# Pipe (G)

Rigid conduit for gas flow

**Libraries:**

Simscape /
Foundation Library /
Gas /
Elements

## Description

The Pipe (G) block models pipe flow dynamics in a gas network. The block accounts for viscous friction losses and convective heat transfer with the pipe wall. The pipe contains a constant volume of gas. The pressure and temperature evolve based on the compressibility and thermal capacity of this gas volume. Choking occurs when the outlet reaches the sonic condition.

**Caution**

Gas flow through this block can choke. If a Mass Flow Rate Source (G) block or a Controlled Mass Flow Rate Source (G) block connected to the Pipe (G) block specifies a greater mass flow rate than the possible choked mass flow rate, you get a simulation error. For more information, see Choked Flow.

### Mass Balance

Mass conservation relates the mass flow rates to the dynamics of the pressure and temperature of the internal node representing the gas volume:

$$\frac{\partial M}{\partial p}\cdot \frac{d{p}_{I}}{dt}+\frac{\partial M}{\partial T}\cdot \frac{d{T}_{I}}{dt}={\dot{m}}_{A}+{\dot{m}}_{B}$$

where:

$$\frac{\partial M}{\partial p}$$ is the partial derivative of the mass of the gas volume with respect to pressure at constant temperature and volume.

$$\frac{\partial M}{\partial T}$$ is the partial derivative of the mass of the gas volume with respect to temperature at constant pressure and volume.

*p*_{I}is the pressure of the gas volume.*T*_{I}is the temperature of the gas volume.*t*is time.$$\dot{m}$$

_{A}and $$\dot{m}$$_{B}are mass flow rates at ports A and B, respectively. Flow rate associated with a port is positive when it flows into the block.

### Energy Balance

Energy conservation relates the energy and heat flow rates to the dynamics of the pressure and temperature of the internal node representing the gas volume:

$$\frac{\partial U}{\partial p}\cdot \frac{d{p}_{I}}{dt}+\frac{\partial U}{\partial T}\cdot \frac{d{T}_{I}}{dt}={\Phi}_{A}+{\Phi}_{B}+{Q}_{H}$$

where:

$$\frac{\partial U}{\partial p}$$ is the partial derivative of the internal energy of the gas volume with respect to pressure at constant temperature and volume.

$$\frac{\partial U}{\partial T}$$ is the partial derivative of the internal energy of the gas volume with respect to temperature at constant pressure and volume.

*Φ*_{A}and*Φ*_{B}are energy flow rates at ports**A**and**B**, respectively.*Q*_{H}is heat flow rate at port**H**.

### Partial Derivatives for Perfect and Semiperfect Gas Models

The partial derivatives of the mass *M* and the internal energy
*U* of the gas volume, with respect to pressure and temperature at
constant volume, depend on the gas property model. For perfect and semiperfect gas models,
the equations are:

$$\begin{array}{l}\frac{\partial M}{\partial p}=V\frac{{\rho}_{I}}{{p}_{I}}\\ \frac{\partial M}{\partial T}=-V\frac{{\rho}_{I}}{{T}_{I}}\\ \frac{\partial U}{\partial p}=V\left(\frac{{h}_{I}}{ZR{T}_{I}}-1\right)\\ \frac{\partial U}{\partial T}=V{\rho}_{I}\left({c}_{pI}-\frac{{h}_{I}}{{T}_{I}}\right)\end{array}$$

where:

*ρ*_{I}is the density of the gas volume.*V*is the volume of gas.*h*_{I}is the specific enthalpy of the gas volume.*Z*is the compressibility factor.*R*is the specific gas constant.*c*_{pI}is the specific heat at constant pressure of the gas volume.

### Partial Derivatives for Real Gas Model

For real gas model, the partial derivatives of the mass *M* and the internal
energy *U* of the gas volume, with respect to pressure and temperature at
constant volume, are:

$$\begin{array}{l}\frac{\partial M}{\partial p}=V\frac{{\rho}_{I}}{{\beta}_{I}}\\ \frac{\partial M}{\partial T}=-V{\rho}_{I}{\alpha}_{I}\\ \frac{\partial U}{\partial p}=V\left(\frac{{\rho}_{I}{h}_{I}}{{\beta}_{I}}-{T}_{I}{\alpha}_{I}\right)\\ \frac{\partial U}{\partial T}=V{\rho}_{I}\left({c}_{pI}-{h}_{I}{\alpha}_{I}\right)\end{array}$$

where:

*β*is the isothermal bulk modulus of the gas volume.*α*is the isobaric thermal expansion coefficient of the gas volume.

### Momentum Balance

The momentum balance for each half of the pipe models the pressure drop due to momentum flux and viscous friction:

$$\begin{array}{l}{p}_{A}-{p}_{I}={\left(\frac{{\dot{m}}_{A}}{S}\right)}^{2}\cdot \left(\frac{1}{{\rho}_{I}}-\frac{1}{{\rho}_{A}}\right)+\Delta {p}_{AI}\\ {p}_{B}-{p}_{I}={\left(\frac{{\dot{m}}_{B}}{S}\right)}^{2}\cdot \left(\frac{1}{{\rho}_{I}}-\frac{1}{{\rho}_{B}}\right)+\Delta {p}_{BI}\end{array}$$

where:

*p*is the gas pressure at port**A**, port**B**, or internal node I, as indicated by the subscript.*ρ*is the density at port**A**, port**B**, or internal node I, as indicated by the subscript.*S*is the cross-sectional area of the pipe.*Δp*_{AI}and*Δp*_{BI}are pressure losses due to viscous friction.

The heat exchanged with the pipe wall through port **H** is added to the
energy of gas volume represented by the internal node via the energy conservation
equation (see Energy Balance). Therefore, the momentum
balances for each half of the pipe, between port **A** and the
internal node and between port **B** and the internal node, are
assumed to be adiabatic processes. The adiabatic relations are:

$$\begin{array}{l}{h}_{A}+\frac{1}{2}{\left(\frac{{\dot{m}}_{A}}{{\rho}_{A}S}\right)}^{2}={h}_{I}+\frac{1}{2}{\left(\frac{{\dot{m}}_{A}}{{\rho}_{I}S}\right)}^{2}\\ {h}_{B}+\frac{1}{2}{\left(\frac{{\dot{m}}_{B}}{{\rho}_{B}S}\right)}^{2}={h}_{I}+\frac{1}{2}{\left(\frac{{\dot{m}}_{B}}{{\rho}_{I}S}\right)}^{2}\end{array}$$

where *h* is the specific enthalpy at port **A**, port
**B**, or internal node I, as indicated by the
subscript.

The pressure losses due to viscous friction, *Δp*_{AI} and *Δp*_{BI},
depend on the flow regime. The Reynolds numbers for each half of the
pipe are defined as:

$$\begin{array}{l}{\mathrm{Re}}_{A}=\frac{\left|{\dot{m}}_{A}\right|\cdot {D}_{h}}{S\cdot {\mu}_{I}}\\ {\mathrm{Re}}_{B}=\frac{\left|{\dot{m}}_{B}\right|\cdot {D}_{h}}{S\cdot {\mu}_{I}}\end{array}$$

where:

*D*_{h}is the hydraulic diameter of the pipe.*μ*_{I}is the dynamic viscosity at internal node.

If the Reynolds number is less than the **Laminar flow
upper Reynolds number limit** parameter value, then the flow
is in the laminar flow regime. If the Reynolds number is greater than
the **Turbulent flow lower Reynolds number limit** parameter
value, then the flow is in the turbulent flow regime.

In the laminar flow regime, the pressure losses due to viscous friction are:

$$\begin{array}{l}\Delta {p}_{A{I}_{lam}}={f}_{shape}\frac{{\dot{m}}_{A}\cdot {\mu}_{I}}{2{\rho}_{I}\cdot {D}_{h}^{2}\cdot S}\cdot \frac{L+{L}_{eqv}}{2}\\ \Delta {p}_{B{I}_{lam}}={f}_{shape}\frac{{\dot{m}}_{B}\cdot {\mu}_{I}}{2{\rho}_{I}\cdot {D}_{h}^{2}\cdot S}\cdot \frac{L+{L}_{eqv}}{2}\end{array}$$

where:

*f*_{shape}is the**Shape factor for laminar flow viscous friction**parameter value.*L*_{eqv}is the**Aggregate equivalent length of local resistances**parameter value.

In the turbulent flow regime, the pressure losses due to viscous friction are:

$$\begin{array}{l}\Delta {p}_{A{I}_{tur}}={f}_{Darc{y}_{A}}\frac{{\dot{m}}_{A}\cdot \left|{\dot{m}}_{A}\right|}{2{\rho}_{I}\cdot {D}_{h}\cdot {S}^{2}}\cdot \frac{L+{L}_{eqv}}{2}\\ \Delta {p}_{B{I}_{tur}}={f}_{Darc{y}_{B}}\frac{{\dot{m}}_{B}\cdot \left|{\dot{m}}_{B}\right|}{2{\rho}_{I}\cdot {D}_{h}\cdot {S}^{2}}\cdot \frac{L+{L}_{eqv}}{2}\end{array}$$

where *f*_{Darcy} is the Darcy friction factor at port
**A** or **B**, as indicated by the
subscript.

The Darcy friction factors are computed from the Haaland correlation:

$$\begin{array}{l}{f}_{Darc{y}_{A}}={\left[-1.8{\mathrm{log}}_{10}\left(\frac{6.9}{{\mathrm{Re}}_{A}}+{\left(\frac{{\epsilon}_{rough}}{3.7{D}_{h}}\right)}^{1.11}\right)\right]}^{-2}\\ {f}_{Darc{y}_{B}}={\left[-1.8{\mathrm{log}}_{10}\left(\frac{6.9}{{\mathrm{Re}}_{B}}+{\left(\frac{{\epsilon}_{rough}}{3.7{D}_{h}}\right)}^{1.11}\right)\right]}^{-2}\end{array}$$

where *ε*_{rough} is
the **Internal surface absolute roughness** parameter
value.

When the Reynolds number is between the **Laminar flow upper Reynolds number
limit** and the **Turbulent flow lower Reynolds number
limit** parameter values, the flow is in transition between laminar
flow and turbulent flow. The pressure losses due to viscous friction during the
transition region follow a smooth connection between those in the laminar flow
regime and those in the turbulent flow regime.

### Convective Heat Transfer

The convective heat transfer equation between the pipe wall and the internal gas volume is:

$${Q}_{H}={Q}_{conv}+\frac{{k}_{I}{S}_{surf}}{{D}_{h}}\left({T}_{H}-{T}_{I}\right)$$

*S*_{surf} is the pipe surface area,
*S*_{surf} =
4*S**L*/*D*_{h}.
Assuming an exponential temperature distribution along the pipe, the convective heat
transfer is

$${Q}_{conv}=\left|{\dot{m}}_{avg}\right|{c}_{{p}_{avg}}\left({T}_{H}-{T}_{in}\right)\left(1-\mathrm{exp}\left(-\frac{{h}_{coeff}{S}_{surf}}{\left|{\dot{m}}_{avg}\right|{c}_{{p}_{avg}}}\right)\right)$$

where:

*T*_{in}is the inlet temperature depending on flow direction.$${\dot{m}}_{avg}=\left({\dot{m}}_{A}-{\dot{m}}_{B}\right)/2$$ is the average mass flow rate from port

**A**to port**B**.$${c}_{{p}_{avg}}$$ is the specific heat evaluated at the average temperature.

The heat transfer coefficient, *h*_{coeff}, depends
on the Nusselt number:

$${h}_{coeff}=Nu\frac{{k}_{avg}}{{D}_{h}}$$

where *k*_{avg} is the thermal conductivity evaluated
at the average temperature. The Nusselt number depends on the flow regime. The Nusselt
number in the laminar flow regime is constant and equal to the value of the
**Nusselt number for laminar flow heat transfer** parameter. The
Nusselt number in the turbulent flow regime is computed from the Gnielinski
correlation:

$$N{u}_{tur}=\frac{\frac{{f}_{Darcy}}{8}\left({\mathrm{Re}}_{avg}-1000\right){\mathrm{Pr}}_{avg}}{1+12.7\sqrt{\frac{{f}_{Darcy}}{8}}\left({\mathrm{Pr}}_{avg}^{2/3}-1\right)}$$

where *Pr*_{avg} is the Prandtl number evaluated at
the average temperature. The average Reynolds number is

$${\mathrm{Re}}_{avg}=\frac{\left|{\dot{m}}_{avg}\right|{D}_{h}}{S{\mu}_{avg}}$$

where *μ*_{avg} is the dynamic viscosity evaluated at
the average temperature. When the average Reynolds number is between the **Laminar
flow upper Reynolds number limit** and the **Turbulent flow lower
Reynolds number limit** parameter values, the Nusselt number follows a smooth
transition between the laminar and turbulent Nusselt number values.

### Choked Flow

The choked mass flow rates out of the pipe at ports **A** and
**B** are:

$$\begin{array}{l}{\dot{m}}_{{A}_{choked}}={\rho}_{A}\cdot {a}_{A}\cdot S\\ {\dot{m}}_{{B}_{choked}}={\rho}_{B}\cdot {a}_{B}\cdot S\end{array}$$

where *a*_{A} and
*a*_{B} is the speed of sound at ports
**A** and **B**, respectively.

The unchoked pressure at port **A** or **B** is the value of
the corresponding Across variable at that port:

$$\begin{array}{l}{p}_{{A}_{unchoked}}=\text{A}\text{.p}\\ {p}_{{B}_{unchoked}}=\text{B}\text{.p}\end{array}$$

The choked pressures at ports **A** and **B** are obtained
by substituting the choked mass flow rates into the momentum balance equations for
the pipe:

$$\begin{array}{l}{p}_{{A}_{choked}}={p}_{I}+{\left(\frac{{\dot{m}}_{{A}_{choked}}}{S}\right)}^{2}\cdot \left(\frac{1}{{\rho}_{I}}-\frac{1}{{\rho}_{A}}\right)+\Delta {p}_{A{I}_{choked}}\\ {p}_{{B}_{choked}}={p}_{I}+{\left(\frac{{\dot{m}}_{{B}_{choked}}}{S}\right)}^{2}\cdot \left(\frac{1}{{\rho}_{I}}-\frac{1}{{\rho}_{B}}\right)+\Delta {p}_{B{I}_{choked}}\end{array}$$

*Δp*_{AIchoked} and
*Δp*_{BIchoked} are
the pressure losses due to viscous friction, assuming that the choking has occurred.
They are computed similar to *Δp*_{AI} and
*Δp*_{BI}, with the mass flow rates at
ports **A** and **B** replaced by the choked mass
flow rate values.

Depending on whether choking has occurred, the block assigns either the choked or unchoked
pressure value as the actual pressure at the port. Choking can occur at the pipe
outlet, but not at the pipe inlet. Therefore, if *p*_{Aunchoked}
≥ *p*_{I}, then port **A** is an inlet and *p*_{A} =
*p*_{Aunchoked}. If *p*_{Aunchoked}
< *p*_{I}, then port **A** is an outlet and

$${p}_{A}=\{\begin{array}{ll}{p}_{{A}_{unchoked}},\hfill & \text{if}{p}_{{A}_{unchoked}}\ge {p}_{{A}_{choked}}\hfill \\ {p}_{{A}_{choked}},\hfill & \text{if}{p}_{{A}_{unchoked}}{p}_{{A}_{choked}}\text{}\hfill \end{array}$$

Similarly, if *p*_{Bunchoked}
≥ *p*_{I}, then port **B** is an inlet and *p*_{B} =
*p*_{Bunchoked}. If *p*_{Bunchoked}
< *p*_{I}, then port **B** is an outlet and

$${p}_{B}=\{\begin{array}{ll}{p}_{{B}_{unchoked}},\hfill & \text{if}{p}_{{B}_{unchoked}}\ge {p}_{{B}_{choked}}\hfill \\ {p}_{{B}_{choked}},\hfill & \text{if}{p}_{{B}_{unchoked}}{p}_{{B}_{choked}}\text{}\hfill \end{array}$$

### Variables

To set the priority and initial target values for the block variables prior to simulation, use
the **Initial Targets** section in the block dialog box or Property
Inspector. For more information, see Set Priority and Initial Target for Block Variables and Initial Conditions for Blocks with Finite Gas Volume.

Nominal values provide a way to specify the expected magnitude of a variable in a model.
Using system scaling based on nominal values increases the simulation robustness. Nominal
values can come from different sources, one of which is the **Nominal
Values** section in the block dialog box or Property Inspector. For more
information, see Modify Nominal Values for a Block Variable.

### Assumptions and Limitations

The pipe wall is perfectly rigid.

The flow is fully developed. Friction losses and heat transfer do not include entrance effects.

The effect of gravity is negligible.

Fluid inertia is negligible.

This block does not model supersonic flow.

## Examples

## Ports

### Conserving

## Parameters

## References

[1] White, F. M., *Fluid Mechanics*.
7th Ed, Section 6.8. McGraw-Hill, 2011.

[2] Cengel, Y. A., *Heat and Mass
Transfer – A Practical Approach*. 3rd Ed, Section
8.5. McGraw-Hill, 2007.

## Extended Capabilities

## Version History

**Introduced in R2016b**