Calculate helical gear geometry, tooth bending strength, and contact stress per AGMA 2001 and ISO 6336 standards.
ISO 6336-1 / ANSI/AGMA 2001-D04 Standard Configuration
m_t = m_n / \cos(\beta)d_1 = z_1 \cdot m_t, \quad d_2 = z_2 \cdot m_ta = (d_1 + d_2) / 2| Transmitted Power | 15.00 kW |
| Input Speed n₁ | 1450 rpm |
| Gear Ratio i | 3.00 : 1 |
| Normal Module mₙ | 3 mm |
| Pinion Teeth z₁ | 20 |
| Helix Angle β | 15° |
| Normal Pressure Angle αₙ | 20° |
| Face Width Ratio b/d₁ | 1 |
| Gear Teeth z₂ | 60 |
| Transverse Module mₜ | 3.106 mm KEY |
| Pinion Pitch Diameter d₁ | 62.12 mm KEY |
| Gear Pitch Diameter d₂ | 186.35 mm |
| Center Distance a | 124.23 mm KEY |
| Transverse Pressure Angle αₜ | 20.65° |
| Pitch Line Velocity v | 4.72 m/s |
| Tangential Force Fₜ | 3181 N |
| Axial Thrust Force Fₐ | 852 N KEY |
| Radial Force Fᵣ | 1199 N |
| Face Width b | 62.1 mm |
Assumes standard involute helical gear teeth with zero profile shift (x1 = x2 = 0). Recommended helix angle range is 10° ≤ β ≤ 30°. Angles below 10° provide minimal overlap benefits; angles above 30° induce severe axial thrust forces. Axial thrust forces Fa must be reacted by appropriate tapered roller or angular contact ball bearings on the shaft. Calculations omit dynamic factor Kv, overload factor Ko, and mounting factor Km. For ISO 6336 full tooth rating, conduct detailed contact stress analysis.
How helix angle selection balances axial thrust loads against noise reduction and tooth bending capacity.
Key methodological differences between ANSI/AGMA 2001 and ISO 6336 gear stress verification.
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| Center Distance: | 124.23 mm |
| Pinion Pitch Diameter: | 62.12 mm |
| Gear Pitch Diameter: | 186.35 mm |
| Axial Thrust Force: | 852 N |