While the SimDriveline™ library contains a Planetary Gear, you can create your own custom
planetary gear using the **Planetary Subcomponents** sublibrary.
The sdl_custom_planetary_gearsdl_custom_planetary_gear example
model combines three Sun-Planet Bevel subgears
into a masked subsystem to model a coupled planetary gear train. The
model uses an Ideal Angular Velocity Source to
place a fixed velocity demand on the gearbox input, while damping
the system on both the input and output driveshafts with Rotational Dampers.

**Custom Planetary Gear System and Subsystem**

The blocks of the SimDriveline Gears Library contain
optional built-in models of frictional losses, allowing you to represent
nonideal gear couplings. In a nonideal gear pair (1,2), the angular
velocity, gear radii, gear teeth constraints, and gear ratio *g*_{12} = *r*_{2}/*r*_{1} = *ω*_{1}/*ω*_{2} are
unchanged. The transferred torque and power are reduced by:

Coulomb friction between imperfectly meshing teeth surfaces on gears 1 and 2, parameterized by an efficiency

*η*, 0 <*η*≤ 1. This efficiency depends on the torque load on the teeth. But it is often approximated as constant.Viscous coupling of driveshafts with bearings, parameterized by viscous friction coefficients

*μ*

*τ*_{loss} = *τ*_{Coul}·tanh(4*ω*_{2}/*ω*_{th})
,

*not* including the effect of viscosity.
When the angular velocity changes sign, the hyperbolic tangent regularizes
the sign change in the Coulomb friction torque without introducing
a discontinuity in the torque that could lead to inefficient simulation.
The viscous friction terms act to reduce the torques *τ*_{1} and *τ*_{2} and
are taken into account before implementing the *τ*_{loss} model.

Power Flow | Power Loss Condition | Coulomb Friction Torque τ_{Coul} | Torque Loss |
---|---|---|---|

Forward | ω_{1}τ_{1} ≥ ω_{2}τ_{2} | g_{12}·|τ_{1}|·(1
– η) | τ_{2} = g_{12}τ_{1} – τ_{loss} |

Reverse | ω_{1}τ_{1} < ω_{2}τ_{2} | |τ_{2}|·(1
– η)/g_{12} | τ_{1} = τ_{2}/g_{12} – τ_{loss} |

In the simplest nonideal gear loss model, the efficiency *η*_{12} of
meshing in gear pair (1,2) is constant, independent of load (torque
or power transferred).

The friction loss represented by

*η*_{12}is effectively applied in full only if the absolute value of the output gear angular velocity is greater than a velocity tolerance*ω*_{th}.If the absolute velocity is less than

*ω*_{th}, the actual efficiency is automatically regularized to 1 at zero velocity.For gear sets with a carrier,

*η*_{12}represents the ordinary efficiency, defined when the carrier is not moving.

Making *η* dependent on the load is a
way to make the loss model more accurate. For an example of load-dependent
efficiency, see the Simple Gear block
reference page.

Making *η* dependent on the geometry
of gear meshing is another way to make the loss model more accurate.
For an example of geometry-dependent efficiency, see the Leadscrew block reference page.

On a driveshaft mounted to a gear wheel by lubricated, nonideal
bearings, the viscous friction experienced by the axis is controlled
by the viscous friction coefficient *μ*. The
viscous friction torque on a driveshaft "a" is –*μ*_{a}·*ω*_{a},
where *ω*_{a} is the angular
velocity of the driveshaft with respect to its mounting or carrier
(if a carrier is present).

Here, you revisit the sdl_simple_transmission model in Model a Two-Speed Transmission with Braking. You reconfigure the Simple Gears to model power loss due to nonideal meshing. The effect of viscous bearing losses is ignored.

Open the sdl_simple_transmissionsdl_simple_transmission model and simulate to check the ideal gear behavior.

Open the Simple Gear 5:1 and Simple Gear 2:1 blocks. Under

**Meshing Losses**, in the**Friction model**drop-down list, choose`Constant efficiency`

for both. Enter efficiencies less than 1, but greater than 0. For example, for the 5:1 gear, enter 0.7; and for the 2:1 gear, enter 0.95.Leave the other settings as they are, including zero viscosity. Close the blocks.

Restart the model. The driveline runs at a lower efficiency and slightly smaller angular velocities, because of the power losses. If you enter different efficiency factors for the two gears, the effect of the loss is different if you switch between gears.

Experiment with load-dependent efficiency. In the **Friction
model** drop-down menu, choose ```
Load-dependent
efficiency
```

instead. In that case, you need more efficiency
model details to specify.

Was this topic helpful?