Gear Base Diameter
Calculate the base circle diameter of an involute gear, d_b = d·cos(φ), from the pitch diameter d (mm) and the pressure angle φ (degrees). The base circle is the circle from which the INVOLUTE tooth profile is generated — the standard profile of modern gears. The involute is the curve traced by the tip of a string unwinding from a cylinder: that cylinder is exactly the base circle. The entire active tooth profile (the part that actually transmits force) is ABOVE the base circle; below it there is no involute profile. The base diameter is fundamental in gear geometry because it defines the involute profile and, with it, key properties: the LINE OF ACTION (the line tangent to both base circles of the mesh, along which tooth contact travels, always in the same direction — why involute gears transmit uniform motion), the base pitch and the contact ratio. The relation d_b = d·cos(φ) shows that the pressure angle is the angle between the line of action and the tangent to the pitch circles. It is an essential parameter in designing and manufacturing (generating) involute gears. Enter the pitch diameter and the pressure angle.
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Gear base diameter
The base circle diameter of an involute-toothed gear is d_b = d·cos(φ), built from the pitch diameter d and the pressure angle φ. The base circle is the circumference from which the involute tooth profile is generated — the standard profile of modern gearing. The involute is the curve traced by the end of a taut string as it unwinds from a cylinder: that cylinder is precisely the base circle. The whole active flank of the tooth (the part that actually transmits force) lies above the base circle; below it there is no involute profile at all. The base diameter matters because it defines the involute profile and, with it, key properties: the line of action (the straight line tangent to both base circles, along which the contact between teeth travels, always in the same direction — the reason involute gears transmit uniform motion, with no velocity fluctuation), the base pitch and the contact ratio. The relation d_b = d·cos(φ) shows that the pressure angle is the angle between the line of action and the tangent to the pitch circles — and that it is also the inclination of the force transmitted between the teeth (hence the name 'pressure angle'). It is an essential parameter in the design and in the manufacture (generation) of involute gears. Enter the pitch diameter and the pressure angle.
Related Tools
Minimum Pinion Teeth
Calculate the minimum number of pinion teeth to avoid interference, z_min = 2 ÷ sin²(φ), from the pressure angle φ (degrees). Interference is a geometric problem occurring when gears with FEW teeth mesh: the pinion tooth flank (the part below the base circle, where the involute profile does not exist) collides with the larger gear's tooth tip, causing vibration, noise, rapid wear or jamming. To avoid it, the pinion needs a minimum tooth count depending on the pressure angle: LARGER pressure angles ('fatter' teeth at the root) allow pinions with FEWER teeth without interference. For the standard 20° pressure angle, the theoretical minimum is about 17-18 teeth; for 14.5° (old standard), about 32; for 25°, about 12. When a pinion with fewer than the minimum is needed (for a high gear ratio in little space), profile CORRECTION (profile shift, corrected teeth) or undercut (root relief) is used, avoiding interference at the cost of weakening the tooth. This calculation is fundamental in designing a gear pair's geometry. Enter the pressure angle.
Cam Pressure Angle
Calculate the pressure angle of a radial translating-follower cam, α = arctan((ds/dθ) ÷ (R_b + s)), from the displacement derivative with respect to angle ds/dθ (mm/rad, the profile 'slope'), the base circle radius R_b (mm) and the follower displacement s (mm). The pressure angle is the angle between the direction of the FORCE the cam applies to the follower (normal to the profile, at the contact point) and the direction of the follower MOTION. It is a critical design parameter: the LARGER the pressure angle, the greater the LATERAL force component (perpendicular to follower motion), which does no useful work but pushes the follower against its guides, causing friction, wear and possibly JAMMING the follower if excessive. The rule of thumb limits the pressure angle to about 30° (less for translating followers with long guides). The pressure angle depends on the profile (ds/dθ, steeper = larger angle), the base radius (larger cams have smaller angles and smoother operation) and the displacement. So when the pressure angle comes out excessive, the solution is to INCREASE the base circle radius (bigger cam) — at the cost of more space, mass and peripheral speed. Controlling the pressure angle is essential for smooth, durable operation. Enter the displacement derivative, the base radius and the displacement.
Gear Base Pitch
Calculate the base pitch of an involute gear, p_b = π·m·cos(φ), from the module m (mm) and the pressure angle φ (degrees). The base pitch is the distance between two homologous flanks of consecutive teeth, measured along the base circle (or, equivalently, along the line of action) — different from the circular pitch (π·m), measured on the pitch circle. The base pitch is a FUNDAMENTAL property of involute meshing for an elegant reason: for two meshes to transmit motion correctly, they must have the SAME base pitch — it is the conjugacy condition of involute profiles. Moreover, the base pitch appears directly in the CONTACT RATIO (the average number of teeth in simultaneous contact, found by dividing the line-of-action length by the base pitch): a contact ratio above 1 (ideally above 1.4) ensures there is always at least one tooth pair meshed, transmitting motion continuously and smoothly, without impacts. The base pitch is also the basis of checking gears 'over two pins' or by span measurement (W over teeth), classic dimensional-control methods. It is an essential parameter in gear geometry and metrology. Enter the module and the pressure angle.
Thickness/Diameter Ratio (Thin Wall)
Calculate a pressure vessel's thickness/diameter ratio, t/D, from the wall thickness t and the diameter D (same unit). This ratio is the criterion deciding whether a vessel can be treated as THIN-walled or needs THICK-walled (Lamé) theory. The distinction is fundamental because the formulas change: in THIN walls (rule of thumb t/D < 0.05, or t/r < 0.1), stress is practically UNIFORM across the thickness, and the simple membrane formulas hold (σ = P·r/t for hoop) — the case of the vast majority of vessels, pipes and tanks. In THICK walls (larger t/D, as in very-high-pressure vessels — hydrogenation reactors, gun barrels, high-pressure hydraulic tubing), stress VARIES strongly across the thickness (maximum at the inner surface, decreasing outward), and the simple formulas dangerously underestimate the inner peak stress — Lamé's equations must be used. Checking the t/D ratio is thus the first step in choosing the correct calculation theory. Vessels with t/D above ~0.1 require thick-wall analysis. This simple check avoids the serious error of applying thin-wall formulas to a thick vessel. Enter the thickness and the diameter.
Cam Pitch Radius
Calculate the pitch radius of a roller-follower cam, R_p = R_b + R_r, from the base circle radius R_b (mm) and the follower roller radius R_r (mm). In ROLLER-follower cams (a bearing rolling on the cam profile, reducing friction versus flat-face or knife-edge followers), two important curves are distinguished: the real PROFILE of the cam (the physical surface the roller touches) and the PITCH curve, the locus of the roller CENTER as it follows the cam. The pitch curve is designed first (from the displacement diagram), and the real profile is obtained by 'offsetting' the roller radius from the pitch curve. The pitch radius, at the base position, is the sum of the base circle radius and the roller radius. This distinction is fundamental for a practical reason: the roller radius cannot exceed the smallest RADIUS OF CURVATURE of the pitch curve in CONCAVE regions, or the roller does not 'fit' and the cam gets an incorrect profile (undercutting), distorting the motion. So the choice of roller radius and base radius is coupled to the cam geometry. The pitch radius also enters the pressure-angle and peripheral-speed calculations. Enter the base circle radius and the roller radius.
Gear Torque
Calculate the torque transmitted by a gear, T = (F_t·d) ÷ 2000, from the tangential force F_t (N) and the pitch diameter d (mm); the result is in N·m (the 2000 converts d/2 from mm to m). Torque is the moment the gear transmits about its axis, and the tangential force F_t acts at the pitch radius (d/2), creating that moment. This relation is the bridge between the POWER/torque side (what the shaft transmits) and the TOOTH-FORCE side (what sizes the strength): from shaft torque, the tooth tangential force (F_t = 2T/d) is obtained, which then feeds the bending (Lewis) and contact (Hertz) calculations. Conversely, given the tangential force, the torque is obtained. In a gear train, torque CHANGES at each stage by the gear ratio (a reduction that multiplies speed by 1/i multiplies torque by i, conserving power minus losses), while power stays roughly constant. So a reducer's last stage (low speed) transmits the HIGHEST torque and needs the most robust gears. Knowing the torque at each gear is essential to size teeth, shafts, keys and bearings. Enter the tangential force and the pitch diameter.
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