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Shaft Size Calculator

Table of contents

Considerations when calculating shaft designCalculating shaft diameter for torque onlyCalculating shaft design for bending moment onlyCalculating shaft design for combined twisting and bending momentCalculating shaft size for fluctuating torsion and bending momentsCalculating minimum shaft diameter for torsional rigidityUsing this shaft size calculatorFAQs

Welcome to our shaft size calculator, your one-stop site for designing a shaft ideal for your requirements. When designing a shaft, we start with calculating the minimum diameter the shaft must have to withstand various loads. Whether you wish to calculate the diameter of a hollow shaft or a solid shaft, our calculator can assist you.

You would be forgiven for being confused with the shaft design process, for there is much to consider. Fret not — in the article below, we shall discuss the essential fundamentals of calculating shaft design for various loads.

Considerations when calculating shaft design

A shaft is a rotating member that transmits power between two parts through a twisting moment or torque. Machine parts such as gears or pulleys can be mounted onto the shaft to transmit power from or to the shaft.

Most shafts are of circular cross-section. Hence, calculating shaft size or designing a shaft entails the calculation of shaft diameter. While designing a shaft, one has to ensure that the stresses acting on the shaft are within the permissible limits. The stresses one needs to consider for shaft design are:

  1. Shear stress while carrying torque (torsion load).

  2. Bending stress due to members like gears and pulleys, along with the shaft's weight.

  3. Stresses developed due to combined torsional and bending loads.

So we must consider the types of load the shaft will undergo before calculating shaft size. We can base the shaft design on any one of the following:

  1. Shaft transmitting torque only.

  2. Shaft under bending moment only.

  3. Shaft subjected to a combination of twisting and bending moments.

  4. Shaft under fluctuating twisting and bending moments.

  5. Shaft with a desired torsional rigidity.

In the following sections, we shall discuss the shaft design process for each case listed above one by one.

Calculating shaft diameter for torque only

Some shafts are designed for carrying torque alone from one place to another. Any effect from other loads is negligible. Calculation of propeller shaft size could fall into this category.

In such cases, we can use the torsion equation to calculate the shaft size:

TJ=τr(1)\tag{1} \frac{T}{J} = \frac{\tau}{r}


  • TTTwisting moment acting on the shaft;

  • JJPolar moment of inertia about the shaft's rotational axis;

  • τ\tauTorsional shear stress; and

  • rrDistance from the neutral axis to the outermost fiber, equal to the shaft radius for circular cross-section.

r=d2(2)\qquad \tag{2} r = \frac{d}{2}

where dd is the diameter of the shaft.

The polar moment of inertia JJ for a solid circular shaft is given by:

J=π32×d4(3)\tag{3} J = \frac{\pi}{32} \times d^4

🔎 Are you curious why this is the case? Head to our polar moment of inertia calculator.

Substituting (2) and (3) in (1), we get:

T=π16×τd3(4)\tag{4} T = \frac{\pi}{16} \times \tau \cdot d^3

Thus, we can calculate the shaft diameter from the torque it carries and the allowable shear stress.

🙋 Remember that we just calculated the minimum shaft diameter. You can find a standard-sized shaft with a diameter greater than this value.

Let's now calculate the diameter of a hollow shaft. The polar moment of inertia for a hollow shaft is given by:

J=π32[do4di4](5)\tag{5} J = \frac{\pi}{32} \left[ d_o^4 - d_i^4 \right]


  • dod_o — Outer diameter of the hollow shaft; and

  • did_i — Inner diameter of the hollow shaft.

Similarly, rr is given by:

r=do2(6)\tag{6} r = \frac{d_o}{2}

Substituting (5) and (6) in (1), we arrive at:

T=π16×τ[do4di4do](7)\tag{7} T = \frac{\pi}{16} \times \tau \left[ \frac{d_o^4 - d_i^4}{d_o}\right]

Introducing k=di/dok = d_i / d_o, the ratio of inner to the outer diameter, we can simplify this to:

T=π16×τdo3(1k4)(8)\tag{8} T = \frac{\pi}{16} \times \tau \cdot d_o^3 (1-k^4)

So, in addition to torque and the allowable shear stress, we need to know kk, the ratio between inner and outer diameter.

🙋 You can also calculate a shaft's diameter from the power it transmits. This is possible due to the relation between torque and power, given by P=2πNT/60P = 2 \pi NT / 60. To learn more about this torque-power conversion, visit our torque to hp calculator.

Calculating shaft design for bending moment only

Shafts are rarely designed to handle bending moment only but say you are designing a shaft with negligible torsional loads. In such cases, the allowable stress in the shaft is given by the bending equation:

MI=σby(9)\tag{9} \frac{M}{I} = \frac{\sigma_b}{y}


  • MMBending moment acting on the shaft;

  • IIMoment of inertia of the shaft's cross-section;

  • σb\sigma_bBending stress acting on the shaft; and

  • yyDistance from the neutral axis to the outermost fiber.

For a circular cross-section solid shaft, the moment of inertia would be:

I=π64×d4(10)\tag{10} I = \frac{\pi}{64} \times d^4

🔎 Learn more with our moment of inertia calculator.

And yy would be:

y=d2(11)\tag{11} y = \frac{d}{2}

Substituting (10) and (11) in (9), we get the formula to calculate shaft diameter:

M=π32×σbd3(12)\tag{12} M = \frac{\pi}{32} \times \sigma_b \cdot d^3

Now let's calculate the diameter of a hollow shaft. The moment of inertia would be:

I=π64×[do4di4](13)\tag{13} I = \frac{\pi}{64} \times [d_o^4 - d_i^4]

And yy would be:

y=do2(14)\tag{14} y = \frac{d_o}{2}

Substituting (13) and (14) in (9) and using k=di/dok = d_i / d_o, we arrive at:

M=π32×σbdo3(1k4)(15)\tag{15} M = \frac{\pi}{32} \times \sigma_b \cdot d_o^3 (1-k^4)

Calculating shaft design for combined twisting and bending moment

When a combination of twisting and bending moments are acting on a shaft, the combined stresses must be accounted for. Two important theories for calculating these combined stresses are:

  1. Maximum shear stress theory (or Guest's theory) states that the maximum shear stress τmax\tau_{\rm max} in the shaft is given by:
τmax=12σb2+4τ2(16)\qquad \tag{16}\tau_{\rm max} = \frac{1}{2} \sqrt{\sigma_b^2 + 4\tau^2}
  1. Maximum normal stress theory (or Rankine's theory) states that the maximum normal stress σb(max)\sigma_{\rm b(max)} in the shaft is given by:
σb(max)=12(σb+σb2+4τ2)(17)\small \sigma_{\rm b(max)} = \frac{1}{2} \left(\sigma_{\rm b} + \sqrt{\sigma_b^2 + 4\tau^2} \right)(17)

Let's start with a solid shaft. Rewriting equation (4), we get:

τ=16Tπd3(18)\tag{18} \tau = \frac{16 T}{\pi d^3}

Similarly, rewriting equation (12), we get:

σb=32Mπd3(19)\tag{19} \sigma_b = \frac{32 M}{\pi d^3}

Using (18) and (19) in (16), we get:

 ⁣τmax=12(32Mπd3)2+4(16Tπd3)2=16πd3M2+T2\!\small \begin{align*} \tau_{\rm max} &= \frac{1}{2} \sqrt{\left( \frac{32 M}{\pi d^3}\right)^2 + 4\left( \frac{16 T}{\pi d^3}\right)^2}\\[1em] &= \frac{16 }{\pi d^3} \sqrt{M^2 + T^2}\\[1em] \end{align*}
or: M2+T2=π16×τmaxd3\small \begin{align*} \text{or: } \sqrt{M^2 + T^2} &= \frac{\pi}{16} \times \tau_{\rm max} \cdot d^3 \end{align*}

We call the expression M2+T2\sqrt{M^2 + T^2} the equivalent twisting moment TeT_e in the shaft.

Te=M2+T2=π16×τmaxd3(20)\small \tag{20}\begin{split}T_e &= \sqrt{M^2 + T^2}\\[.5em] &= \frac{\pi}{16} \times \tau_{\rm max} \cdot d^3\end{split}

Let's give a similar consideration to the maximum normal stress theory. Using (18) and (19) in (17), we get:

 ⁣σb(max)=12[32Mπd3+(32Mπd3)2+4(16Tπd3)2]=32πd3(12[M+M2+T2])\!\scriptsize \begin{align*} \sigma_{\rm b(max)}\! &= \frac{1}{2}\!\! \left[\frac{32 M}{\pi d^3}\! +\! \sqrt{\!\left( \frac{32 M}{\pi d^3} \right)^2\! + 4\!\left( \frac{16 T}{\pi d^3} \right)^{\!2}\!} \right]\\[1.5em] &= \frac{32}{\pi d^3} \left( \frac{1}{2}\left[ M + \sqrt{M^2 + T^2} \right] \right) \end{align*}

The expression 12[M+M2+T2]\frac{1}{2}\left[ M + \sqrt{M^2 + T^2} \right] is called the equivalent bending moment MeM_e. Rearranging the above equation:

Me=12[M+M2+T2]=π32×σb(max)d3(21)\small \tag{21} \begin{split}M_e &= \frac{1}{2}\left[ M + \sqrt{M^2 + T^2} \right]\\[1em] &= \frac{\pi}{32} \times \sigma_{\rm b (max)} \cdot d^3 \end{split}

🙋 We will get two diameter values — one from equation (20) for TeT_e and one from equation (21) for MeM_e. We must pick whichever value is larger among the two for shaft design so that the shaft can withstand the combined stresses.

For a hollow shaft, the equivalent twisting moment is given by:

Te=M2+T2=π16×τmaxdo3(1k4)(22)\tag{22}\small \begin{split}T_e &= \sqrt{M^2 + T^2}\\ &= \frac{\pi}{16} \times \tau_{\rm max} \cdot d_o^3 (1-k^4)\end{split}

Similarly, the equivalent bending moment is given by:

Me=12[M+M2+T2]=π32×σb(max)do3(1k4)(23)\small \tag{23} \begin{split}M_e &= \frac{1}{2}\left[ M + \sqrt{M^2 + T^2} \right]\\[1em] &= \frac{\pi}{32} \times \sigma_{\rm b (max)} \cdot d_o^3(1-k^4) \end{split}

Again, we will obtain two outer diameter values from equations (22) and (23). We must pick whichever value is larger for our shaft design calculation.

Calculating shaft size for fluctuating torsion and bending moments

In real-world scenarios, shafts are subjected to fluctuating torque and bending moments, not constant loads. In such cases, we must account for the combined shock and fatigue factors when calculating twisting and bending moments.

The equivalent twisting moment would be:

Te=(KmM)2+(KtT)2(24)\footnotesize\tag{24} T_e = \sqrt{(K_m \cdot M)^2 + (K_t \cdot T)^2}


  • KmK_m — Combined shock and fatigue factor for bending; and
  • KtK_t — Combined shock and fatigue factor for torsion.

Similarly, the equivalent bending moment is given by (25):

Me=12[KmM+(KmM)2+(KtT)2]\footnotesize \begin{split} M_e &= \frac{1}{2}\Big[ K_m \cdot M\\ &\qquad + \sqrt{(K_m \cdot M)^2 + (K_t \cdot T)^2}\Big] \end{split}

We then use this equivalent twisting and bending moment to find the diameter value:

Te={π16×τmaxd3for solid shaftπ16×τmaxdo3(1k4)for hollow shaftMe={π32×σb(max)d3for solid shaftπ32×σb(max)do3(1k4)for hollow shaft\footnotesize T_e = \begin{cases} \frac{\pi}{16} \times \tau_{\rm max} \cdot d^3 &\!\!\!\text{\scriptsize for solid shaft} \\ \frac{\pi}{16} \times \tau_{\rm max} \cdot d_o^3 (1-k^4)&\!\!\!\text{\scriptsize for hollow shaft} \end{cases}\\[2em] M_e = \begin{cases} \frac{\pi}{32} \times \sigma_{\rm b(max)} \cdot d^3 &\!\!\!\!\text{\scriptsize for solid shaft} \\ \frac{\pi}{32} \times \sigma_{\rm b(max)} \cdot d_o^3 (1-k^4)&\!\!\!\!\text{\scriptsize for hollow shaft} \end{cases}

The recommended values for KmK_m and KtK_t are listed in the table below.

Recommended values for rotating shafts.

Load type



Gradually applied or steady load



Suddenly applied load with minor shocks



Suddenly applied load with heavy shocks



Calculating minimum shaft diameter for torsional rigidity

Shafts, like the camshaft of an IC engine, require a maximum amount of twist angle not to be exceeded during operation. In such cases, we design the shaft to meet desired torsional rigidity.

The torsion equation gives us the following:

TJ=GθL(25)\tag{25} \frac{T}{J} = \frac{G \cdot \theta}{L}


  • GGModulus of rigidity of the shaft;

  • θ\theta — Maximum permissible angle of twist in the shaft; and

  • LL — Shaft length.

For a solid circular shaft, using the polar moment of inertia described in (4), we get:

T=GθL×π32×d4(26)\tag{26} T = \frac{G \cdot \theta}{L} \times \frac{\pi}{32} \times d^4

For a hollow circular shaft, using the polar moment of inertia described in (5), we get:

T=GθL×π32×[do4di4] (27)T = \frac{G \cdot \theta}{L} \times \frac{\pi}{32} \times [d_o^4 - d_i^4]\ (27)

Using this shaft size calculator

If our shaft size calculator seems intimidating, don't worry! By design, it can handle all the situations we've described in this article so far, so allow us to walk you through it:

  1. First, select your shaft's design basis. You can choose to design a shaft based on:

    1. Twisting moment only.

    2. Bending moment only.

    3. A combination of twisting and bending moments.

    4. A combination of fluctuating twisting and bending moments.

    5. Desired torsional rigidity.

  2. Based on your selection, enter the torque and/or bending moment values along with allowable stress values.

    • Tip: You can calculate shaft diameter from power instead of torque. To do this, enter the power and shaft speed in rpm in their respective fields.

    • For fluctuating twisting and bending loads, provide the combined shock and fatigue factors for twisting and bending.

  3. The calculator will use the data to calculate the minimum shaft diameter of a solid shaft.

  4. To calculate the outer and inner diameters of a hollow shaft, you must provide the ratio of inner to the outer diameter (k).


What is the shaft size required to transmit 20 kW at 200 rpm?

Assuming the shaft is mild steel, the minimum required shaft diameter is 48.7 mm. To calculate this result, follow these steps:

  1. Calculate the torque acting on the shaft from the power and shaft speed, using T = 60⋅P/(2π⋅n) = (60 × 20 × 103)/(2π⋅200) = 955 N-m.

  2. Assume the allowable shear stress of mild steel τ = 42 MPa.

  3. Substituting the values in the shaft diameter formula for torsion loads, T = π ⋅τ⋅d3/16, we get: 955 = π × 42 × 106 × d3/16.

  4. Solving this equation, we get d = 0.487 m = 48.7 mm.

What is the difference between a shaft and an axle?

A shaft is a rotating machine member transmitting torque and power from one part to another. On the other hand, an axle is a stationary member designed to support rotating bodies like car wheels by transmitting bending moment.

Why is torsional rigidity important when designing camshafts?

A camshaft in an internal combustion engine is used for timing valve opening and closing. If the angle of twist exceeds an acceptable amount of 0.25° per meter, the timing of these valves will be affected. Torsional rigidity is thus an essential factor to consider when designing camshafts.

What is the maximum permissible shear stress for a transmission shaft?

According to the American Society of Mechanical Engineers (ASME) code for transmission shaft design, the maximum permissible shear stress is:

  1. 56 MPa without allowance for key ways.
  2. 42 MPa with allowance for keyways.

Power and torque

Allowable stress

Shaft size for torsion

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