Hi to all,

I would like to be able to write equations to model my tracked vehicle which has a mass**m=200Kg**.

My skid-steering vehicle uses one track per side with a rubber belt made in 100% natural rubber, please refer to the next photo to get a more detailed idea.

Since I mounted an IMU in its geometric center, I can read both the angular velocites and the accelerations along the three axis plus the heading, the pitch and yaw angles in degrees.

I would like to be able to write a model for the vehicle in order to simulate and study its outputs depending on specific inputs.

Each track has a length**L=1000 mm**, a width **W=330 mm** and a lug height, **H = 32 mm**.

The vehicle is**Lv= 1000 mm** long and **Wv=900 mm** width.

There are no suspensions, but I consider the rubber track as the combination of a spring, coefficient**K**, and a damper, coefficient **b**. The rubber compression is about **Dx =1,5 mm**

By supposing a sinusoidal input below the track generated by the terrain profile, u(t) = Asin(wt), I was able to write the equation for the Z axis:

Now, I would like to consider the lateral**force Ft** which acts on the robot during a turning motion.

Let's consider the vehicle during a steering maneuver on the left: while the YAW angle changes to reach the target heading, the tracks are subjected to the later force as result of the terrain resistance.

Is there any way to write an equation to define the relation between the heading of the vehicle and the force Ft?

I do not know if you should consider the force Ft as a sine wave or a costant since it changes on if the vehicle sinks into the terrain.

I would like to write something like: Z(s) = G(s)X(s).

Can you suggest me how to write this relation, please?

track-robot.jpg

I would like to be able to write equations to model my tracked vehicle which has a mass

My skid-steering vehicle uses one track per side with a rubber belt made in 100% natural rubber, please refer to the next photo to get a more detailed idea.

Since I mounted an IMU in its geometric center, I can read both the angular velocites and the accelerations along the three axis plus the heading, the pitch and yaw angles in degrees.

I would like to be able to write a model for the vehicle in order to simulate and study its outputs depending on specific inputs.

Each track has a length

The vehicle is

There are no suspensions, but I consider the rubber track as the combination of a spring, coefficient

By supposing a sinusoidal input below the track generated by the terrain profile, u(t) = Asin(wt), I was able to write the equation for the Z axis:

```
X(s)/Y(S)=(bs+k)/((m/2)*s^2 + bs+k) for the right track
X(s)/Y(S)=(bs+k)/((m/2)*s^2 + bs+k) for the left track
```

Now, I would like to consider the lateral

Let's consider the vehicle during a steering maneuver on the left: while the YAW angle changes to reach the target heading, the tracks are subjected to the later force as result of the terrain resistance.

Is there any way to write an equation to define the relation between the heading of the vehicle and the force Ft?

I do not know if you should consider the force Ft as a sine wave or a costant since it changes on if the vehicle sinks into the terrain.

I would like to write something like: Z(s) = G(s)X(s).

Can you suggest me how to write this relation, please?

track-robot.jpg

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You will get a lot more out of doing a discrete-time solution of difference equations because you'll be able to easily incorporate new coefficients and any nonlinearities.

And, then you can work with the forcing functions (like the terrain profile) without assuming sinusoids necessarily.

For example, the drag related to rotation is an even function of rotation rate and may well be related to the square or cube of the rotation rate.

Of course, you can simplify where it makes sense.

I have requested a copy of my report on such a model and await getting it. But, it may take months!

In the mean time, Google for six-degree-of-freedom or 6DOF.

While old (as is mine of 1973), here is an example with Fortran code included:

http://www.dtic.mil/dtic/tr/fulltext/u2/614699.pdf

And, I'd look to see what Matlab has to offer.

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Start your 7-day free trialDuring the next days, I will try to implement a solution based on your suggestions and I will let you know! :)

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This looks to me like a very common six-degree of freedom set of equations - likely will be second-order.

The 6 degrees of freedom are: X, Y,Z,theta, phi, zeta where the last 3 are roll, pitch and yaw.

And, you would likely be considering X, X', X'' position, velocity and acceleration for each.

Surely you'll be doing a simulation in discrete time and not seeking some analytical solution.

Yet, you're showing a steady-state equation which isn't likely so flexible.

This critical decision will allow strange terrain profiles vs. steady-state or uniformly-varying profiles (like a sinusoidal surface).

You can write the simplest equations first that assume no cross-coupling. Not much fidelity in this but to imagine the others.

f=ma

a=f/m

X''=fx/m; X'=X'0 + at; X=X0+x't where "t" is time and you'd be using deltat for each time step in the simulation.

etc.

This will incorporate the external forces and compute the position and velocity in each degree of freedom.

The tricky part is determining the coefficients of second-order damping factors such as:

How much resistance or drag is there resulting from roll acceleration or roll velocity? etc.

Then you can have a more realistic model if you add cross-coupling terms:

e.g. forward velocity is an even function of yaw rate - the faster the vehicle turns, the more negative effect on forward velocity. It's "even" because it doesn't matter the direction of the yaw on the forward velocity.

Other terms will be "odd". Rotational drag depends on the direction of rotation - so it's and "odd" function of rotational velocity.

etc.

In terms of starting out, I'd get a set of fully-coupled 6DOF equations and then "trim" the cross-coupling coefficients according to what you think is unimportant or insignificant. For example, the rate of change of acceleration may not be important but the acceleration certainly is - so you limit the terms in the equations that way right off. The coupling of roll rate to

As far as the vehicle sinking, I've done this for water-skimming vehicles like yours using a simple f=ma model where "f" is the weight of the vehicle, "m" is the mass of the displaced liquid and "a" is gravity. You can calculate the vertical velocity due to gravity and fluid displacement and the vertical position due to displacement in a time step.

At each time step, you calculate the displacement until, for steady forward velocity, there is a constant depth.

It's the same as calculating the trajectory of a skipping stone without the skipping.

The weight of the object is the force. The density of the liquid provides the "drag" force. "m" is the mass of the liquid under the vehicle footprint.

I have a simple model in Excel for this one if it's of any interest.

I must admit that it's been a long time since I've done the full 6DOF models so I'd need to refresh my memory.