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- Repeat Problem 6.2-17 but now use a transformed-section approach.Problem 1: The pin in a Box-Pin coupling is acted upon by a force (F), that varies as random variable due to misalignment as (2, 0.08) kN. The load act at a distance (1) that varies as (25 ± 3) mm. The diameter of the pin (D) is 18 mm. The fillet radius at the pin shoulder is about 1.5 mm. The stress concentration factor due to fatique in bending is thus a random variable kb that could vary from 1.3 to 1.5. The pin is made of steel AISI 4340 with mean endurance strength in bending of 400 MPa, and a standard deviation of 25 MPa. Determine the pin diameter (d), if one pin in every 10000 may be permitted to fail. R1.6 O L Problem (1)MM Diameter = ? Pin Anvil FIGURE P4-21 Impact hammer for Problem 4-21, 4-21. Figure P4-21 shows an anvil for an impact hammer held in a fixture by a circular pin. If the force is to be 500 lb, specify a suitable diameter for the steel pin if it is to be made from SAE 1040 WQT 900.
- Please answer in this format. Sketch: Given: Required: Solution: (Please answer in detailed (step by step). Indicate labels on what you are doing/performing, for example what formula is used) A torque To is transmitted between two flanged shafts by means of four 20-mm bolts. diameter of the bolt circle is 2=150mm. If the allowable shear stress in the bolts is 90 Mpa, what is the maximum permissible torque? Disregard friction between between flanges. The ToShown below is a figure of a landing gear configuration on the VS and VD planes (for landing gear the directions V, D, and S are often used instead of x, y and z) This gear unit is assumed to represent one side of the main gear on a tricycle type of the landing gear system. The loading assumed corresponds to a condition of nose wheel up or tail down. The design load on the wheel is vertical and it s magnitude for this problem is 15,000 lbf. Determine the reactions at F, H, and G. The fittings at F and H are pinned and therefore cannot transmit any bending moments. The fitting at G is also a pinned fitting.10) A screw clamp similar to the one shown in the figure has a handle with diameter in made of cold-drawn AISI 1006 steel. The overall length is 3 in. The screw is in-14 UNC and is 5 in long. overall. Distance A is 2 in The clamp will accommodate parts up to 4 in tagh. (a) What screw torque will cause the handle to bend permanenly? See sample problem 10.1, sections 10.4, 10.7 Given; hordle dia : 16 in L: 3in. Disa: Zin 10/29 Find: Scrcw torque ,! Assumphon : The screw torque is far cold decun AISI 1006 steel. a L: 3- 8 2.406 in %3D 4 32 T: 2.406F H:(L-3) -굵)F. 2.188F F- (2406 F: 2.188F Sy: 41 Kpsi. 32 (2-188) F TI (O.1875)3 Sy = 32M F-12:13 1bf T. 2.406 CI2:13) = 29.216f. in The lorque of the screw which will couse the scoch to bend pemorently is 29.21of. in. is 29.210f.10.
- For crank slider, L,=40mm; L,= 120mm; %3D Offset =-20mm and d=100mm and . Find the possible value of 0, and 0,3) A double screw (Acme thread angle o = 14.5) mechanism is designed to lift a load of 18,000 lb in such a way that screw is loaded in tension. Use of Safe Factor of safety of 3.2. Select a suitable screw from data table provided in class notes for tensile load and shear load. Limiting tensile and shear stresses are 10,000 psi and 5,500 psi, respectively. Required thickness of Yoke which functions as a nut. It is desired to raise the hatch a total of 30.0 inches in 15 seconds. Use coefficient of friction f= 0.15. List necessary assumptions. Sketch and Label a schematic diagram. Determine a. Nominal major diameter of screw (D) b. Threads per Inch of selected thread (n) c. Thickness of Yoke (h) d. Lead angle (2) e. Torque required to raise the load (Tup) f. Torque required to lower the load (Tdown) g. Efficiency of the screw h. RPM required to operate each screw i. Compute the Total Power required to operate the mechanism.Project 1: A Pully drive system used in washing machine is designed based on flat belt as in Figure.1/a. The tension in the pully is 115 N when it is stationary. The flat and V-belt type as well as the geometry specifications (Diameters and lap angle) are shown in Figure.2. The speed of rotation N is 1400 rpm and the coefficients of friction is u = 0.25 Flat Belt V-Belt (b) Figure.1: Flat vs V-belt pully drive section (а) lap angle = 480 mm D = 160 D,=240 mm Figure.2: Pully drive system specifications HT Page 5 of 10 الحسين التقنية Al Hussein Technical 1. Find the initial tension in each side 2. Find the power transmitted on the smaller wheel 3. Discuss the initial tension requirements/calculations to convert the system to the operation of a V-belt drive, if the included angle of V-section B = 15° (assume same u ), in your discussion compare the critical tension ration for both type and the transmitted power values.
- PROBLEM:1 A gas engine valve spring is to have a mean diameter of 55 mm. The maximum load it will have to sustain is 584 N with a corresponding deflection of 7.18 mm. The spring is to be made of tempered wire. Since the material is to be subjected to repeated loading and fatigue must be considered a low working stress of 650 N/mm? will be used. Find the size for wire and number of coils used. Take modulus of rigidity as 0.84 x 105 N/mm? .Assume the spring coil is squared and ground. Take shear stress Concentration factor as 1.15.Provide step-by-step solution with complete given and formula to this problem. Draw sketch also. A mine hoist is to carry a cage loaded with ore at a total load of 8 tons. The depthof mine shaft is 328 ft. A 6 x 19 IPS wire rope with rope diameter of 1.75 in is to beuse with sheave diameter of 39 in. The cage loaded is to start from rest and will attaina maximum velocity of 525 fpm in 10 seconds. Find the total load of the rope. A. 12,086 lbs B. 14,086 lbs C. 16,086 D. 18, 086 lbsDesign the elliptical cross-section of a belt pulley arm near the hub for the following specifications: The mean pulley diameter is 300 mm and the number of pulley arms are 4. The elliptical section has major axis twice the minor axis length. The tight and slack sides tension in the belt are 600 N and 200 N respectively. Assume half number of arms transmit torque at any time and the load factor of 1.75 to account for dynamic effects on the pulley while transmitting torque. The permissible tensile stress for cast iron pulley material is 15 MPa. The pulley hub diameter is 60 mm.