Introduction: The Workhorse of Gearing
Series Overview: This is Part 4 of our 24-part Mechanical Movements & Power Transmission Series. Now that we've established gear fundamentals in Part 3, we apply them to the most basic and widespread gear type: the spur gear.
1
Foundations of Mechanical Movement
Motion types, power transmission, history of machines
Completed
2
Pulleys, Belts & Rope Drives
Simple/compound pulleys, V-belts, chain drives
Completed
3
Gear Fundamentals & Geometry
Pitch, pressure angle, module, involute profile
Completed
4
Spur & Internal Gears
External/internal spur, friction gearing
You Are Here
5
Helical, Herringbone & Crossed Gears
Thrust forces, skew gears, double helical
6
Bevel, Miter & Hypoid Gears
Straight/spiral bevel, hypoid offset
7
Worm Gears & Self-Locking
Single/multi-start, efficiency, irreversibility
8
Planetary & Epicyclic Trains
Sun-planet-ring, compound planetary
9
Rack & Pinion, Scroll & Sector
Linear motion, mangle racks, sector gears
10
Gear Trains & Differentials
Simple/compound trains, differential mechanisms
11
Cams, Followers & Eccentrics
Plate/barrel/face cams, follower types
12
Cranks, Linkages & Four-Bar Mechanisms
Grashof condition, slider-crank, bell cranks
13
Ratchets, Pawls & Intermittent Motion
Geneva drive, mutilated gears, indexing
14
Screws, Toggle Joints & Presses
Lead screws, differential screws, mechanical advantage
15
Escapements & Clockwork
Anchor, deadbeat, lever escapements, horology
16
Governors, Regulators & Feedback
Centrifugal governors, Watt, speed control
17
Parallel & Straight-Line Motions
Watt, Chebyshev, Peaucellier linkages
18
Hydraulic & Pneumatic Movements
Pumps, cylinders, Pascal's law, compressors
19
Water Wheels, Turbines & Wind Power
Overshot/undershot, Pelton, Francis, wind mills
20
Steam Engines & Valve Gear
Reciprocating, rotary, Stephenson, Walschaerts
21
Gearmotors, Sensors & Encoders
DC/AC/stepper gearmotors, encoder feedback
22
Efficiency, Backlash & Contact Ratio
Power loss, anti-backlash, mesh analysis
23
Vibration, Noise & Failure Analysis
Gear tooth failure, resonance, diagnostics
24
Materials, Lubrication & Standards
AGMA/ISO, heat treatment, tribology
The spur gear is the simplest type of gear, with straight teeth cut parallel to the axis of rotation. Two meshing spur gears connect parallel shafts. In Brown's 507 Mechanical Movements, spur gears appear in entries #24, #34, #55, and #57, demonstrating their fundamental role in mechanical design from the Industrial Revolution onward.
Despite the development of more sophisticated gear types (helical, bevel, worm, planetary), spur gears remain the most widely manufactured gear type worldwide. Their simplicity, low cost, high efficiency (98-99% per mesh), and ease of manufacture make them the default choice whenever parallel-shaft power transmission is needed and noise is not the primary concern.
Key Insight: Spur gears produce no axial (thrust) forces because the teeth are parallel to the shaft axis. This simplifies bearing selection and housing design compared to helical or bevel gears, which generate significant thrust loads that must be managed with thrust bearings.
External Spur Gears
Basics & Operating Principles
An external spur gear has teeth cut on the outside of a cylindrical blank. When two external spur gears mesh, they rotate in opposite directions. The smaller gear is called the pinion and the larger is simply the gear (or wheel). The pinion is typically the driver in speed-reduction applications.
The tooth engagement process follows a specific sequence: as the driving tooth approaches the driven tooth, initial contact occurs near the root of the driver and the tip of the driven tooth. Contact then progresses along the line of action, passing through the pitch point (where pure rolling occurs with no sliding), and continues until the contact reaches the tip of the driver and root of the driven tooth.
This engagement-disengagement cycle means that the teeth experience sliding contact everywhere except at the pitch point, with the sliding velocity increasing with distance from the pitch point. This sliding generates friction, heat, and wear — which is why lubrication is essential for metal spur gears operating under load.
Advantages & Limitations
| Advantages |
Limitations |
| Simple design and manufacturing |
Noisy at high speeds (sudden tooth engagement) |
| No axial thrust forces |
Lower load capacity than helical (single tooth contact) |
| High efficiency (98-99%) |
Limited to parallel shaft arrangements |
| Wide range of ratios available |
Vibration at high speeds due to meshing impacts |
| Easy to inspect and measure |
Contact ratio limited to ~1.0-2.0 (typically 1.3-1.8) |
| Low cost (hobbing, molding) |
Not suitable for speed-sensitive applications above ~6 m/s pitch velocity |
Internal Spur Gears
Compact Design & Same-Direction Rotation (Brown's #34, #55)
An internal gear (also called a ring gear or annular gear) has teeth cut on the inside of a cylindrical ring. When an internal gear meshes with an external pinion, both gears rotate in the same direction, and the center distance equals the difference of the pitch radii rather than their sum.
Brown's Movement #34 illustrates the internal gear arrangement, showing how it produces a compact coaxial design. Movement #55 shows a variation used in early compound gear mechanisms. The key advantages of internal gears are:
- Same-direction rotation: Eliminates the need for an idler gear when same-direction output is required
- Compact design: The internal gear surrounds the pinion, reducing the overall package size
- Higher contact ratio: The concave-convex contact between internal gear and pinion produces a longer line of action and therefore a higher contact ratio than equivalent external pairs
- Greater load capacity: The concave tooth profile of the internal gear is stronger than the convex profile of an external gear with the same parameters
- Enclosed design: Naturally contains lubricant and protects the gear mesh from contamination
Design Constraints
Internal gears have additional design constraints beyond those of external gears:
- Minimum tooth difference: The number of teeth on the internal gear must exceed the pinion teeth by at least 10-12 (depending on pressure angle) to avoid tip interference (the tips of the internal and external teeth collide during assembly or operation)
- Trochoid interference: The tooth root fillet of the pinion can interfere with the tooth tip of the internal gear. This is checked using a trochoid analysis
- Manufacturing: Internal gears cannot be hobbed (the hob cannot reach inside). They must be shaped (reciprocating pinion cutter), broached, or wire-EDM machined
- Assembly: The pinion must be inserted through the bore of the internal gear, which may require axial assembly access
Design Rule: For a 20-degree pressure angle, the minimum tooth difference (N_internal - N_pinion) should be at least 12. For 25 degrees, at least 10. Failing to meet this minimum results in interference during assembly or operation, potentially locking the gears.
Gear Ratio & Speed Calculations
Multi-Stage Gear Trains
For ratios greater than approximately 6:1, a single pair of spur gears becomes impractical (the gear becomes very large relative to the pinion). Multi-stage gear trains solve this by cascading multiple pairs:
Total ratio = i_1 * i_2 * i_3 * ...
A two-stage gear train with 4:1 per stage achieves 16:1 total ratio with much smaller gears than a single-stage 16:1 pair. Each intermediate shaft carries a large gear (driven by the previous stage) and a small pinion (driving the next stage) on the same shaft.
Interference & Undercutting
Minimum Number of Teeth
Tooth interference occurs when the tip of a gear tooth contacts the non-involute (fillet) portion of the mating tooth. This happens when gears have too few teeth, causing the contact path to extend beyond the base circle. The result is a gouging action that removes material from the tooth root — this is called undercutting.
The minimum number of teeth to avoid undercutting with a standard rack (full-depth teeth, standard addendum) is:
N_min = 2 / sin^2(phi)
| Pressure Angle |
Minimum Teeth (Theoretical) |
Practical Minimum |
| 14.5 degrees |
32 |
23 (slight undercut acceptable) |
| 20 degrees |
17 |
14 (with profile shift) |
| 25 degrees |
12 |
10 (with profile shift) |
Undercutting weakens the tooth (material removed at the highest stress region) and reduces the contact ratio (the involute portion of the tooth is shortened). Even mild undercutting should be avoided in loaded power gears.
Profile Shift Correction
Profile shift (also called addendum modification or gear correction) is a technique where the cutting tool is moved radially outward from its standard position when cutting the gear. A positive profile shift thickens the tooth at the root and moves the involute profile away from the base circle, eliminating or reducing undercutting.
Profile shift is specified by the profile shift coefficient (x), where x = 0 is standard, x > 0 is positive shift (thicker teeth), and x < 0 is negative shift (thinner teeth). Typical values range from -0.5 to +0.5. For a pinion with fewer teeth than the minimum, a positive shift of x = 0.3 to 0.5 can eliminate undercutting while maintaining proper mesh with a mating gear that has zero or negative shift.
Balance Rule: For a gear pair, the sum of profile shift coefficients (x1 + x2) should ideally be zero or slightly positive. Positive sum increases center distance; negative sum decreases it. The AGMA/ISO standards provide detailed tables for optimal profile shift combinations based on gear ratio and pinion tooth count.
Friction Gearing
Smooth Rollers for Light Loads (Brown's #28, #32, #45, #413)
Friction gearing uses smooth cylindrical or conical rollers pressed together to transmit motion and power through friction alone, without teeth. Brown's movements #28, #32, #45, and #413 illustrate various friction drive arrangements.
Friction drives have significant advantages for specific applications: completely silent operation, no backlash, inherent overload protection (the rollers slip rather than breaking teeth), and very simple construction. However, they can only transmit limited torque before slipping, and the high contact pressure required for adequate friction generates significant bearing loads.
The maximum transmittable torque is: T = mu * F * r, where mu is the friction coefficient, F is the normal (pressing) force between rollers, and r is the roller radius. With steel-on-steel (mu = 0.15-0.20) and reasonable contact pressures, friction drives are limited to light-duty applications.
Modern applications include paper feed mechanisms in printers, phonograph turntable drives, CVTs (continuously variable transmissions using cone-and-roller arrangements), and precision instrument drives where zero backlash is critical.
Crown & Stud Gearing (Brown's #26, #197, #219)
Brown's Movement #26 and #219 show crown gears (also called face gears), which have teeth cut on the flat face of a disc rather than on the circumference. A crown gear meshes with a standard spur pinion at right angles, providing a simple method for 90-degree power transmission without requiring bevel gears. Crown gears have limited load capacity but are easy to manufacture and were common in early clockwork and light machinery.
Movement #197 illustrates stud gearing, where cylindrical pins (studs) projecting from the face of a disc engage with slots or gaps in a mating member. Stud gearing is a primitive form of toothed gearing that was widely used in wooden mill mechanisms before precision metal gear cutting became available.
Spur Gear Design Procedure
Follow these steps for a systematic spur gear design:
- Define requirements: Input power, input speed, output speed (or ratio), service life, space constraints, noise limits
- Calculate gear ratio: i = n_input / n_output. Determine if single-stage (i < 6) or multi-stage is needed
- Select number of teeth: Choose pinion teeth (minimum 17 for 20-degree PA, more for quieter operation). Gear teeth = pinion teeth * ratio
- Select module: Based on tooth bending strength (Lewis equation) and surface contact stress (Hertz equation). Use AGMA 2001 or ISO 6336 rating methods
- Calculate geometry: Pitch diameters, center distance, addendum/dedendum, face width
- Check contact ratio: Must be > 1.2 (preferably > 1.4)
- Check for interference: Verify no undercutting; apply profile shift if needed
- Verify stresses: Bending stress and contact stress must be below allowable limits for chosen material and heat treatment
- Specify tolerances: Select AGMA/ISO quality grade based on speed and noise requirements
- Select material and heat treatment: Through-hardened, case-carburized, nitrided, or induction-hardened based on stress levels and application
Case Studies
Case Study 1: Clock Mechanisms
Mechanical clocks use trains of spur gears to step down the high-speed escapement (4-5 beats per second) to the minute and hour hands. A typical clock gear train uses 4-5 stages of reduction, with ratios carefully chosen so that the minute hand shaft rotates once per hour and the hour hand once per 12 hours. The gear teeth are very fine (module 0.3-0.5), typically made from brass, and operate at negligible loads — accuracy of the gear ratio is the primary design criterion, not load capacity.
Case Study 2: Simple Industrial Gearbox
A conveyor belt requires 50 RPM from a 1750 RPM motor. The total ratio needed is 35:1, far too high for a single spur gear stage. Solution: a 3-stage spur gear reducer with ratios of approximately 3.3:1 per stage (3.3^3 = 35.9). Each stage uses a 20-tooth pinion and 66-tooth gear (ratio 3.3:1), module 3, 20-degree pressure angle. The total gearbox is compact, efficient (0.98^3 = 94.1%), and straightforward to manufacture.
Case Study 3: Conveyor Drive with Internal Gear
An internal gear arrangement is used in the final stage of a conveyor drive where coaxial input and output shafts are required. The motor drives a sun pinion (24 teeth), which meshes with an internal ring gear (72 teeth), giving a 3:1 reduction in a compact, enclosed package. The same-direction rotation of the internal gear arrangement eliminates the need for an idler gear. This configuration forms the basis of simple planetary reducers used extensively in conveyor and winch drives.
Python Calculations
import math
class SpurGearPair:
"""Complete spur gear pair design calculator."""
def __init__(self, module, pinion_teeth, gear_teeth,
pressure_angle_deg=20.0, face_width_factor=10):
self.m = module
self.Np = pinion_teeth
self.Ng = gear_teeth
self.phi = math.radians(pressure_angle_deg)
self.phi_deg = pressure_angle_deg
self.face_width = face_width_factor * module
# --- Gear Ratio ---
@property
def ratio(self):
return self.Ng / self.Np
# --- Pitch Diameters ---
@property
def dp(self):
"""Pinion pitch diameter (mm)."""
return self.m * self.Np
@property
def dg(self):
"""Gear pitch diameter (mm)."""
return self.m * self.Ng
# --- Center Distance ---
@property
def center_distance(self):
"""Center distance for external gear pair (mm)."""
return (self.dp + self.dg) / 2
@property
def center_distance_internal(self):
"""Center distance for internal gear pair (mm)."""
return (self.dg - self.dp) / 2
# --- Speed & Torque ---
def output_speed(self, input_rpm):
"""Calculate output RPM given input RPM."""
return input_rpm / self.ratio
def output_torque(self, input_torque, efficiency=0.98):
"""Calculate output torque given input torque (Nm)."""
return input_torque * self.ratio * efficiency
# --- Interference Check ---
@property
def min_pinion_teeth(self):
"""Minimum pinion teeth to avoid undercutting."""
return math.ceil(2 / (math.sin(self.phi) ** 2))
@property
def has_undercutting(self):
return self.Np < self.min_pinion_teeth
# --- Contact Ratio ---
@property
def contact_ratio(self):
"""Profile contact ratio for external spur gear pair."""
rp = self.dp / 2
rg = self.dg / 2
rap = rp + self.m # addendum circle radius
rag = rg + self.m
rbp = rp * math.cos(self.phi)
rbg = rg * math.cos(self.phi)
C = self.center_distance
base_pitch = math.pi * self.m * math.cos(self.phi)
path_length = (math.sqrt(rap**2 - rbp**2) +
math.sqrt(rag**2 - rbg**2) -
C * math.sin(self.phi))
return path_length / base_pitch
# --- Pitch Line Velocity ---
def pitch_velocity(self, pinion_rpm):
"""Pitch line velocity (m/s)."""
return math.pi * self.dp * pinion_rpm / 60000
# --- Lewis Bending Stress Estimate ---
def lewis_stress(self, tangential_force_N, lewis_form_factor=0.32):
"""
Estimate bending stress using Lewis equation (simplified).
Args:
tangential_force_N: Tangential tooth force in Newtons
lewis_form_factor: Y factor (0.32 typical for 20T, 20deg PA)
Returns:
Bending stress in MPa
"""
return tangential_force_N / (self.face_width * self.m * lewis_form_factor)
def summary(self, input_rpm=1750):
print(f"=== Spur Gear Pair Design ===")
print(f"Module: {self.m} mm | PA: {self.phi_deg} deg")
print(f"Pinion: {self.Np} teeth, d={self.dp:.1f} mm")
print(f"Gear: {self.Ng} teeth, d={self.dg:.1f} mm")
print(f"Ratio: {self.ratio:.3f}:1")
print(f"Center distance (ext): {self.center_distance:.2f} mm")
print(f"Center distance (int): {self.center_distance_internal:.2f} mm")
print(f"Face width: {self.face_width:.1f} mm")
print(f"Contact ratio: {self.contact_ratio:.3f}")
print(f"Min teeth (no UC): {self.min_pinion_teeth}")
print(f"Undercut risk: {'YES' if self.has_undercutting else 'No'}")
print(f"\nAt {input_rpm} RPM input:")
print(f" Output speed: {self.output_speed(input_rpm):.1f} RPM")
print(f" Pitch velocity: {self.pitch_velocity(input_rpm):.2f} m/s")
if input_rpm > 0:
power_W = 5000 # 5 kW example
Ft = power_W / (self.pitch_velocity(input_rpm))
print(f"\n For 5 kW power transmission:")
print(f" Tangential force: {Ft:.1f} N")
print(f" Est. bending stress: {self.lewis_stress(Ft):.1f} MPa")
# Example: Design a 4:1 reduction
pair = SpurGearPair(module=3, pinion_teeth=20, gear_teeth=80)
pair.summary(input_rpm=1750)
# Example: Internal gear arrangement
print("\n--- Internal Gear (same teeth) ---")
print(f"Center distance (internal): {pair.center_distance_internal:.2f} mm")
print(f"Package OD: {pair.dg + 2*pair.m:.1f} mm (very compact!)")
print(f"Tooth difference: {pair.Ng - pair.Np} (min recommended: 12)")
Exercises & Self-Assessment
Exercise 1
Spur Gear Pair Design
Design a spur gear pair for these requirements:
- Input: 1450 RPM electric motor
- Output: approximately 350 RPM
- Power: 7.5 kW
- Select appropriate module, tooth counts, and calculate all geometry
- Verify contact ratio and check for undercutting
- Calculate the tangential force and estimate bending stress
Exercise 2
Internal Gear Analysis
Analyze an internal gear pair:
- Pinion: 18 teeth, module 4, 20-degree pressure angle
- Internal gear: 54 teeth
- Calculate center distance, gear ratio, and verify minimum tooth difference
- Compare the package diameter with an equivalent external gear pair of the same ratio
- List three applications where an internal gear would be preferred over an external pair
Exercise 3
Multi-Stage Gear Train
Design a multi-stage spur gear reducer:
- Total ratio needed: 25:1 (from 1750 RPM motor to 70 RPM output)
- Determine the optimal number of stages and ratio per stage
- Select tooth counts for each stage (minimum 18 teeth on all pinions)
- Calculate the overall efficiency assuming 98% per mesh
- Calculate the total center-to-center distance (width of gearbox)
Exercise 4
Reflective Questions
- Why are spur gears still the most common gear type despite being noisier than helical gears? Under what conditions would you choose spur over helical?
- Explain physically what causes undercutting. Draw a sketch showing what happens when a standard rack generates a gear with too few teeth.
- Profile shift is sometimes called "the most powerful tool in the gear designer's toolkit." Explain three different problems that profile shift can solve.
- Why does an internal gear pair have a higher contact ratio than an external pair with the same tooth counts? Think about the geometry of concave-convex contact vs. convex-convex contact.
- Friction gearing is seeing a renaissance in modern CVTs and precision drives. What fundamental limitation prevents friction drives from replacing gears in high-power applications?
Conclusion & Next Steps
You now have a comprehensive understanding of spur and internal gears. Here are the key takeaways from Part 4:
- External spur gears are the simplest, most efficient (98-99%), and most widely manufactured gear type — the default choice for parallel-shaft power transmission
- Internal gears provide same-direction rotation, compact coaxial design, higher contact ratio, and form the basis of planetary gear systems
- Gear ratio = N_driven/N_driver — when speed decreases, torque increases proportionally (conservation of power)
- Undercutting occurs below 17 teeth (at 20-degree PA) and weakens the tooth at its most critical point — profile shift correction can prevent it
- Friction gearing offers zero backlash and silent operation for light loads, with modern applications in CVTs and precision instruments
- Systematic design procedure from requirements through geometry, stress analysis, and material selection ensures reliable gear performance
Next in the Series
In Part 5: Helical, Herringbone & Crossed Gears, we explore gears with angled teeth. Helical gears solve the noise and load capacity limitations of spur gears through gradual engagement, but introduce axial thrust forces. Herringbone (double helical) gears elegantly eliminate thrust, while crossed helical gears handle non-parallel, non-intersecting shafts.
Continue the Series
Part 5: Helical, Herringbone & Crossed Gears
Angled teeth for smoother, quieter operation. Thrust forces, herringbone designs, and crossed helical configurations.
Read Article
Part 3: Gear Fundamentals & Geometry
Pitch, pressure angle, module, involute profile, conjugate action, contact ratio, and gear standards.
Read Article
Part 6: Bevel, Miter & Hypoid Gears
Gears for intersecting and offset shaft axes: straight bevel, spiral bevel, and hypoid configurations.
Read Article