An inward-flow reaction turbine has an inlet guide vane angle of \(30^{\circ}\) and the inlet edges of the runner blades are at \(120^{\circ}\) to the direction of whirl. The breadth of the runner at inlet is a quarter of the diameter at inlet and there is no velocity of whirl at outlet. The overall head is \(15 \mathrm{~m}\) and the rotational speed \(104.7 \mathrm{rad} \cdot \mathrm{s}^{-1}\) (16.67 rev/s). The hydraulic and overall efficiencies may be assumed to be \(88 \%\) and \(85 \%\) respectively. Calculate the runner diameter at inlet and the power developed. (The thickness of the blades may be neglected.)

Short Answer

Expert verified
The runner diameter at inlet is 0.86 m, and the power developed is 213.4 kW.

Step by step solution

01

- Known Values and Formulas

List all the given values:- Inlet guide vane angle, \(\beta_1 = 30^{\circ}\)- Inlet edges of runner blades angle to direction of whirl, \(\alpha_1 = 120^{\circ}\)- Overall head, \(H = 15 \,\text{m}\)- Rotational speed, \(\omega = 104.7 \,\text{rad/s}\)- Hydraulic efficiency, \(\eta_h = 88\% or 0.88\)- Overall efficiency, \(\eta_o = 85\% or 0.85\)Given relationships and formulas:- Breadth of runner at inlet \(b_1 = \frac{D_1}{4}\)- Power developed \(P = \eta_o \rho g Q H\)- Euler's equation for turbines: \[P = \rho Q \left( gH + \frac{\omega^2 D_1^2}{8} \right)\]
02

- Calculate Flow Rate Q

Use the hydraulic efficiency and head to find the flow rate:Given \[ \text{Hydraulic Efficiency} \eta_h = \frac{gH_1}{gH} \]Therefore, flow rate \[Q = \frac{H}{\eta_h} = \frac{15 \,\text{m}}{0.88} = 17.045 \,\text{m/s}\]
03

- Find the Runner Diameter at Inlet, D_1

The velocity triangle gives the relationship:Given \[\tan \beta_1 = \frac{C_{w1}}{U} \]Therefore, \[C_{w1} = U \tan \beta_1\]Since \[U = \frac{\omega D_1}{2}\]Substitute to find \[C_{w1}:\tan 30^{\circ} = \frac{C_{w1}}{\frac{104.7 D_1}{2}} \]Solving this gives \[D_1 = 0.86\,\text{m}\]
04

- Calculate Power Developed

Finally, calculate the power developed:Given \[P = \eta_o \rho g Q H\]Plugging in the values: \[P = 0.85 \times 1000 \,\text{kg/m}^3 \times 9.81 \,\text{m/s}^2 \times 17.045 \times 15 \,\text{m}\]Therefore, \[P = 213.4 \,kW\]

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Key Concepts

These are the key concepts you need to understand to accurately answer the question.

fluid mechanics
Fluid mechanics is the branch of physics concerned with the behavior of fluids (liquids and gases) and the forces on them. In the context of an inward-flow reaction turbine, understanding fluid mechanics is crucial because this helps us model how water (a fluid) flows through the turbine blades. This turbine uses water's kinetic and potential energy to generate power. Since the water flow is directed inward from the periphery to the centre, the motion and behavior of fluids through the turbine are pivotal for its efficiency and effectiveness. Concepts like continuity equation, Bernoulli's principle, and potential energy transformations are heavily applied here.
turbine efficiency
Turbine efficiency is a measure of how well the turbine converts the energy in the fluid (water, in this case) into useful mechanical energy. There are different efficiency types to consider: hydraulic efficiency and overall efficiency. Hydraulic efficiency (\( \eta_h\) determines the ratio of the mechanical energy produced by the water pressure to the input energy. For our turbine, this value is 88%. Overall efficiency (\( \eta_o\) accounts for all energy losses including those due to mechanical friction and electrical generation inefficiencies. It is 85% in this exercise. High efficiencies imply that there are minimal losses and the turbine design effectively harnesses the energy available in the fluid.
velocity triangles
Velocity triangles are graphical representations used to understand the velocities of fluids at different points in a turbine. They help illustrate the relationship between the different velocity components like absolute velocity, relative velocity, and the whirl velocity. For our problem, we have inlet and outlet triangles, where we work with the angles of the guide vane (\( \beta_1 = 30^\circ \)) and the runner blade (\( \alpha_1 = 120^\circ \)). The key part of solving turbine problems is correctly interpreting these triangles to find relationships like the tangential component of velocity (\( \C_{w1}\)) and blade speed (\( \U = \frac{\omega D_1}{2}\)). This allows us to eventually find crucial measurements like the runner diameter.
power calculation
Power calculation in turbines involves determining the useful work output from the available hydraulic energy. The power developed (\( \P\)) is derived using the formula: \( P = \eta_o \rho g Q H\). In this exercise, we use the given overall efficiency (85%), fluid density (\( \rho = 1000 \ kg/m^3\)), gravitational acceleration (\( g = 9.81 \ m/s^2\)), flow rate (\( Q = 17.045 \ m^3/s\)), and head (\( H = 15 \ m\). Substituting these values into the formula gives \( \P = 213.4 \ kW\), which is the amount of power generated by the turbine under given conditions. This illustrates the practical application of theoretical aspects in hydraulic engineering.
hydraulic engineering
Hydraulic engineering focuses on the flow and conveyance of fluids, primarily water and sewage. It encompasses the design and management of systems and structures like dams, channels, and turbines. Inward-flow turbines like the one in our exercise require strong hydraulic engineering principles for design efficiencies. Understanding pressure dynamics, fluid flow characteristics, and energy conversions is essential. This ensures that the water pressure and flow are harnessed optimally to produce energy. By calculating hydraulic and overall efficiencies, designing velocity triangles and ensuring the conversion of hydraulic power to mechanical energy, hydraulic engineering plays a pivotal role in the effective functioning of reaction turbines.

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Most popular questions from this chapter

A reciprocating pump has two double-acting cylinders each \(200 \mathrm{~mm}\) bore and \(450 \mathrm{~mm}\) stroke, the cranks being at \(90^{\circ}\) to each other and rotating at \(2.09 \mathrm{rad} \cdot \mathrm{s}^{-1}\) (20 rev/min). The delivery pipe is \(100 \mathrm{~mm}\) diameter, \(60 \mathrm{~m}\) long. There are no air vessels. Assuming simple harmonic motion for the pistons determine the maximum and mean water velocities in the delivery pipe and the inertia pressure in the delivery pipe near the cylinders at the instant of minimum water velocity in the pipe.

The following duties are to be performed by rotodynamic pumps driven by electric synchronous motors, speed \(100 \pi / n \mathrm{rad} \cdot \mathrm{s}^{-1}(=50 / n \mathrm{rev} / \mathrm{s})\), where \(n\) is an integer: (a) \(14 \mathrm{~m}^{3} \cdot \mathrm{s}^{-1}\) of water against \(1.5 \mathrm{~m}\) head; \((b)\) oil (relative density \(0.80\) ) at \(11.3 \mathrm{~L} \cdot \mathrm{s}^{-1}\) against \(70 \mathrm{kPa}\) pressure; \((c)\) water at \(5.25 \mathrm{~L} \cdot \mathrm{s}^{-1}\) against \(5.5 \mathrm{MPa}\). Designs of pumps are available with specific speeds of \(0.20,0.60,1.20,2.83,4.0\) rad. Which design and speed should be used for each duty?

\(13.23\) A fluid coupling is to be used to transmit \(150 \mathrm{~kW}\) between an engine and a gear-box when the engine speed is \(251.3 \mathrm{rad} \cdot \mathrm{s}^{-1}\) (40 rev/s). The mean diameter at the outlet of the primary member is \(380 \mathrm{~mm}\) and the cross-sectional area of the flow passage is constant at \(0.026 \mathrm{~m}^{2}\). The relative density of the oil is \(0.85\) and the efficiency of the coupling \(96.5 \%\). Assuming that the shock losses under steady conditions are negligible and that the friction loss round the fluid circuit is four times the mean velocity head, calculate the mean diameter at inlet to the primary member.

During a laboratory test on a water pump appreciable cavitation began when the pressure plus velocity head at inlet was reduced to \(3.26 \mathrm{~m}\) while the total head change across the pump was \(36.5 \mathrm{~m}\) and the discharge was \(48 \mathrm{~L} \cdot \mathrm{s}^{-1} .\) Barometric pressure was \(750 \mathrm{~mm} \mathrm{Hg}\) and the vapour pressure of water \(1.8 \mathrm{kPa}\). What is the value of \(\sigma_{\mathrm{c}}\) ? If the pump is to give the same total head and discharge in a location where the normal atmospheric pressure is \(622 \mathrm{~mm} \mathrm{Hg}\) and the vapour pressure of water \(830 \mathrm{~Pa}\), by how much must the height of the pump above the supply level be reduced?

A centrifugal fan, for which a number of interchangeable impellers are available, is to supply air at \(4.5 \mathrm{~m}^{3} \cdot \mathrm{s}^{-1}\) to a ventilating duct at a head of \(100 \mathrm{~mm}\) water gauge. For all the impellers the outer diameter is \(500 \mathrm{~mm}\), the breadth \(180 \mathrm{~mm}\) and the blade thickness negligible. The fan runs at \(188.5 \mathrm{rad} \cdot \mathrm{s}^{-1}\) ( \(\left.30 \mathrm{rev} / \mathrm{s}\right)\). Assuming that the conversion of velocity head to pressure head in the volute is counterbalanced by the friction losses there and in the impeller, that there is no whirl at inlet and that the air density is constant at \(1.23 \mathrm{~kg} \cdot \mathrm{m}^{-3}\), determine the most suitable outlet angle of the blades. (Neglect whirl slip.)

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