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Machine DesignPower Transmission

Gearbox Design Workspace

Design a single-stage spur gear pair: compute gear ratio, output torque and RPM, pitch diameters, transmitted forces, and verify the tooth root against Lewis bending stress — all visualized on a live gear mesh schematic.

i = Z₂ / Z₁Lewis Bending EquationInteractive Mesh Schematic

Engineering Schematic

Spur Gear Mesh — Front View

Pinion Gear Pitch Circle
SPUR GEAR PAIR / FRONT VIEWFt = 4444 NT₁ = 120 NmT₂ = 353 Nma = 108.0 mmPINION · Z₁ = 18d₁ = 54.0 mmGEAR · Z₂ = 54d₂ = 162.0 mmm = 3 mm · α = 20° · b = 25 mm

Drive Input

Stage 1
Nm

Shaft torque

RPM

Pinion speed

-

Mesh efficiency

deg

Typically 20°

Gear Geometry

Spur Pair
teeth

Driving gear

teeth

Driven gear

mm

Tooth size

mm

Tooth face

Material Limits

MPa

Bending limit

Typical values: through-hardened steel 180–250 MPa, case-hardened 300+ MPa, cast iron 60–120 MPa, engineering plastic 30–70 MPa.

Calculated Results

Kinematics & Torque

Gear Ratio

3.00:1

54/18 teeth

Output RPM

500RPM

n₂ = n₁ / i

Output Torque

352.8Nm

η = 0.98

Transmitted Power

18.85kW

P = T₁·n₁/9550

Pitch Velocity

4.24m/s

v = π·d₁·n₁/60000

Contact Ratio

1.65-

≥ 1.2 recommended

Geometry & Forces

Pinion d₁

54.0mm

da = 60.0

Gear d₂

162.0mm

da = 168.0

Center Distance

108.0mm

a = (d₁+d₂)/2

Tangential Ft

4444N

2T₁/d₁

Radial Fr

1618N

Ft·tan(α)

Normal Fn

4730N

Ft/cos(α)

Lewis Bending Check

σ Pinion

296.3MPa

Y₁ = 0.200

σ Gear

296.3MPa

Y₂ = 0.200

Safety Factor

0.74-

σ_all = 220 MPa

Engineering Check

Review Required

Bending safety factor (0.74) is below 1.2 — tooth failure risk.

CRITICAL: bending stress exceeds allowable. Redesign required.

Engineering Relations

Governing Formula

i = Z₂ / Z₁ = d₂ / d₁
i-

Gear ratio

Z-

Tooth count

dmm

Pitch dia.

Governing Formula

T₂ = T₁ · i · η
T₂Nm

Output torque

T₁Nm

Input torque

η-

Efficiency

Governing Formula

Ft = 2·T₁ / d₁
FtN

Tangential load

T₁Nm

Pinion torque

d₁mm

Pinion pitch

Governing Formula

σ = Ft / (b · m · Y)
σMPa

Bending stress

bmm

Face width

mmm

Module

Y-

Lewis factor

Understanding Spur Gear Design and Tooth Strength

A spur gearbox transmits power between parallel shafts through a pair of gears whose teeth are straight and parallel to the axis. The first design decision is the gear ratio, fixed by the tooth counts: $i = Z_2 / Z_1$. Once the ratio is set, the output speed and torque follow directly from the input conditions and the mesh efficiency.

Module, Pitch Diameter and Center Distance

The module (m) is the fundamental size parameter of a metric gear — the pitch diameter equals $d = m \cdot Z$. Two meshing gears must share the same module, otherwise the teeth cannot engage. The center distance between shafts is simply $a = (d_1 + d_2)/2$, which locks the housing geometry.

Lewis Bending Equation

The classical Lewis equation treats each tooth as a cantilever beam loaded at the tip by the tangential force $F_t$. The resulting root bending stress is $\sigma = F_t / (b \cdot m \cdot Y)$, where $Y$ is the Lewis form factor depending on tooth count and pressure angle. A safety factor of at least 1.2–1.5 is normally required for steady industrial service.

Beyond the Lewis Check

The Lewis equation only covers static bending. A complete design must also verify surface (Hertz) contact stress, dynamic factors from pitch-line velocity, lubrication regime and fatigue life — typically using AGMA 2001 or ISO 6336 standards. This workspace gives you a fast, conservative first pass.

Frequently Asked Questions

What is the gear module and why does it matter?

The module (m) is the ratio of pitch diameter to tooth count, expressed in millimeters ($m = d / Z$). It defines the physical size of each tooth. Two meshing gears must share the same module — otherwise the teeth cannot engage. Changing the module while keeping the tooth count fixed scales the whole gear up or down and directly affects the bending strength.

How is Lewis bending stress used in gear design?

The Lewis equation models a gear tooth as a cantilever beam loaded at the tip by the tangential force. The resulting root stress $\sigma = F_t / (b \cdot m \cdot Y)$ is compared to the material's allowable bending stress. A safety factor above 1.2 is normally required for steady service; above 1.5 for shock loads. The Lewis check is a first-pass tool — full designs also require surface (Hertz) contact stress and fatigue analysis per AGMA/ISO.

Why does the pinion usually have fewer teeth than the gear?

In a reduction stage the pinion is the smaller, faster gear. It cycles through more load reversals per unit time, so its tooth root is the life-limiting element. Designers therefore size the module and face width around the pinion's bending stress. The minimum practical tooth count for a 20° pressure-angle spur gear without undercut is 17 teeth.