- A 1/4 -in drill rod was heat-treated and ground. The measured hardness was found to be 490 Brinell. Estimate the endurance strength if the rod is
- Estimate S′e for the following materials: (a) AISI 1020 CD steel. (b) AISI 1080 HR steel. (c) 2024 T3 aluminum. (d) AISI 4340 steel
- Estimate the fatigue strength of a rotating-beam specimen made of AISI 1020 hot-rolled steel corresponding to a life of 12.5 kilocycles of stress
- Derive Eq. (6–17). For the specimen of Prob. 6–3, estimate the strength corresponding to 500 cycles.
- For the interval 103 ≤ N ≤ 106 cycles, develop an expression for the axial fatigue strength (S′f ) ax for the polished specimens of
- Estimate the endurance strength of a 32-mm-diameter rod of AISI 1035 steel having a machined finish and heat-treated to a tensile strength of 710 MPa.
- Two steels are being considered for manufacture of as-forged connecting rods. One is AISI 4340 Cr-Mo-Ni steel capable of being heat-treated to a
- A solid round bar, 25 mm in diameter, has a groove 2.5-mm deep with a 2.5-mm radius machined into it. The bar is made of AISI 1018 CD steel and is
- A solid square rod is cantilevered at one end. The rod is 0.8 m long and supports a completely reversing transverse load at the other end of ±1 kN.
- A rectangular bar is cut from an AISI 1018 cold-drawn steel flat. The bar is 60 mm wide by 10 mm thick and has a 12-mm hole drilled through the
- Bearing reactions R1 and R2 are exerted on the shaft shown in the figure, which rotates at 1150 rev/min and supports a 10-kip bending force. Use a
- A bar of steel has the minimum properties Se = 276 MPa, Sy = 413 MPa, and Sut = 551 MPa. The bar is subjected to a steady torsional stress of 103
- Repeat Prob. 6–12 but with a steady torsional stress of 138 MPa and an alternating bending stress of 69 MPa.
- Repeat Prob. 6–12 but with a steady torsional stress of 103 MPa, an alternating torsional stress of 69 MPa, and an alternating bending stress of 83
- Repeat Prob. 6–12 but with an alternating torsional stress of 207 MPa.
- Repeat Prob. 6–12 but with an alternating torsional stress of 103 MPa and a steady bending stress of 103 MPa.
- The cold-drawn AISI 1018 steel bar shown in the figure is subjected to an axial load fluctuating between 800 and 3000 lbf. Estimate the factors of
- Repeat Prob. 6–17, with the load fluctuating between .800 and 3000 lbf. Assume no buckling.
- Repeat Prob. 6–17, with the load fluctuating between 800 and -3000 lbf. Assume no buckling.
- The figure shows a formed round-wire cantilever spring subjected to a varying force. The hardness tests made on 25 springs gave a minimum hardness of
- The figure is a drawing of a 3- by 18-mm latching spring. A preload is obtained during assembly by shimming under the bolts to obtain an estimated
- Repeat Prob. 6–21, part b, using the modified Goodman criterion.
- The figure shows the free-body diagram of a connecting-link portion having stress concentration at three sections. The dimensions are r = 0.25 in, d
- The torsional coupling in the figure is composed of a curved beam of square cross section that is welded to an input shaft and output plate. A torque
- Repeat Prob. 6–24 ignoring curvature effects on the bending stress.
- In the figure shown, shaft A, made of AISI 1010 hot-rolled steel, is welded to a fixed support and is subjected to loading by equal and opposite
- A schematic of a clutch-testing machine is shown. The steel shaft rotates at a constant speed ω. An axial load is applied to the shaft and is
- For the clutch of Prob. 6–27, the external load P is cycled between 20 kN and 80 kN. Assuming that the shaft is rotating synchronous with the
- A flat leaf spring has fluctuating stress of σmax = 420 MPa and σmin = 140 MPa applied for 5 (104) cycles. If the load changes to σmax
- A machine part will be cycled at ±48 kpsi for 4 (103) cycles. Then the loading will be changed to ±38 kpsi for 6 (104) cycles. Finally, the load
- A rotating-beam specimen with an endurance limit of 50 kpsi and an ultimate strength of 100 kpsi is cycled 20 percent of the time at 70 kpsi, 50
- Solve Prob. 6–1 if the ultimate strength of production pieces is found to be Sut = 245LN (1, 0.0508) kpsi.
- The situation is similar to that of Prob. 6–10 wherein the imposed completely reversed axial load Fa = 15 LN (1, 0.20) kN is to be carried by the
- A solid round steel bar is machined to a diameter of 1.25 in. A groove 1/8 in deep with a radius of 1/8 in is cut into the bar. The material has a
- Repeat Prob. 6–34, with a completely reversed torsional moment of T = 1400 lbf • in applied.
- A 5/4 -in-diameter hot-rolled steel bar has a 1/8 -in diameter hole drilled transversely through it. The bar is nonrotating and is subject to a
- Repeat Prob. 6–36, with the bar subject to a completely reversed torsional moment of 2400 lbf • in.
- The plan view of a link is the same as in Prob. 6–23; however, the forces F are completely reversed, the reliability goal is 0.998, and the
- A 1/4 by 3/2 -in steel bar has a 3/4 -in drilled hole located in the center, much as is shown in Table A–15–1. The bar is subjected to a
- From your experience with Prob. 6–39 and Ex. 6–19, you observed that for completely reversed axial and bending fatigue, it is possible to •
- A shaft is loaded in bending and torsion such that Ma = 600 lbf • in, Ta = 400 lbf • in, Mm = 500 lbf • in, and Tm = 300 lbf • in. For the
- The section of shaft shown in the figure is to be designed to approximate relative sizes of d = 0.75D and r = D/20 with diameter d conforming to
- The rotating solid steel shaft is simply supported by bearings at points B and C and is driven by a gear (not shown) which meshes with the spur gear
- A geared industrial roll shown in the figure is driven at 300 rev/min by a force F acting on a 3-in-diameter pitch circle as shown. The roll exerts a
- The figure shows a proposed design for the industrial roll shaft of Prob. 7–4. Hydrodynamic film bearings are to be used. All surfaces are machined
- In the double-reduction gear train shown, shaft a is driven by a motor attached by a flexible coupling attached to the overhang. The motor provides a
- In the figure is a proposed shaft design to be used for the input shaft a in Prob. 7–7. A ball bearing is planned for the left bearing, and a
- An AISI 1020 cold-drawn steel shaft with the geometry shown in the figure carries a transverse load of 7 kN and a torque of 107 N • m. Examine the
- A 1-in-diameter uniform steel shaft is 24 in long between bearings. (a) Find the lowest critical speed of the shaft. (b) If the goal is to
- Demonstrate how rapidly Rayleigh’s method converges for the uniform-diameter solid shaft of Prob. 7–14, by partitioning the shaft into first
- Compare Eq. (7–27) for the angular frequency of a two-disk shaft with Eq. (7–28), and note that the constants in the two equations are
- For a uniform-diameter shaft, does hollowing the shaft increase or decrease the critical speed?
- The shaft shown in the figure carries a 20-lbf gear on the left and a 35-lbf gear on the right. Estimate the first critical speed due to the loads,
- A transverse drilled and reamed hole can be used in a solid shaft to hold a pin that locates and holds a mechanical element, such as the hub of a
- A guide pin is required to align the assembly of a two-part fixture. The nominal size of the pin is 15 mm. Make the dimensional decisions for a 15-mm
- An interference fit of a cast-iron hub of a gear on a steel shaft is required. Make the dimensional decisions for a 45-mm basic size medium drive fit.
- A pin is required for forming a linkage pivot. Find the dimensions required for a 50-mm basic size pin and clevis with a sliding fit.
- A journal bearing and bushing need to be described. The nominal size is 1 in. What dimensions are needed for a 1-in basic size with a close running
- A gear and shaft with nominal diameter of 1.5 in are to be assembled with a medium drive fit, as specified in Table 7–9. The gear has a hub, with
- LM35 is selected as a sensors. Classify the sensor in all possible ways.Extract all performance characteristics Total Words: 457
- An uncrowned straight-bevel pinion has 20 teeth, a diametral pitch of 6 teeth/in, and a transmission accuracy number of 6. Both the pinion and gear
- For the gearset and conditions of Prob. 15–1, find the power rating based on the AGMA surface durability.
- An uncrowned straight-bevel pinion has 30 teeth, a diametral pitch of 6, and a transmission accuracy number of 6. The driven gear has 60 teeth. Both
- For the gearset and conditions of Prob. 15–3, find the power rating based on AGMA surface durability. For the solutions to Probs. 15–3 and
- An uncrowned straight-bevel pinion has 22 teeth, a module of 4 mm, and a transmission accuracy number of 5. The pinion and the gear are made of
- For the gearset and conditions of Prob. 15–5, find the power rating for AGMA bending strength.
- In straight-bevel gearing, there are some analogs to Eqs. (14–44) and (14–45). If we have a pinion core with a hardness of (HB) 11 and we try
- Refer to your solution to Probs. 15–1 and 15–2, which is to have a pinion core hardness of 300 Brinell. Use the relations from Prob. 15–7 to
- Repeat Probs. 15–1 and 15–2 with the hardness protocol
- A catalog of stock bevel gears lists a power rating of 5.2 hp at 1200 rev/min pinion speed for a straight-bevel gearset consisting of a 20-tooth
- Apply the relations of Prob. 15–7 to Ex. 15–1 and find the Brinell case hardness of the gears for equal allowable load Wt in bending and wear.
- Use your experience with Prob. 15–11 and Ex. 15–2 to design an interactive computer-aided design program for straight-steel bevel gears,
- A single-threaded steel worm rotates at 1725 rev/min, meshing with a 56-tooth worm gear transmitting 1 hp to the output shaft. The pitch diameter of
- As in Ex. 15–4, design a cylindrical worm-gear mesh to connect a squirrel-cage induction motor to a liquid agitator. The motor speed is 1125
- The smart grid is not simply a unit entity but consist of multiple networks and multiple power generation sources along with multiple operators
- The figure shows an internal rim-type brake having an inside rim diameter of 12 in and a dimension R = 5 in. The shoes have a face width of 1 ½ in
- For the brake in Prob. 16–1, consider the pin and actuator locations to be the same. However, instead of 120°, let the friction surface of the
- In the figure for Prob. 16–1, the inside rim diameter is 280 mm and the dimension R is 90 mm. The shoes have a face width of 30 mm. Find the
- The figure shows a 400-mm-diameter brake drum with four internally expanding shoes. Each of the hinge pins A and B supports a pair of shoes. The
- The block-type hand brake shown in the figure has a face width of 30 mm and a mean coefficient of friction of 0.25. For an estimated actuating force
- Suppose the standard deviation of the coefficient of friction in Prob. 16–5 is = 0.025, where the deviation from the mean is due entirely to
- The brake shown in the figure has a coefficient of friction of 0.30, a face width of 2 in, and a limiting shoe lining pressure of 150 psi. Find the
- Refer to the symmetrical pivoted external brake shoe of Fig. 16–12 and Eq. (16–15). Suppose the pressure distribution was uniform, that is, the
- The shoes on the brake depicted in the figure subtend a 90◦ arc on the drum of this external pivoted-shoe brake. The actuation force P is
- Problem 16–9 is preliminary to analyzing the brake. A molded lining is used dry in the brake of Prob. 16–9 on a cast iron drum. The shoes are 7.5
- The maximum band interface pressure on the brake shown in the figure is 90 psi. Use a 14-indiameter drum, a band width of 4 in, a coefficient of
- The drum for the band brake in Prob. 16–11 is 300 mm in diameter. The band selected has a mean coefficient of friction of 0.28 and a width of 80
- The brake shown in the figure has a coefficient of friction of 0.30 and is to operate using a maximum force F of 400 N. If the band width is 50 mm,
- The figure depicts a band brake whose drum rotates counterclockwise at 200 rev/min. The drum diameter is 16 in and the band lining 3 in wide. The
- The figure shows a band brake designed to prevent “backward” rotation of the shaft. The angle of wrap is 270◦, the band width is 2 1/8 in,
- A plate clutch has a single pair of mating friction surfaces 300 mm OD by 225 mm ID. The mean value of the coefficient of friction is 0.25, and the
- A hydraulically operated multidisk plate clutch has an effective disk outer diameter of 6.5 in and an inner diameter of 4 in. The coefficient of
- Look again at Prob. 16–17. (a) Show how the optimal diameter d∗ is related to the outside diameter D. (b) What is the optimal inner
- A cone clutch has D = 330 mm, d = 306 mm, a cone length of 60 mm, and a coefficient of friction of 0.26. A torque of 200 N ?m is to be transmitted.
- Show that for the caliper brake the T / (f F D) versus d / D plots are the same as Eqs. (b) and (c) of Sec. 16–5.
- A two-jaw clutch has the dimensions shown in the figure and is made of ductile steel. The clutch has been designed to transmit 2 kW at 500 rev/min.
- A brake has a normal braking torque of 320 N m and heat-dissipating surfaces whose mass is 18 kg. Suppose a load is brought to rest in 8.3 s from an
- A cast-iron flywheel has a rim whose OD is 60 in and whose ID is 56 in. The flywheel weight is to be such that an energy fluctuation of 5000 ft ?lbf
- A single-geared blanking press has a stroke of 8 in and a rated capacity of 35 tons. A cam-driven ram is assumed to be capable of delivering the full
- Using the data of Table 16–6, find the mean output torque and flywheel inertia required for a three-cylinder in-line engine corresponding to a