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# gear design.pptx

desiging gear specifications

desiging gear specifications

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### gear design.pptx

1. 1. AGMA Gear Design Equations
2. 2. Gear Design Calculations Power generated by bullocks, P is 650 W Rpm generated is 2. Rpm of the pulley is = 145/35*94/22*110/31*2 = 125 rev/min Let us call the driving gear as pinion and the driven gear as gear. 1st Meshing Assumed face width of pinion = 45mm Assumed face width of gear = 50mm Torque on the pinion shaft, T = P*60/(2*3.14*2) = 3103.5Nm Transmitted load, Wt is T/(pitch dia / 2) = 10700 N Pitch line velocity, V = (2*3.14*2/60)*(.58/2) = 0.06 m/s Kv = 0.977 J(pinion) = 0.46, J(gear) = 0.41 σbp = 211.33 Mpa, σbg = 213.7 Mpa Kr is taken as 0.85 (90% reliability) Designing for 10 years of life, Kl = 1.01 For E=207 Gpa, v=0.28, Cp = 189 (MPa)0.5 ρp = 0.1, ρg = 0.023, I = 0.03. σc = 894 MPa. CL = 0.9988, CR = 0.85, We choose A3 AGMA class steel for the material, which has Sfb ’ = 325MPa, Sfc ’ = 930MPa Sfb = 1.01*325/0.85 = 386 MPa, Sfc = 0.9988*930/0.85 = 1092 MPa. Nb(pinion) = (386/211) = 1.8, Nb(gear) = (386/213) = 1.8 Nc(pinion-gear) = (1092/894)^2 = 1.49 All FOS are greater than 1, the design is safe and we can proceed further. Let us call the driving gear as pinion and the driven gear as gear. Rpm of the pinion is 2*(145/35) = 8.3 rev/min. 2nd Meshing Assumed face width of pinion = 40mm Assumed face width of gear = 40mm Torque on the pinion shaft, T = P*60/(2*3.14*8.3) = 747Nm Transmitted load, Wt is T/(pitch dia / 2) = 6364 N Pitch line velocity, V = (2*3.14*8.3/60)*(.235/2) = 0.102 m/s Kv = 0.97 J(pinion) = 0.4, J(gear) = 0.35 σbp = 262 Mpa, σbg = 299 Mpa Kr is taken as 0.85 (90% reliability) Designing for 10 years of life, Kl = 0.99 ρp = 0.04, ρg = 0.0096, I = 0.03. σc = 1134 MPa. CL = 0.966, CR = 0.85, We choose A4 AGMA class steel for the material, which has Sfb ’ = 360MPa, Sfc ’ = 1100MPa Sfb = 0.99*360/0.85 = 419 MPa, Sfc = 0.966*1100/0.85 = 1242 MPa. Nb(pinion) = (419/262) = 1.6, Nb(gear) = (419/299.9) = 1.39 Nc(pinion-gear) = (1242/1134)^2 = 1.2 All FOS are greater than 1, the design is safe and we can proceed further.
3. 3. Let us call the driving gear as pinion and the driven gear as gear. Rpm of the pinion is 2*(145/35)*(94/22) = 35.4 rev/min. 3rd Meshing Assumed face width of pinion = 24mm Assumed face width of gear = 24mm Torque on the pinion shaft, T = P*60/(2*3.14*35.4) = 175.34Nm Transmitted load, Wt is T/(pitch dia / 2) = 1594 N Pitch line velocity, V = (2*3.14*35.4/60)*(0.22/2) = 0.4 m/s Kv = 0.94 J(pinion) = 0.45, J(gear) = 0.39 σbp = 125.61 Mpa, σbg = 144.9 Mpa Kr is taken as 0.85 (90% reliability) Designing for 10 years of life, Kl = 0.966 ρp = 0.037, ρg = 0.011, I = 0.036. σc = 714 MPa. CL = 0.935, CR = 0.85, We choose A2 AGMA class steel for the material, which has Sfb ’ = 280MPa, Sfc ’ = 790MPa Sfb = 0.966*280/0.85 = 318 MPa, Sfc = 0.935*790/0.85 = 869 MPa. Nb(pinion) = (318/125) = 2.5, Nb(gear) = (318/144) = 2.2 Nc(pinion-gear) = (869/714)^2 = 1.48 All FOS are greater than 1, the design is safe.