GAS Type

This option gives an adiabatic pressure volume relation. With

γ

= 1 an isothermal condition can also be applied.

It is possible to define an incompressible sub-volume to model a volume partially filled with a liquid.

The general equation is:(1)

P = {(V - V_{i})}^{γ} = P_{0} {(V_{0} - V_{i})}^{γ}

With

$V_{0}$: Initial volume
$V_{i}$: Incompressible volume $V_{i} < V_{0}$

A viscosity $μ$ can be used to reduce numerical oscillations.

μ

= 1 a critical damping (shell mass and volume stiffness) is used. The viscous pressure

q

is:(2)

q = μ \frac{1}{A} \sqrt{\frac{γ P m_{f a b r i c}}{V}} \frac{d V}{d t}

Where,

$m_{f a b r i c} = A ρ t$: Mass of fabric
$A$: Its surface

The applied pressure is $P - P_{e x t} + q$ .

The specific inputs for this type are:

$γ$
$μ$
$P_{e x t}$
$P_{0}$
$V_{i}$

If the deflation is considered (isenthalpic outflow computation), the initial mass of gas, must also be input.

This monitored volume is typically used to model tire pressure or simple fuel tank. For tire model $V_{i}$ is zero and for fuel tank $V_{i}$ is the fuel volume.

Thermodynamical Equations

The basic energy equation of the monitored volume can be written as:(3)

d E_{M o n i t o r e d V o l u m e} = - P d (V - V_{i}) - d H_{o u t}

Where,

$E$: Internal energy
$P$: Pressure
$V$: Monitored volume
$V_{i}$: Incompressible volume
$H_{o u t}$: Outgoing enthalpy

When the adiabatic condition is applied and assuming a perfect gas:(4)

P = \frac{(γ - 1) E}{V - V_{i}}

Where, $γ$ is the gas constant. For air, $γ$ = 1.4.

The two equations above allow the current volume to be determined. The energy and pressure can then be found.

External Work Variation

At the current time step,

t

, assume:

$P (t - d t)$
$E (t - d t)$
$\tilde{V} = V - V_{i}$

δ

W (t), E (t), P (t)

will be obtained as: (5)

δ W = \frac{P (t) + P (t - d t)}{2} (\tilde{V} (t) - \tilde{V} (t - d t))

be the variation of external work and from the adiabatic condition:(6)

P = \frac{(γ - 1) E}{\tilde{V}}

you have:(7)

δ W = \frac{(γ - 1) Δ \tilde{V}}{2} [\frac{E (t)}{\tilde{V} (t)} + \frac{E (t - d t)}{\tilde{V} (t - d t)}]

Let:

$E = E (t - d t)$

$\tilde{V} = (\tilde{V} (t) - \tilde{V} (t - d t)) / 2$

Δ E = E (t) - E (t - d t)

(8)

δ W = \frac{(γ - 1)}{2} \frac{Δ \tilde{V}}{\tilde{V}} [\frac{1 + \frac{Δ E}{E}}{1 + \frac{Δ \tilde{V}}{2 \tilde{V}}} + \frac{1}{1 - \frac{Δ \tilde{V}}{2 \tilde{V}}}]

Hence, the external work is given by:(9)

δ W \approx (γ - 1) E \frac{Δ \tilde{V}}{\tilde{V}} [1 + \frac{Δ E}{2 E}]

Computing the energy from basic principles:(10)

Δ E = - (γ - 1) E \frac{Δ \tilde{V}}{\tilde{V}} [1 + \frac{Δ E}{2 E}] - Δ H_{o u t}

$Δ H_{o u t}$ can be estimated from, $u (t - d t)$ , the velocity at vent hole; this estimation will be described hereafter.

The variation of internal energy

Δ E

can be given by:(11)

Δ E = [- (γ - 1) E \frac{Δ \tilde{V}}{\tilde{V}} - Δ H_{o u t}] [1 - (γ - 1) E \frac{Δ \tilde{V}}{2 \tilde{V}}]

Therefore:(12)

E (t) = E (t - d t) + Δ E

(13)

P (t) = (γ - 1) \frac{E (t)}{\tilde{V} (t)}

This pressure is then applied to the monitored volume to get:

New accelerations
New velocities
New geometry
New volume
Ready for next step evaluation

Venting

Venting, or the expulsion of gas from the volume, is assumed to be isenthalpic.

The flow is also assumed to be unshocked, coming from a large reservoir and through a small orifice with effective surface area, $A$ .

Conservation of enthalpy leads to velocity,

u

, at the vent hole. The Bernouilli equation is then written as: (14)

(monitored volume) \frac{γ}{γ - 1} \frac{P}{ρ} = \frac{γ}{γ - 1} \frac{P_{e x t}}{ρ_{v e n t}} + \frac{u^{2}}{2} (vent hole)

Applying the adiabatic conditions:(15)

\frac{P}{ρ^{γ}} = \frac{P_{e x t}}{ρ_{v e n t}^{γ}}

Therefore, the exit velocity is given by:(16)

u^{2} = \frac{2 γ}{γ - 1} \frac{P}{ρ} (1 - {(\frac{P_{e x t}}{P})}^{\frac{γ - 1}{γ}})

The mass flow rate is given by:(17)

{\dot{m}}_{o u t} = ρ_{v e n t} A_{v e n t} u = ρ {(\frac{P_{e x t}}{P})}^{1 / γ} A_{v e n t} u

The energy flow rate is given by:(18)

{\dot{E}}_{o u t} = \dot{m} \frac{E}{ρ \tilde{V}} = {(\frac{P_{e x t}}{P})}^{1 / γ} A_{v e n t} u \frac{E}{\tilde{V}}

The vent hole area or scale factor area,

A_{v e n t}

, can be defined in these ways:

a constant area taking into account a discharge coefficient
a variable area equal to the area of a specified surface, multiplied by a discharge coefficient
a variable area equal to the area of the deleted elements within a specified surface, multiplied by a discharge coefficient

Supersonic Outlet Flow

Vent pressure

P_{v e n t}

is equal to external pressure

P_{e x t}

for unshocked flow. For shocked flow,

P_{v e n t}

is equal to critical pressure

P_{c r i t}

and

U

is bounded to critical sound speed:(19)

u^{2} < \frac{2}{γ + 1} c^{2} = \frac{2}{γ + 1} \frac{P}{ρ}

And,(20)

P_{c r i t} = P {(\frac{2}{γ + 1})}^{\frac{γ}{γ - 1}}

$P_{v e n t} = \max (P_{c r i t})$ , $P_{e x t}$ )

Example: GAS Type

Some applications in Radioss:

A tire model:
The inputs are:
- $γ$ = 1.4
- $μ$
- $P_{e x t}$ = 10⁵ Pa
- $P_{i n i}$ = initial tire pressure
  Then, the pressure in the tire is $P_{t i r e} = P_{i n i} - P_{e x t}$
- $V_{i n c} = 0$
A fuel tank model if the sloshing effect is neglected
Only if the sloshing effect is neglected, pressure in a partial filled fuel tank can be modeled with a type GAS monitored volume. Use the following input:
- $γ$ = 1.4
- $μ$
- $P_{e x t}$ = 10⁵ Pa
- $P_{i n i}$ = 10⁵ Pa
- $V_{i n c}$ = volume of fuel