While the Simscape™ Driveline™ library contains a Planetary Gear, you can create your own custom
planetary gear using the **Planetary Subcomponents** sublibrary.
The `sdl_gear_planetary_custom`

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 Damper blocks.

**Custom Planetary Gear System and Subsystem**

The blocks of the Simscape Driveline 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*.

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 transmitted power is greater than the power threshold*p*_{th}. Below this value, a hyperbolic tangent function smooths the efficiency factor, lowering the efficiency losses to zero when no power is transmitted.For gear sets with a carrier,

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

For gears with different efficiencies for the forward and reverse power flow:

*ForwardLoss*= (1 –*η*_{FB}),*η*_{FB}is the torque transfer efficiency from the follower shaft to the base shaft.*BackwardLoss*= (1/*η*_{BF}– 1), where*η*_{BF}is the torque transfer efficiency from the base shaft to the follower shaft.

The frictional torque is calculated as:

*T*_{f} = *T* /
2((*ForwardLoss* + *BackwardLoss*)tanh(4*p* /* p*_{th})
+ *ForwardLoss* – *BackwardLoss*)

where:

T is the transferred torque.

*p*is the transferred power.*p*_{th}is the power threshold at the base shaft above which full efficiency losses are in effect.

For certain gear models, such as the Simple
Gear, efficiency is assumed equal for both the forward and
reverse power flow, *η*_{BF} = *η*_{FB}.

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_transmission_2spd`

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_transmission_2spd`

model and simulate to check the ideal gear behavior.Open the Gear High and the Gear Low 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 Gear Low block, enter 0.7; and for the Gear High block, 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.

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