Please summarise the answers for this question for i and ii as it looks too long Q1. Describe the following modes of failure associated with gearteeth, indicating their causes and how they might be prevented inpractice:(i) tooth breakage (bending failure);and(ii) surface damage of teeth (pitting).i. Bending failure occurs as a result of bending stresses in the tooth which aregreatest at the root. Because of the cyclic loading this is a fatigue problem whichmanifests itself by cracks propagating across the tooth and the facewidth of thegear itself. This results in partial or total removal of a tooth.ii.The situation maybe made worse by the use of unsubstantial rims or the pressureof stress concentrations arising from pits may move the critical stress away fromthe fillet.Materials with a high fatigue resistance need to be used-surface hardened steelsare best in this sense,Therefore, offer little improvement in load distribution.Residual stresses maybe beneficial - compressive stresses due to Carburising orshot peeing.In general (bending strength) a UTS with Carburising steel showing a markedimprovement over other materials.The repeated application of Hertzian stresses to gear surfaces results in smallfatigue cracks at or near the surface. These extend until lumps fall out leavingcraters. These usually occur on the dedendum surfaces of teeth.This is also a fatigue problem, but the associated knee point is muchhigher ~108 or 10⁹ cycles.The craters reduce the load bearing surface, break the lubricant film, andconstitute a stress concentration from which total tooth breakage could initiate.There is evidence that pitting is initiated by stresses associated with asperitycontacts. Pitting can be avoided by ensuring that the oil film thickness issubstantially greater than the total surface roughness.

Details about the prevention of1) tooth breakage of gear and 2) surface damage of teeth

Q1. Describe the following modes of failure associated with gear teeth, indicating their causes and how they might be prevented in practice: (i) tooth breakage (bending failure); and (ii) surface damage of teeth (pitting).

Q1. Describe the following modes of failure associated with gear teeth, indicating their causes and how they might be prevented in practice: (i) tooth breakage (bending failure); and (ii) surface damage of teeth (pitting).

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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Question 1 What is the difference between bending stress and pitting resistance? And why is it important to verify the bending stress of the standard selected gears
The drawback(s) of the classic Lewis equation to find bending stress in gear a tooth are: The tooth load in practice is not static. The whole load is carried by single tooth is not correct. The greatest force exerted at the tip of the tooth is not true All of these options Which of the following design factor (suggested by AGMA) depends on the tooth profile inaccuracies? AGMA Geometry factor (J) Load Distribution Factor (Km) Dynamic Factor (K,)
QUESTION 3 DETAILED GEARING A gear drive is proposed to connect a 30-KW electric motor, with a shaft speed of 1475 r/min, to a uniformly loaded conveyor with a required shaft speed of approximately 531 r/min. Use a pinion with 18 teeth, a pressure angle of 20. and a gear with 50 teeth. Both gears will be made from hardened through grade 2 steel, while the Brinell hardness of the pinion and gear will be 160 BHN. The gears are b be manufactured to a number 9 AGMA quality standard while the teeth are uncrowned. The module of the gears is 5 mm, and the face width is 20 mm. The gears are straddle mounted within a precision enclosed gear unit. Assume a pinion life of 10° cycles and a reliability of 90 %. 3.1 Determine the AGMA bending stress for the gear and pinion. 3.2 Determine the corresponding factors of safety for both the pinion and the gear. 3.3 Write the conclusion.
Fill the blank: 1) In fatigue failure analysis, regarding S-N diagram, S stands for........ and N stands for ............ 2) The circle on which the involute profile of the gear teeth are generated is called .......... circle 3) The helix angle on the worm is ......... than the one on the mating gear.
The client requires a single step-up spur gearbox to transmit a 10 kW power from a shaft rotating at 1000 rpm, while the output speed must be 1700 rpm. The material for gear and pinion is 817M40 and 655M13, respectively. Use table 6.10 on page 128 to select the suitable gear and pinion. 1.4 If the pinion has 20 teeth, use the Lewis formula to determine the face width of the pinion and gear. Then, do one set of calculations and tabulate the answers.
According to AGMA standards, contact stress numbers of pitting resistance for different types of gear teeth are calculated differently. Please select the right formula for each type of gear teeth. Equation a: Equation b: For helical gears, equation a should be used. For spur gears, equation b should be used. For spur gears, equation a should be used. For helical gears, equation b should be used. For bevel gears, equation a should be used. For bevel gears, equation b should be used.
When interested in performing a bending stress analysis for gear teeth, the width, F, should fall within this range related to diametral pitch Pd: a. F > 16/Pd b. F < 8/Pd c. 8/Pd < F
If a pinion having 20 teeth transmit the power to the gear shaft having 40 teeth, the gear ratio of this system is 0.5. Select one: O True O False Stress concentration factor is defined as the ratio of the lowest stress or nominal stress in the component to the highest stress any where in the same component. Select one: O True O False A radial ball bearing fitted on to the shaft of a refinery vessel is subjected to axial load of 3340.8 N, take the service factor(K;) as 1.5. The equivalent dynamic load acting on the bearing will be . O 10022.40 O 1670,40 O 2505.60 O 5011.20 The outer diameter of muff is calculated as 81.2 mm. The shaft diameter of muff coupling is . mm. O a. 39.60 O b. 34.10 O c.61.38 O d. 26.80
Gear 2 (pinion) runs at 1800 rpm ccw and transmits 3.5 kW to frictionless, idler gear 3. The pressure angle is 20° with a module = 2 mm. Determine the following: a. Draw the free body diagram for the gear set. b. Pitch diameters of each gear. 50T of m b. 3 30T - 20T C. Transmitted load on gear 2. d. Torque on gear 2 shaft a. e. Tangential and radial force from gear 2 shaft. f. Tangential and radial forces on gear 4. g. Torque on gear 4 shaft c.
If in a gear design problem, the required hardness of steels per allowable gear bending strength is: HB = 158; while the required hardness of steels per allowable gear contact strength is: HB = 256. Which material HB hardness will be used for gear material specification? 256 158 120 400
1. Calculate the power that can be transmitted safely by a pair of spur gears with the data given below. Calculate also the bending stresses induced in the two wheels when the pair transmits this power. Number of teeth in the pinion = 20 Number of teeth in the gear = 80 Module = 4 mm Width of teeth = 60 mm Tooth profile = 20° involute Allowable bending strength of the material = 200 MPa, for pinion = 160 MPa, for gear = 400 r.p.m. Speed of the pinion Service factor = 0.8 0.912 0.154- T Lewis form factor %3D 3 Velocity factor 3 + v
A Design of Single Reduction Spur Gearbox An input shaft connected to the motor rotates at 1200 rpm, while the output speed must be 570 rpm. The contact force between the gears is transmitted through the pressure angle of 20°. The radial force is 321,90 kN. The material for both gear and pinion is 817M40. 1.1) select the suitable gear and pinion (make use of the Lewis formula). Then, do one set of calculations for single reduction gearbox