A schematic of a clutch-testing machine is shown. The steel shaft rotates at a constant speed w. An axial load 1.170P is applied to the shaft and is cycled from zero to 1.170 P torque T induced by the clutch face onto the shaft is given by f(l.xxxP)(D+d) T 4 Where D and d are defined in the figure and f is the coefficient of friction of the clutch face. The shaft is machined with Sy = 800 MPa and Su = 1000 MPa. The theoretical stress- concentration factors for the fillet are 3.0 and 1.8 for the axial and torsional loading, respectively. Assume the load variation P is synchronous with shaft rotation. With f = 0.3, find the maximum allowable load P such that the shaft will survive a minimum of 10° cycles with a factor of safety of 3. Use the modified Goodman criterion. Determined the corresponding factor of safety guarding against yielding. Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. R= 3 mm d = 30 mm 1.015 Friction pad D= 150 mm

A schematic of a clutch-testing machine is shown. The steel shaft rotates at a constant speed w. An axial load 1.170P is applied to the shaft and is cycled from zero to 1.170 P torque T induced by the clutch face onto the shaft is given by f(l.xxxP)(D+d) T 4 Where D and d are defined in the figure and f is the coefficient of friction of the clutch face. The shaft is machined with Sy = 800 MPa and Su = 1000 MPa. The theoretical stress- concentration factors for the fillet are 3.0 and 1.8 for the axial and torsional loading, respectively. Assume the load variation P is synchronous with shaft rotation. With f = 0.3, find the maximum allowable load P such that the shaft will survive a minimum of 10° cycles with a factor of safety of 3. Use the modified Goodman criterion. Determined the corresponding factor of safety guarding against yielding. Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. R= 3 mm d = 30 mm 1.015 Friction pad D= 150 mm

Elements Of Electromagnetics

7th Edition

ISBN:9780190698614

Author:Sadiku, Matthew N. O.

Publisher:Sadiku, Matthew N. O.

ChapterMA: Math Assessment

Section: Chapter Questions

Problem 1.1MA

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Q1) For a cone clutch, see figure (Q1), when the wear is uniform (Pr=constant), show that the transmitted torque is equal to: T = π *μ*csc(B)* C* (r² − r₂²) Where T: Transmitted torque, u: coefficient of friction, C:Constant, 2ß: Cone angle, ₁: Inner radius, ₂: Outer radius driving Shaft お 3 (rad/sec) or (rpm) 90° driven shaft. W (rpm) (read /sea) total axial force.
4. A plate clutch has three discs on the driving shaft and two discs on the driven shaft, providing four pairs of contact surfaces. The outside diameter of the contact surfaces is 240 mm and inside diameter 120 mm. Assuming uniform pressure and f = 0.3, find the total spring load pressing the plates to transmit 25 kW at 1575 rpm. If there are 6 springs each of the contact surfaces has worn away by 1.25 mm, find the maximum power that can be transmitted, assuming uniform wear.
In the design in the figure, a force of Fn=45992 N acts in the vertical plane on a machine element with a diameter of D=200 mm on the shaft resting on the A and B bearings. If the angle made by this force with the horizontal is b=40o, find the life of the 6210 coded Deep Ball bearing to be used in the B bearing, in hours. Number of revolutions = 30 rpm. 1-) The diameter of the machine element on which the force acts will be taken into account in the calculation of bearing forces (That is, it will be assumed that the Fn force AFFECTS THE GROUND shown in the figure, NOT the axis of the shaft). 2-) Pi number will be taken as 3.14.
The value of curvature correction factor k, will be if the spring index is 6. O a. 1.33 O b. 1.08 O c. 0.92 O d. 4.00 The figure below shows the components of normal forces, the value of radial force on the gear wheel due to a tangential force of 642 N is N, Take pressure angle as 14½0. at Pitch P. point Gear driven to 02 The radial force is
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. The mean diameter of the driving pulley for a vec-belt drive with two belts is 110 mm. The pulley groove angle is 40° and the drive transmits 4.4 kW at a speed of rotation of 1500 rev/min. The coefficient of frietion between belt and pulley 0.32, and the angle of lap is 160°. Determine the driving torque and the maximum stress in the belt material if the cross-sectional area of each belt is 120 mm.
In a gearbox, a spur gear is mounted on a shaft at equal distances from twosupporting bearings. The shaft and mounted gear turn together at a speed of3600RPM. The gearbox is designed to transmit a maximum power of 3kW. Thegear contact angle is φ = 20°. The pitch diameter of the gear is dp = 30 in. a) Findthe radial force on each of the two bearings supporting the shaft.The ratio of the two bearings’ length and diameter is L/D = 0.5. The bearings aremade of acetal resin material with the following limits:Surface velocity limit, V, is 5m/s.Average surface-pressure limit, P, is 7 MPa.PV limit is 3000 psi-ft/min.b) Find the diameter of the shaft in order not to exceed the stated limits.
The shaft shown in the figure below and rotating at a speed of 1 radian / sec transmits 9 kW of power from the gear at the B point to the pulley at the D point. Manufactured from cold drawn AISI 1040 steel, the shaft is machined to the given dimensions and bedded from A and C points. The highest working temperature of the spindle is 50 ° C. At point D; Since (d2 / d3 = 1.1) and (r /d = 0.1), determine the diameter d3 of the shaft using Goodman's theory. (kb = kc = kf = 1, q = 0.8 and qs = 0.9) 200 mm 140 mm 60 mm F1= 5F Fa Kasnak 160 Ry F2 = F Dig!! Ray Ray
Q3/ A multi plate clutches an included angle of 120°. A multi plate clutch, has 2 discs on the driving shaft and1 on the drive shaft, the outer radius is 100 cm and inside diameters 600 mm. The maximum intensity of pressure at any point is 0.2 N mm. If the u is 0.25, determine the speed of the clutch if the power generated = 31582.807 kW. Use both the uniform wear theory and the uniform pressure theory %3D
Two gears are designed to mesh as shown. Gear 1 is driven by another gear that is not shown which induces a force, F, equal to 52 N as shown. Gear 1 has 78 teeth and a pitch diameter equal to 64 mm. If Gear 2 has 44 teeth, and the gears are to remain at constant speed while the tangent force F is applied, find the Value of the resisting torque that is applied to Gear 2.  Direction that the resisting torque should be applied. Explain youranswer. Note: Gears are not drawn to scale.
A single block brake is shown in the figure. The diameter of the drum is 250 mm and the angle of contact is 103.7°. If the operating force of 661N is applied at the end of a lever and the coefficient of friction between the drum and the lining is 0.35, determine: a. The tangential braking force, Ft, in Newtons b. The braking the torque transmitted by the block brake in N-m.
3. A motor is connected by a belt to pulley B. T, is the tight-side tensile force equal to 1800 N. The shaft spins at a constant speed, 650 rpm. The power delivered by the motor is 12.6 kW. On pulley A, connected to the load, the slack side of the belt has a tension equal to th of the tight side. b T T, B d shaft Dimensions are as follows: da 200 тm 300 тт | 250 тm |180 тm | 250 тm 26 тm dB dahaft a We analyzed a problem similar to this on Test 01 using static failure theories. Is this strictly correct? Because the shaft is spinning, would not a material particle see a time-varying reversal of the the bending stress as in the R.R. rotating beam test? Would a particle see a reversal of the torsional shear stress? Assume Sut = 370 MPa and Sy = 300 MPa. Ignore Marin factors. Ignore stress concentrations. Ignore direct shear stress (that due to V). Find the safety factors with respect to fatigue and yielding. Be guided by section 6-14 on combined loading.