis also carried out by using FEA and the results are compared with the calculated values. Shaft is having varying cross sections due to this stress concentration is occurred at the stepped, keyways ,shoulders, sharp corners etc. caused fatigue failure of shaft. So, calculated stress concentration factor from which fatigue stress concentration factor is calculated. Endurance limit using Modified Goodman Method, fatigue factor of safety and theoretical number cycles sustained by the shaft before failure is estimated and compared results with FEA.

The paper presents the analytical fatigue calculation compared to the numerical fatigue analysis for the primary shaft of a manual gearbox using four types of materials. The gearbox is similar with the Land Rover R380 gearbox and it was designed to withstand the specific loads from this vehicle's engine. The loads of the shaft are known, so the the reactions are calculated and the bending diagrams are drawn for all the gears of the gearbox. For the maximum load case of the shaft it is presented the fatigue calculation for the stress concentrators in the vicinity of the bearing from inside of the gearbox housing. Finally it was studied the influence of mechanical properties of the material for the fatigue strength.