Figure 5.14 shows the rotor-inlet velocity diagram for an adiabatic compressor stage that has a constant mean radius (r_{m}) of 8.56 cm, together with the corresponding compressor map. The following operating conditions also apply:
• A stagewise constant axial-velocity component
• Inlet total pressure = 1.0 bar
• Inlet total temperature = 288 K
• Mass-flow rate = 7.0 kg/s
Assuming an average specific-heat ratio of 1.4, justify (on the basis of Figure 5.8) the axial-flow stage choice. You may take the standard sea-level pressure and temperature to be 1.0 bar and 288 K, respectively.
We begin by locating the stage operating conditions on the stage map:
\theta_{i n}=\theta_{0}={\frac{T_{t\ 0}}{T_{S T P}}}=1.0
\delta_{in}=\delta_{0}=\frac{p_{t\ 0}}{p_{S T P}}=1.0
It follows that
\dot{m}_{C}={\frac{\dot{m}\sqrt{\theta_{i n}}}{\delta_{i n}}}=7.0\,\mathrm{kg/s}
Referring to the rotor-inlet velocity triangle in Figure 5.14, we get
U_{m}=W_{1}\ \sin\beta_{1}+V_{1}\ \sin\alpha_{1}=304.6\,\mathrm{m/s}
V_{z}=V_{1}\ \cos\alpha_{1}=131.6\mathrm{\,m/s}
V_{\theta\ 1}=V_{1}\ \sin\alpha_{1}=76.0\ \mathrm{m/s}
N={\frac{U_{m}}{r_{m}}}{\frac{60}{2\pi}}\approx34,000\ \mathrm{rpm}
\frac{N}{\sqrt{\theta_{i n}}}=34,000\,\mathrm{rpm}
Now, referring to the stage map, we get the following variables:
{\frac{p_{t\ 2}}{p_{t\ 1}}}=1.85
\eta_{t-t}=0.8
Using this efficiency magnitude, and referring to expression (3.60), we have
T_{t\ r}=T_{t}+\frac{W^{2}-V^{2}}{2c_{p}} (3.60)
T_{t\ 2}=357.2\,\mathrm{K}
Now, applying Euler’s equation,
w_{s}=c_{p}(T_{t\ 2}-T_{t\ 1})=U_{m}(V_{\theta\ 2}-V_{\theta\ 1})
which yields
V_{\theta\ 2}=304.2\ {\mathrm{m/s}}
Pursuing the solution procedure,
V_{2}={\sqrt{V_{\theta\ 2}{}^{2}+V_{z}{}^{2}}}=331.5\ {\mathrm{m/s}}
V_{c r_{2}}={\sqrt{\left({\frac{2\gamma}{\gamma+1}}\right)R T_{t\ 2}}}=345.8\ {\mathrm{m/s}}
M_{c r_{2}}=\frac{V_{2}}{V_{c r_{2}}}=0.96
\rho_{2}=\left(\frac{p_{t\ 2}}{R T_{t\ 2}}\right)\left[1-\frac{\gamma-1}{\gamma+1}(M_{cr_{2}})^{2}\right]^{\frac{1}{\gamma-1}}=1.19\ \mathrm{kg/m^{3}}
At this point, we are prepared to compute the stage specific speed (N_{s}), by substituting the foregoing variables in expressions (5.28) and (5.29),
N_{s}={\frac{N{\sqrt{\frac{\dot m}{\rho_{e x}}}}}{(\Delta h_{t\ i d})^{\frac{3}{4}}}} (5.28)
\Delta h_{t\ i d}=c_{p}\,T_{t\ i n}\left[\left(\frac{p_{t\ e x}}{p_{t\ i n}}\right)^{\frac{\gamma-1}{\gamma}}-1\right] (5.29)
N_{s} = 2.38 radians
Finally, we see (by reference to Figure 5.8) that this specific-speed magnitude places this stage well within the axial-flow compressor-stage “dome.” This clearly justifies the axial-flow choice for this compressor stage.