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Gear normal module $m_n$ is the gear normal pitch divided by $\pi$, measured normal to the tooth direction of a helical gear. It describes a different section from gear transverse module $m_t$, which uses the circumferential spacing in a plane perpendicular to the rotation axis.^[ref]

If $\beta$ is reference gear helix angle, geometric projection givesFor an original inference example, reference diameter $d=60\mathrm{mm}$, tooth count $N=30$ and $\beta =30{}^{\circ }$ imply $m_t=2\mathrm{mm}$ but $m_n=\sqrt{3}\mathrm{mm}\approx 1.73205\mathrm{mm}$. The normal pitch is approximately $5.4414\mathrm{mm}$, compared with transverse pitch $6.2832\mathrm{mm}$. This is a geometric example, not a claim that the inferred normal module belongs to a particular manufacturer's preferred series.

Conversely, specifying $m_n=2\mathrm{mm}$ for the same30 teeth and30degree helix angle gives reference diameter $69.282\mathrm{mm}$. Thus two drawings both labeled “module2” can describe different gears when one means normal module and the other transverse module.

Pressure angles need the same care: for reference tooth geometry, $\tan {\alpha }_t=\tan {\alpha }_n/\cos \beta$. Matching only a module number, without its plane, pressure-angle convention and helix geometry, does not establish a compatible pair. In a conventional parallel-axis external mesh, the two helical gears also require appropriate opposite hands; the normal-module definition alone does not specify that connection.

Gear overlap ratio measures the additional engagement overlap caused by a helical gear's tooth inclination across its gear face width. It is distinct from the transverse gear contact ratio, which measures contact length within one transverse section. For face width $b$, reference gear helix angle $\beta$ and gear normal module $m_n$,where $m_t$ is gear transverse module and $p_x$ is gear axial pitch.^[ref]

Unwrapping the reference cylinder explains the ratio: moving across axial width $b$ shifts the tooth pattern circumferentially by $b\tan |\beta |$. Dividing this shift by gear transverse pitch $\pi m_t$ counts how many tooth spacings the engagement progresses across the face.

For an original example, $b=20\mathrm{mm}$, $m_n=2\mathrm{mm}$ and $|\beta |=30{}^{\circ }$ giveDoubling the face width doubles this geometric overlap if the other parameters stay fixed. At the spur gear limit $\beta =0$, the overlap contribution tends to zero.

In the ideal cylindrical-helical model, total geometric contact ratio is the sum of transverse and axial contributions, ${ϵ}_{\gamma }={ϵ}_{\alpha }+{ϵ}_{\beta }$. This does not specify a uniform division of load: flexibility, alignment and the usable flank region affect actual contact. Increasing helix angle can improve overlap while also increasing gear axial force; increasing width also changes the alignment and support demands. These are related geometric tradeoffs, not a guarantee of a specified noise level or load capacity.

Gear transverse module $m_t$ specifies tooth spacing in the plane perpendicular to a cylindrical gear's axis. If $N$ is tooth count and $d$ is reference diameter, $m_t=d/N$, so reference-circle gear transverse pitch is $p_t=\pi m_t$. For a helical gear, this transverse section differs from the section normal to the tooth direction.^[ref]

Unwrapping the reference cylinder makes the tooth direction a slanted line. Projecting its normal spacing into the circumferential direction giveswhere $m_n$ is gear normal module and $\beta$ is reference gear helix angle. At zero helix angle the normal and transverse modules coincide, recovering the spur gear case.

For an original example, take $m_n=2.5\mathrm{mm}$, $\beta =30{}^{\circ }$ and $N=24$. Then $m_t\approx 2.88675\mathrm{mm}$ and $d\approx 69.282\mathrm{mm}$. A compatible 48-tooth gear has reference diameter $138.564\mathrm{mm}$, giving standard separation $103.923\mathrm{mm}$. Treating2.5 as the transverse module instead would incorrectly give diameters60 and120mm and separation90mm.

The transverse specification is convenient for reference diameters and axis separations, while the normal specification is convenient for the tooth-normal geometry. A drawing must identify which module and pressure-angle planes it uses; a numerical module value alone is incomplete for a helical gear. These are reference dimensions: a changed operating separation must additionally be interpreted through the mounted geometry, rather than redefining the gear's original module.

A helical gear is a cylindrical gear whose teeth follow a helix around the reference cylinder. The gear helix angle $\beta$ measures their inclination to the axis. In a conventional external pair on parallel axes, mating gears have opposite hands with matching helix-angle magnitudes. Inclination makes engagement progress across the face rather than beginning everywhere along a straight tooth at once, but also creates a gear axial force that the supports must carry.^[ref]

A helical gear must specify its reference plane. The gear normal module $m_n$ is based on a section normal to the tooth direction, whereas gear transverse module $m_t$ is based on the plane perpendicular to the gear axis. Their geometric relation isSimilarly, reference pressure angles satisfy $\tan {\alpha }_t=\tan {\alpha }_n/\cos \beta$. Equal numbers labeled “module” in different planes therefore need not specify interchangeable gears.^[ref]

For an original example, take $m_n=2\mathrm{mm}$, $N=20$ and $\beta =30{}^{\circ }$. Reference diameter is $46.188\mathrm{mm}$, rather than $40\mathrm{mm}$. With ${\alpha }_n=20{}^{\circ }$, the transverse angle is about $22.796{}^{\circ }$.

At standard mounting, a transmitted torque $2\mathrm{N}\mathrm{m}$ gives gear tangential force $F_t\approx 86.60\mathrm{N}$. Ideal contact-force resolution gives axial magnitudeIts direction depends on helix hand and transmitted-torque direction. The corresponding radial component uses the transverse gear pressure angle. This illustrates the design trade: distributed engagement can improve smoothness, but the same transmission requires axial-load support. The example concerns parallel-axis cylindrical gearing; it should not be applied unchanged to crossed-axis arrangements.