In: Mechanical Engineering
A small-scale Kaplan turbine has a power output of $8 \mathrm{MW}$, an available head at turbine entry of $13.4 \mathrm{~m}$, and a rotational speed of $200 \mathrm{rev} / \mathrm{min}$. The inlet guide vanes have a length of $1.6 \mathrm{~m}$ and the diameter at the trailing edge surface is $3.1 \mathrm{~m}$. The runner diameter is $2.9 \mathrm{~m}$ and the hub-tip ratio is 0.4. Assuming the hydraulic efficiency is $92 \%$ and the runner design is "free-vortex," determine
The radial and tangential components of velocity at exit from the guide vanes
As P=ηHρgQHE, then the volume flow rate is
Q=PηHρgHE=8×1060.92×9810×13.4=66.15m/s
Therefore,
cr1=Q2πr1L=66.152π×1.55×1.6=4.245m/scx2=4QπD2t2(1−v2)=4×66.15π×2.92×0.84=11.922m/s
Parameter | Ratio r/rt | ||
---|---|---|---|
0.4 | 0.7 | 1.0 | |
Cθ2(m/s) | 9.955 | 5.687 | 3.982 |
tanα2 | 0.835 | 0.4772 | 0.334 |
α2(deg) | 39.86 | 25.51 | 18.47 |
U/Cx2 | 1.019 | 1.7832 | 2.547 |
β2(deg) | 10.43 | 52.56 | 65.69 |
β3(deg) | 45.54 | 60.72 | 68.57 |
Table 9.4 Calculated Values of Flow Angles
The component of axial velocity at the runner
As the specific work done is ΔW=U2cθ2 and ηH=ΔWgHE, then at the tip
cθ2=ηHgHEU2=0.92×9.81×13.430.37=3.892m/s
where the blade tip speed is U2=ΩD22=(200×π30)×2.92=30.37m/s,
cθ1=cθ2r2r1=3.892×1.451.55=3.725m/sα1=tan−1(cθ1cr1)=tan−1(3.7254.245)=41.26∘
The absolute and relative flow angles upstream and downstream of the runner at the hub, mid-radius, and tip.
Values α2,β2, and β3 given in Table 9.4 have been derived from the following relations:
α2=tan−1(cθ2cx2)=tan−1(cθ2tcx2rtr)β2=tan−1(Ωrcx2−tanα2)=tan−1(U2tcx2rrt−tanα2)β3=tan−1(Ucx2)=tan−1(U2tcx2rrt)
Finally, Figure 9.19 illustrates the variation of the flow angles, from which the large amount of blade twist mentioned earlier can be inferred.
There is the answer.