## What are splines and serrations?

shaft splines and serrations are ridges, or teeth type keys that are an integral part of the shaft that mesh with grooves in a mating hub to transfer torque and rotational motion. For example, a bevel gear mounted on a shaft might use a male shaft spline that matches the female spline on the gear as shown in Figure 1.

Although a splined shaft looks like having a series of shaft keyways with keys pushed in, splines are considerably stronger than the keyed joint as the keyways weaken the shaft and reduce its torque carrying capacity.

## Application of splines and serrations

Although they look like gears, Splines are only used to transmit torque and rotation on the same axis. They are used mainly for the following reasons.

- Mechanical transmission element such as gears and pulleys might need removing from the shaft due to design for manufacture and assembly (DFMA) ie during assembly or to aid manufacturing.
- Relative axial movement of the mechanical transmission element is required for functional purposes such as speed reducers and clutches.
- High torque transfer is required.

Good spline joint provides very high secure torque transmission, little clearance, minimum backlash, good centring between the coupled components, low noise, low wear and small or no axial forces.

Surface wear, fretting corrosion, tooth breakage and fatigue failure are the most common failure modes associated with spline joints.

## Types of Splines and Serrations

The term “spline” provides an umbrella term for all profiles and the splines can be divided into the following three groups based on their flank form.

- Parallel-sided or straight-sided spline
- Involute spline
- Serration

Splines and serrations can also be grouped as fixed spline or flexible spline depending on their relative axial movement. Fixed spline as the name suggests is a joint which does not move axially such as gears, pullers, turbine wheels etc.

Flexible splines slide axially, mainly used between shafts couplings and do not carry much torque as fixed spline joint.

### Parallel-sided or Straight-sided spline

These have straight and parallel tooth flanks a shown in the figure below and as per various standards number of teeth can vary from 4 to 12. They can transmit higher torque compared to involute splines and serrations because of their large tooth thickness from minor to the major diameter of the profile. But might fail due to fatigue due to stress concentration in the root of the flanks.

Naturally, it lacks centring ability because of the straight flanks, therefore forces it to rely on the major and minor diameter fits to be able to manage the centring. Because of the straight-sided face, there will be a line of contact and surface contact will only exist after some wear.

### Involute

Involute splines are very common and very similar to internal and external involute gear tooth. They are comparably stronger than the parallel spline because of the lower stress concentration factor and have better surface quality. Involute splines can be produced by gear manufacturing techniques and have the ability to self-centre under load.

Involute splines are made with pressure angles 30^{o}, 37.5 and 45^{o} and can include between 60 and 100 splines as per the American National Standard. Involute splines can be either Side fit or Diameter fit.

### Serrations

Serrations also have straight flanks, but they are angled as shown in the figure below. The biggest advantage of the serrations is that the angles flanks centre the shafts and the hub resulting in self-centring splines. Flank angles are generally between 50^{o} and 90^{o}.

The main disadvantages of serrations are due to comparably small teeth it can be only used for low torque applications. These are only used for the non-axial moving application. Like straight-sided splines, there will be line contact and wear.

## Spline strength calculation

During the design of shaft splines and serrations, the following stresses have to be considered to evaluate the suitability of the spline joint strength.

- Spline shaft shear stress
- Spline teeth shear stress
- Spline teeth compressive stress

Generally, the shaft diameter is dictated by the overall design such as bearing arrangements, seals, elements etc. In that instance, the spline strength calculations can be used in the following two ways

- Stress calculation can be used either to find the safety factor by calculating the stress involved and comparing it with the allowable stresses as per failure modes.
- Using the factor of safety, the spline connection can be defined using spline length, spline type, number of splines etc.

### Spline shaft shear stress

Solid shaft stresses | Hollow shaft stresses |
---|---|

\( S_s = \frac{16T}{\pi{D_{re}}^{3}} \) | \( S_s = \frac{16T{D_{re}}}{\pi ({D_{re}}^4-D_h^4)} \) |

Where | |

\(S_s\) | Shear stress |

\({D_{re}}\) | Diameter of the spline |

\(T\) | Torque |

\({D_{h}}\) | Bore diameter of hollow shaft |

Calculated stress using the above equations must not exceed the allowable stress (\(S^a\)) of the spline material and can be shown as follows

\(S^a_s \geq S_s \frac{{K_{a}}}{{L_{f}}}\)Usually, the factor of safety is calculated using the allowable stress for various material using the following equations

Allowable shaft stress | |
---|---|

\(S^a_s = {N_{sf}}S_s \frac{{K_{a}}}{{L_{f}}}\) | \(S^a_s \geq S_s \frac{{K_{a}}}{{L_{f}}}\) |

Where | |

\(S_s\) | Shear stress |

\(S^a_{s}\) | Allowable shear stress |

\(T\) | Torque |

\({L_{f}}\) | Life factor |

\({N_{sf}}\) | Safety factor |

\({K_{a}}\) | Application factor |

### Spline teeth shear stress

Shear stress in spline teeth | |
---|---|

\(S_s = \frac{4T{K_{m}}}{DN{F_{e}}{t_{e}}}\) | |

\(S_s\) | Induced shear stress in spines |

\(D\) | Pitch diameter |

\(T\) | Torque |

\({K_{m}}\) | Load distribution factor |

\({F_{e}}\) | Effective face width |

\({t_{e}}\) | Chordal thickness at pitch line ( approximately equal to D/2N) |

\(N\) | Number of spline teeth |

### Spline teeth compressive stress

Compressive stress on spline teeth | |
---|---|

\( S_c = \frac{2T{K_{m}}}{DN{F_{e}h}} \) | |

\(S_c\) | Compressive stress |

\({K_{m}}\) | Load distribution factor |

\(T\) | Torque |

\({F_{e}}\) | Effective face width |

\(h\) | Radial height of the tooth in contact |

Again similar to shear stresses, calculated compressive stresses should be compared with allowable compressive stress and must not exceed them to avoid failure.

\(S^a_s \geq S_s \frac{{K_{a}}}{{L_{f}}}\) – Flexible splines \(S^a_s \geq S_s \frac{{K_{a}}}{{L_{f}}}\) – Fixed splinesAllowable shaft stress | |
---|---|

Flexible splines | Fixed Splines |

\(S^a_c = {N_{sf}}S_c \frac{{K_{a}}}{{L_{w}}}\) | \(S^a_c = {N_{sf}}S_c \frac{{K_{a}}}{{9L_{f}}}\) |

Where | |

\(S_s\) | Shear stress |

\({S^a_{s}}\) | Allowable shear stress |

\(T\) | Torque |

\({L_{f}}\) | Life factor |

\({N_{sf}}\) | Safety factor |

\({K_{a}}\) | Application factor |

## Spline stress factors

### Allowable stress

The relationship between allowable stress and specified minimum yield strength as per AISC code.

Allowable stresses vs Yield strength | |
---|---|

Allowable tensile stress | \({0.45}S_{y}\leq S^a_{t}\leq {0.6}S_{y}\) |

Allowable Shear stress (\({S^a_{s}}\)) | \(S^a_{s}= 0.4S_{y }\) |

Allowable compressive/bearing stress (\({S^a_{c}}\)) | \(0.45S_{y}\leq S^a_{c} \leq 0.6S_{y}\) |

Allowable bending stress (\({S^a{b}}\)) | \(0.6S_{y} \leq S^a_{b} \leq 0.75S_{y} \) |

Where | |

\({S_{y}}\) | Material yield strength |

### Load distribution factor for splines Km

The load is equally distributed if the transferring load is purely radial torsion and the torsional radial load is in the middle of the spline length. But if for example, a bevel gear is used this will put some unwanted axial loads into the spline.

Misalignment of spline couplings has been recognized as harmful to splines because it causes significant load concentration on spline teeth, and accelerates the wear and fretting fatigue of splines.

Load distribution factor for splines Km | ||||
---|---|---|---|---|

Effective face width (Fe) | ||||

Misalignment | ½-in. (12.7 mm) | 1-in. (25.4 mm) | 2-in. (50.8 mm) | 4-in. (101.6) |

0.001 in. / in. (mm/mm) | 1 | 1 | 1 | 1 ½ |

0.002 in. / in. (mm/mm) | 1 | 1 | 1 ½ | 2 |

0.004 in. / in. (mm/mm) | 1 | 1 ½ | 2 | 2 ½ |

0.008 in. / in. (mm/mm) | 1 ½ | 2 | 2 ½ | 3 |

The following two papers discuss the load distribution factor and how it can affect the life of the spline joint.

- https://www.geartechnology.com/issues/0514x/spline-joints.pdf
- https://www.powertransmission.com/issues/0214/spline-couplings.pdf

### Fatigue life factor for splines- L_{f}

Number of torque cycles | Fatugue Life Factor, Lf | |
---|---|---|

Unidirectional | Fully - reversed | |

1,000 | 1.8 | 1.8 |

10,000 | 1.0 | 1.0 |

100,000 | 0.5 | 0.4 |

1,000,000 | 0.4 | 0.3 |

10,000,000 | 0.3 | 0.2 |

### Spline application factor – K_{a}

If there are any axial or radial shock loading on the element that is been connected, then care should be taken to support the external axial and radial shock loads to increase the joint life. This should also be considered during the calculations using the **spline application factor**.

The application factor compensates for any uncertainties in loads and impacts, where if everything is smooth and uniform then Ka is equal to 1.

Input source category (Driving input or machine) | Type of Load | |||
---|---|---|---|---|

Uniform | Light shock | Intermittent Shock | heavy shock | |

Generators, Fans | Oscillating pumps | Actuators | Presses, Shears | |

Uniform (Turbine, Motor) | 1 | 1.2 | 1.5 | 1.8 |

light shock, (Hydraulic Motor) | 1.2 | 1.3 | 1.8 | 2.1 |

Medium shock, (Internal combustion engine | 2 | 2.2 | 2.4 | 2.8 |

Table 1 Spline application Factor (Ka)

### Wear life factor for splines L_{w}

Life factor for splines under wear conditions are based on the number of revolutions of the spline joint, not reversible cycles. Wear life factor only applies to flexible or sliding spline compressive stress calculations as each time the spline slide back and forth it wears the teeth.

No of revolutions of the spline | Wear life factor for splines (Lw ) |
---|---|

10,000 | 4 |

100,000 | 2.8 |

1,000,000 | 2 |

10,000,000 | 1.4 |

100,000,000 | 1 |

1,000,000,000 | 0.7 |

10,000,000,000 | 0.5 |

**#Productdesigntip **Fixed spline can carry 9 times more compressive stresses than flexible spline

## Standards

- Society of Automotive Engineering standard parallel side splines SAE J 499-2014
- The American standard for involute and straight-sided spline profile ANSI B92.1
- IS 2610 – power transmission-straight sided splines for machine tools dimensions
- IS 3665 – Dimensions for involute sided splines
- IS 2327 – Straight-sided splines for cylindrical shafts
- BS 2059 Straight-sided splines and serrations
- DIN 5463 – spline shaft connections with straight flanks; medium series
- DIN 5480 – Involute splines based on reference diameters
- Some other standards – DIN 5480, DIN 5481, DIN 5482, ISO 4156, E22-141, E22-145, ANSI and SAE standards

## References and recommended reading

- Dudley, D. W. (n.d.). When splines need stress control.
- Oberg, E., Jones, F. D., Horton, H. L., & Ryffel, H. H. (2016).
*Machinery’s handbook*. - Lingaiah, K. (2007).
*Machine design databook*. (Lingaiah, K.: Machine design databook.) Norwich, NY: Knovel. - Bhandari, V. B. (2017).
*Design of machine elements*. New Delhi: McGraw-Hill Education (India). - British Standards Institution. 2059 (1953).
*Straight-sided splines and serrations*. London: B.S.I.