Example 15.4-3: Power Requirement
for Pumping a Compressible Fluid Through a Long Pipe
from Bird, Stewart, & Lightfoot, Transport Phenomena, 1960, p. 467.
Nathaniel
Chongsiriwatana and Steve Meier
CENG 402:
Transport Phenomena II
Spring 2001
Figure 1. Pumping
natural gas through a pipeline. Pumping stations spaced at
intervals of 10 miles recompress and cool the fluid to its
original temperature and pressure.
A natural gas, which may be considered pure methane, is to be pumped through a long smooth pipeline with a 2-ft inside diameter. The gas enters the line at 100 psia at a velocity of 40 ft/sec and at the ambient temperature of 70° F. Pumping stations are provided every 10 miles along the line, and at each of these stations the gas is recompressed and cooled to its original temperature and pressure (see Figure 1). Estimate the power that must be expended on the gas by each pumping station, assuming ideal gas behavior, flat velocity profiles, and negligible changes in elevation.
In solving this problem, one should consider the pipe and
compressor separately. The first step is to apply
Bernoullis Equation in differential form to a length element dz
of the pipe. This equation is then integrated between
planes 1 and 2 to obtain the unknown
pressure p2. Once p2 is known, we again apply
Bernoullis Equation to the system between planes
2 and 3 to determine the work done by the
pump.
Bernoullis Equation (15.2-3):
Because we are assuming flat velocity profiles, we can replace
the quantity <v3>/<v> to a very good
approximation with <v2>. Also, there are no
potential energy considerations and there is no work done on the
pipeline, and by definition:
[2]
If we then write the equation in differential form, we obtain:
> bernoullieq1:=v*dv+1/rho*dp+1/2*v^2*f/R[h]*dz=0;
Rh is given by the cross section of the pipeline
divided by the wetted perimeter (equation 6.2-16).
> R[h]:=(pi*d^2/4)/(pi*d);
> bernoullieq1:=expand(bernoullieq1/v^2);
We assume the methane can be described by the ideal gas
equation of state. In addition, a mass balance allows us to solve
for r and v in terms of other variables.
> eqnofstate:=p=rho*R*T1/M[w]; massbal:=rho*v=rho1*v1;
> s:=solve({eqnofstate,massbal},{rho,v}); assign(s);
Define both the differential change in velocity and r1
to further simplify the Bernoulli equation.
> dv:=diff(v,p)*dp; rho1:=p1*M[w]/(R*T1);
Because the pipe is long, we can assume the flow to be isothermal, thus
> T:=T1;
Section 1.3 showed that the viscosity of ideal gases is
independent of pressure. As a consequence, the Reynold's number,
defined as:
is also constant, since the system is isothermal. Because Re is
constant, the friction factor f is also constant. The
Bernoulli equation thus simplifies down to a form independent of
density, and identical to equation 15.4-18:
> bernoullieq1;
Integration of the first two terms from p=p1 to p=p2 and the last term from z=0 to z=L gives
> bernoullieq1:=-ln(p2/p1)+1/2*R*T1/M[w]/v1^2*((p2/p1)^2-1)+2*f*L/d;
In order to find f , we need to calculate the Reynolds number
> RE:='v1'*d/nu; where n is the kinematic viscosity =m / r
> v1:=1219.2; [cm/sec] (a.k.a. 40 ft/sec)
> d:=60.96; [cm] (a.k.a. 2 ft)
> nu:=2.424769e-2; [cm2/sec] n for methane at 100 psia and 70 F (a.k.a. 2.61e-5 ft2/sec)
> RE;
We can use this Re in conjunction with the graph of f vs Re on p. 186 of B, S, & L (Fig. 6.2-2) to find
> f:=.0025;
Additionally, we are given that
> M[w]:=16.0426; [g/mol] for methane
> T1:=294.261; [K] (a.k.a. 70 F)
> L:=1609344; [cm] (a.k.a. 10 miles)
> p1:=100; [psia]
> R:=8.3144e7; [g*cm^2*/sec^2/mol/K]
> s:=solve(bernoullieq1,p2);
> p2:=s[2];
Part (b) - Flow through the compressor
> restart;
Now we can use Bernoulli's equation in the form to obtain the
work done by the compressor:
[3]
> bernoullieq2:=(1/2)*(v3^2-v2^2)+Int(1/rho,p=p2..p3)+Ev=-W;
If we assume the compression is adiabatic, pr-g is a constant. We call g " g1" in this worksheet because plain g is a "protected" variable in MAPLE.
> eq1:=p*rho^(-gamma1)=p2*rho2^(-gamma1);
> rho:=solve(eq1,rho);
If we assume that we can neglect Êv through the compressor, the Bernoulli equation becomes:
> bernoullieq2:=(1/2)*(v3^2-v2^2)+int(1/rho,p=p2..p3)=-W;
Substitute in for p2 using the ideal gas law.
> p2:=rho2*R*T2/M[w];
> bernoullieq2;
Since the compressor cools the gas to its original temperature and pressure, p1 must equal p3. The same is true for the velocities v1 and v3.
> p3:=p1; v3:=v1;
The equation simplifies to...
> bernoullieq2;
The mass flow rate at point 1 is equal to the mass flow rate at point 2, thus:
> v2:=rho1*v1/rho2;
> bernoullieq2;
Substitute in for r1 and r2 using the ideal gas law.
> p2:='p2':
> bernoullieq2:=subs(rho1=p1*M[w]/(R*T1),rho2=p2*M[w]/(R*T2),bernoullieq2);
The flow is isothermal, thus T1 = T2.
> T1:=T2;
The final equation is:
> bernoullieq2;
Compare with the book's equation 15.4-23.
> bookeq:=v1^2/2*(1-(p1/p2)^2) + R*T2/M[w]*gamma1/(gamma1-1)*((p1/p2)^((gamma1-1)/gamma1)-1);
They are equal.
> simplify(expand(bookeq-lhs(bernoullieq2)),assume=positive);
Input given values:
> d:=60.96; [cm] (a.k.a. 2 ft)
> v1:=1219.2*cm/sec; [cm/sec] (a.k.a. 40 ft/sec)
> M[w]:=16.0426*g/mol; [g/mol] for methane
> T2:=294.261*K; [K] (a.k.a. 70° F)
> p1:=100; [psia]
> p2:=86.16233216; [psia] (from Part (a))
> R:=8.3144e7*g*cm^2/sec^2/mol/K; [g*cm2*/sec2/mol/K]
Calculate g. The heat capacity was found using data from the NIST webbook.
> Cp:=35.6; Cv:=Cp-8.314; gamma1:=Cp/Cv;
> W:=solve(bernoullieq2,W);
Using the FORTRAN program convu, we find that this equals
> W:=-7724.113*ft*lb[f]/lb[m];
Redefine R in different units
> R:=1.5443e3*ft*lb[f]/mol/Rank;
Redefine variables in units of Rankine, feet, and pounds.
> T2:=529.67*Rank;
> d:=2*ft;
> v1:=40*ft/sec;
> p1:=100*lb[f]/inch^2*(12^2*inch^2/ft^2);
> M[w]:=16.0426*lb[m]/mol;
The power required by the compressor is found by multiplying
the work by the mass flow rate, which is given by r1vA.
> power:=evalf(-W*v1*Pi*d^2*p1*M[w]/4/R/T2);
If we now convert the answer to units of horsepower, we obtain
very close to the books answer of 504 hp.
> power:=power*(hp/(550*ft*lb[f]/sec));