The following data refer to a centrifugal pump which is designed to run at 1000 rpm against a head of 70 m.
The diameter of impeller at inlet and outlet = 300 mm and 600 mm respectively
The width of impeller at inlet and outlet = 100 mm and 50 mm respectively
Vane angle at outlet = 30°.
Discharge = 400 litres/s
Find (a) the vane angle at inlet, (b) theoretical head developed, (c) manometric efficiency, and (d) power required to drive the pump if the overall efficiency is 70%. Also find the corresponding mechanical efficiency.
Given data:
Speed of pump N =1000 rpm
Head H = 70 m
Internal diameter of impeller D_1=300 \mathrm{~mm}=0.3 \mathrm{~m}
External diameter of impeller D_2=600 \mathrm{~mm}=0.6 \mathrm{~m}
Width at outlet B_1=100 \mathrm{~mm}=0.1 \mathrm{~m}
Width at outlet B_2=50 \mathrm{~mm}=0.05 \mathrm{~m}
Vane angle at outlet \beta_2=30^{\circ}
Discharge Q=400 \text { litres } / \mathrm{s}=0.4 \mathrm{~m}^3 / \mathrm{s}
Overall efficiency \eta_o=0.70
The inlet and outlet velocity triangles are shown in Fig. 20.18.
(a) The velocity of flow at inlet is found to be
V_{f 1}=\frac{Q}{\pi D_1 B_1}=\frac{0.4}{\pi \times 0.3 \times 0.1}=4.244 \mathrm{~m} / \mathrm{s}
Tangential velocity of impeller at inlet is given by
U_1=\frac{\pi D_1 N}{60}=\frac{\pi \times 0.3 \times 1000}{60}=15.708 \mathrm{~m} / \mathrm{s}
From the inlet velocity triangle, we have
\tan \beta_1=\frac{V_{f 1}}{U_1}
or \beta_1=\tan ^{-1}\left(\frac{4.244}{15.708}\right)=15.12^{\circ}
(b) The velocity of flow at outlet is found to be
V_{f 2}=\frac{Q}{\pi D_2 B_2}=\frac{0.4}{\pi \times 0.6 \times 0.05}=4.244 \mathrm{~m} / \mathrm{s}
Tangential velocity of impeller at outlet is given by
U_2=\frac{\pi D_2 N}{60}=\frac{\pi \times 0.6 \times 1000}{60}=31.412 \mathrm{~m} / \mathrm{s}
From the outlet velocity triangle, we get
\tan \beta_2=\frac{V_{f 2}}{U_2-V_{w 2}}
or \tan 30^{\circ}=\frac{4.244}{31.412-V_{w 2}}
or V_{w 2}=31.412-\frac{4.244}{\tan 30^{\circ}}=31.412-7.351=24.061 \mathrm{~m} / \mathrm{s}
Theoretical head developed is given by Eq. (20.4) as
H_m=\frac{V_{w 2} U_2}{g}=\frac{24.061 \times 31.412}{9.81}=77.04 \mathrm{~m}
(c) The manometric efficiency is given by
\eta_{\text {mano }}=\frac{H}{H_m}=\frac{70}{77.04}=0.9086 \text { or } 90.86 \%
(d) The power required to drive the pump is
=\frac{\rho Q g H_m}{\eta_o}
=\frac{1000 \times 0.4 \times 9.81 \times 77.04}{0.7}=431.86 \times 10^3 \mathrm{~W}=431.86 \mathrm{~kW}
The corresponding mechanical efficiency is found from Eq. (20.14) as
\eta_{o}=\eta_{ma n o}\times\eta_{m} (20.14)
\eta_m=\frac{\eta_o}{\eta_{\text {mano }}}=\frac{0.7}{0.9086}=0.7704 \text { or } 77.04 \%