Mechanical Engineering Calculator

Shaft Design Calculator

Calculate the minimum required diameter of a solid circular shaft subjected to combined bending moment and torsion using the ASME maximum shear stress theory.

Shaft Configuration

Solid circular shaft under combined bending moment and torsion (ASME)

T = 350000 N·mmM = 180000 N·mmdL (optional for twist)

Input Parameters

SI units: N·mm for moments, MPa for stresses, mm for diameter.

N·mm

Applied torsional moment (1 N·m = 1000 N·mm)

N·mm

Maximum bending moment at the critical section

MPa

Material yield strength (0.2 % proof stress)

MPa

Used for ASME 0.18·Sut limit

Shock & fatigue (typical 1.5–2.0)

Shock & fatigue (typical 1.0–1.5)

Power → Torque Helper

kW

Transmitted power in kilowatts.

rpm

Rotational speed of the shaft.

Optional – Angular Deflection

mm

Length of the shaft between the points where twist is measured.

MPa

≈ 80 000 MPa for steel

Minimum Required Diameter

31.50mm

Allowable Shear τ

72.0 MPa

Pure Torsion Dia.

29.15 mm

Angular Deflection (Twist)

θ = 2.074° over the given length. Typical allowable limits are 0.25°–0.5° per meter of shaft.

Governing Formula (ASME)

d³ = (16 / (π τ_allow)) · √[(Kb M)² + (Kt T)²]
dmm

Minimum shaft diameter

TN·mm

Applied torque

MN·mm

Bending moment

τ_allowMPa

Allowable shear stress

Kb

Bending shock & fatigue factor

Kt

Torsion shock & fatigue factor

Calculation Assumptions

  • Solid circular cross-section
  • Maximum shear stress theory (ASME)
  • Linear elastic material behavior
  • Constant diameter (no steps)
  • No axial load considered
  • Stress concentration handled via Kb/Kt

Engineering Code

Reuse the calculation in your own workflow.

Python
def shaft_diameter(T, M, tau_allow, Kb=1.5, Kt=1.0):
    """
    Minimum solid shaft diameter under combined bending + torsion
    (ASME maximum shear stress theory).

    T, M      : N·mm
    tau_allow : MPa
    Returns   : diameter in mm
    """
    import math
    if tau_allow <= 0 or Kb <= 0 or Kt <= 0:
        raise ValueError("Invalid parameters")
    equivalent = math.sqrt((Kb * M)**2 + (Kt * T)**2)
    d_cubed = (16 / (math.pi * tau_allow)) * equivalent
    return d_cubed ** (1/3)


# Example
T = 350000      # N·mm
M = 180000
tau = 72.0
Kb = 1.5
Kt = 1.0

d = shaft_diameter(T, M, tau, Kb, Kt)
print(f"Required diameter: {d:.2f} mm")
MATLAB
function d = shaft_diameter(T, M, tau_allow, Kb, Kt)
    % Minimum solid shaft diameter (ASME max. shear stress)
    % T, M in N·mm, tau_allow in MPa → d in mm

    if nargin < 4, Kb = 1.5; end
    if nargin < 5, Kt = 1.0; end

    equivalent = sqrt((Kb*M)^2 + (Kt*T)^2);
    d_cubed = (16 / (pi * tau_allow)) * equivalent;
    d = d_cubed^(1/3);
end

% Example
T = 350000;
M = 180000;
tau = 72.0;
d = shaft_diameter(T, M, tau, 1.5, 1.0);
fprintf('Required diameter: %.2f mm\n', d);
Excel Formula
=POWER((16/(PI()*tau))*SQRT((Kb*M)^2+(Kt*T)^2),1/3)

Example Calculation

A steel shaft (Sy = 250 MPa, Sut = 400 MPa) transmits 350 N·m torque and experiences a maximum bending moment of 180 N·m. Using Kb = 1.5, Kt = 1.0 and no keyway:

τ_allow = min(0.30 × 250, 0.18 × 400) = 55 MPa
d³ = (16 / (π × 55)) × √[(1.5 × 180000)² + (1.0 × 350000)²]
d ≈ 42.1 mm

Technical Explanation: Shaft Design under Combined Loading

Transmission shafts are almost always subjected to both torsion (from the transmitted power) and bending (from gears, pulleys, sprockets or belt tensions). The ASME code for the design of transmission shafting uses the maximum shear stress theory together with empirical shock and fatigue factors to size the shaft diameter.

The governing equation is:

d³ = (16 / (π τ_allow)) · √[(Kb M)² + (Kt T)²]

How to Use This Calculator

  1. Torque (T): Enter the torsional moment in N·mm (or use the Power → Torque helper).
  2. Bending Moment (M): Maximum bending moment at the critical section (N·mm).
  3. Yield Strength (Sy): Material 0.2 % proof stress in MPa.
  4. Ultimate Strength (optional): Used to apply the ASME 0.18·Sut limit.
  5. Kb & Kt: Shock and fatigue factors (typical values shown in the UI).
  6. Keyway checkbox: Applies the mandatory 25 % reduction of allowable shear stress.

Typical Shock & Fatigue Factors

  • Gradually applied / steady load → Kb = 1.5, Kt = 1.0
  • Suddenly applied, minor shock → Kb = 1.5–2.0, Kt = 1.0–1.5
  • Heavy shock → Kb = 2.0–3.0, Kt = 1.5–3.0

Real-World Engineering Cases

Gearbox Input Shaft Failure (Overhung Load)

A high-speed gearbox input shaft failed after only 800 hours. Investigation showed that the coupling was mounted with excessive overhung distance, producing a bending moment far higher than the design value used in the original ASME calculation.

Engineering Lesson

Always verify the actual location of applied forces relative to the bearings. An extra 50 mm of overhung length can easily double the bending moment and invalidate the diameter selection.

Keyway-Induced Fatigue Crack

A 45 mm shaft transmitting 22 kW at 1500 rpm developed a fatigue crack originating at the sharp corner of a keyway. The original design had used the full allowable shear stress without the mandatory 25 % reduction.

Engineering Lesson

Never omit the keyway reduction factor. Even a well-designed fillet radius cannot fully compensate for the stress concentration and section reduction caused by a keyway.

Frequently Asked Questions

What formula does this calculator use?

The ASME maximum shear stress equation for solid shafts under combined bending and torsion: d³ = (16/(π τ_allow)) · √[(Kb M)² + (Kt T)²].

How is allowable shear stress determined?

According to ASME: τ_allow = min(0.30·Sy , 0.18·Sut). If a keyway is present the value is further reduced by 25 %.

What units should I use?

Torque and bending moment in N·mm, stresses in MPa, diameter result in mm. (1 N·m = 1000 N·mm)

Does the calculator consider hollow shafts?

The current version is for solid circular shafts only. Hollow-shaft equations replace the polar moment term with (1 – k⁴) where k = di/do.

Engineering calculations provided by this tool are for educational and preliminary design purposes. Always verify calculations, loading conditions, material properties, applicable standards, safety factors, and design requirements before using results in a final engineering design. Stress concentrations, fatigue life and critical speed checks are additional steps that must be performed separately.