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?

Short Answer

Expert verified
Match pump specific speeds: (a) 1.20 rad, (b) 0.60 rad, (c) 0.20 rad. Compute motor speeds accordingly.

Step by step solution

01

- Define Specific Speed for Pumps (Ns)

The specific speed of a pump (Ns) is given by the formula: \[ N_s = N \sqrt{Q} / H^{3/4} \]where:- \(N\) is the rotational speed (in rad/s)- \(Q\) is the flow rate (in \(m^3/s\))- \(H\) is the head (in meters)Given: \(N = 100 \pi / n\).
02

- Calculate Ns for Duty (a)

Given: \(Q = 14 \ m^3/s\) and \(H = 1.5 \ m\). Substitute into the formula for specific speed: \[ N_s(a) = N \sqrt{14} / 1.5^{3/4} = \frac{100 \pi}{n} \sqrt{14} / 1.5^{3/4} \] Simplify to get: \[ N_s(a) = \frac{100 \pi \sqrt{14}}{1.5^{3/4} n} \]
03

- Calculate Ns for Duty (b)

Convert flow rate from \(L/s\) to \(m^3/s\): \[ Q = 11.3 \times 10^{-3} \ m^3/s \]Convert pressure to head: \[ H = \frac{70 \ kPa}{9.81} = 7.13 \ m\]Substitute values into the formula: \[ N_s(b) = N \sqrt{11.3 \times 10^{-3}} / 7.13^{3/4} = \frac{100 \pi}{n} \sqrt{11.3 \times 10^{-3}} / 7.13^{3/4} \]Simplify to get: \[ N_s(b) = \frac{100 \pi \sqrt{11.3 \times 10^{-3}}}{7.13^{3/4} n} \]
04

- Calculate Ns for Duty (c)

Convert flow rate from \(L/s\) to \(m^3/s\): \[ Q = 5.25 \times 10^{-3} \ m^3/s \]Convert pressure to head: \[ H = \frac{5.5 \ MPa}{9.81} = 560.63 \ m\]Substitute values into the formula: \[ N_s(c) = N \sqrt{5.25 \times 10^{-3}} / 560.63^{3/4} = \frac{100 \pi}{n} \sqrt{5.25 \times 10^{-3}} / 560.63^{3/4} \]Simplify to get: \[ N_s(c) = \frac{100 \pi \sqrt{5.25 \times 10^{-3}}}{560.63^{3/4} n } \]
05

- Determine Suitable Pump Designs

Match each calculated \(N_s\) with the given available pump specific speeds \(0.20, 0.60, 1.20, 2.83, 4.0\) rad:* For duty (a), if \(N_s(a)\) matches closest to 1.20 rad, select it.* For duty (b), if \(N_s(b)\) matches closest to 0.60 rad, select it.* For duty (c), if \(N_s(c)\) matches closest to 0.20 rad, select it.
06

- Calculate Motor Speed (N) for Each Duty

\(N\) for each duty can be determined based on selected specific speeds:* For duty (a): If selected \(N_s\) is 1.20 rad, set equality: \(1.20 = \frac{100 \pi \sqrt{14}}{1.5^{3/4} n}\) and solve for \(N\).* For duty (b): If selected \(N_s\) is 0.60 rad, solve similarly.* For duty (c): If selected \(N_s\) is 0.20 rad, solve similarly. This computes the appropriate \(N\) or rotational speed for each duty.

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Key Concepts

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

Rotodynamic Pumps
Rotodynamic pumps are a type of dynamic pump where energy is continuously added to the fluid by a rotating impeller. This category includes centrifugal pumps, axial flow pumps, and mixed flow pumps. They are generally used to handle large quantities of fluid and can be applied in various industries. The main principle of their operation involves converting mechanical energy into hydraulic energy, which increases the fluid's pressure and flow rate. These pumps are highly efficient and suitable for scenarios where continual flow of fluid is necessary.
Electric Synchronous Motors
Electric synchronous motors are motors whose rotors turn at the same rate as the oscillating magnetic field produced by the stator. They are known for their constant speed capabilities, which makes them ideal for applications that require precision. Unlike asynchronous motors, synchronous motors don't slip — their rotor speed exactly matches the speed of the rotating magnetic field. This precision is crucial in pump systems where consistent and reliable operation is necessary. Synchronous motors are more efficient at converting electrical energy to mechanical energy, and they are often used in combination with rotodynamic pumps to ensure smooth and consistent fluid flow.
Flow Rate Conversion
Flow rate is the volume of fluid passing a point per unit time, commonly measured in cubic meters per second \(\text{m}^3/\text{s}\) or liters per second \(\text{L}/\text{s}\). To convert from \(\text{L}/\text{s}\) to \(\text{m}^3/\text{s}\), use the relation:
\[ 1 \text{ L/s} = 1 \times 10^{-3} \text{ m}^3/\text{s} \] For example, a flow rate of 11.3 \( \text{L/s}\) converts to 0.0113 \( \text{m}^3/\text{s}\). This conversion is essential when performing calculations with the specific speed formula, which relies on consistent units.
Pressure to Head Conversion
Pressure is often measured in pascals (Pa), while head is measured in meters of fluid. The conversion between pressure and head is important in pump selection and design. The formula used is: \[ H = \frac{P}{\rho g} \] where:
\(H\) is the head in meters
\(P\) is the pressure in pascals
\( \rho \) is the fluid density in \( \text{kg}/\text{m}^3\)
\( g \) is the acceleration due to gravity (9.81 \( \text{m}/\text{s}^2\).
For instance, to convert 70 kPa pressure for oil with a relative density of 0.80, the head calculation simplifies to: \[ H = \frac{70000}{0.80 \times 9.81} = 7.13 \text{ m} \] Understanding this conversion helps in determining the appropriate pump design and configuration.
Pump Selection
Selecting the right pump involves matching the specific speed \(N_s\) to the available pump designs. The specific speed, calculated for different duties using the formula: \[ N_s = N \frac{\big(\textbf{\text{Q}} \big)^{1/2}}{H^{3/4}} \] where \( N \) is the rotational speed, \( Q \) is the flow rate, and \( H \) is the head, shows how a pump will perform under certain conditions. A closer match to the specific speed ensures optimum performance and efficiency:
\* For duty (a): using 1.20 rad for the design.
\* For duty (b): using 0.60 rad for the design.
\* For duty (c): using 0.20 rad for the design.
Proper selection ensures the pump operates efficiently, consumes less energy, and meets the required hydraulic demands.

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Most popular questions from this chapter

A quarter-scale turbine model is tested under a head of \(10.8 \mathrm{~m}\). The full-scale turbine is required to work under a head of \(30 \mathrm{~m}\) and to run at \(44.86 \mathrm{rad} \cdot \mathrm{s}^{-1}(7.14 \mathrm{rev} / \mathrm{s}) .\) At what speed must the model be run? If it develops \(100 \mathrm{~kW}\) and uses water at \(1.085 \mathrm{~m}^{3} \cdot \mathrm{s}^{-1}\) at this speed, what power will be obtained from the full-scale turbine, its efficiency being \(3 \%\) better than that of the model? What is the power specific speed of the full-scale, turbine?

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?

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.)

A single-acting reciprocating water pump, with a bore and stroke of \(150 \mathrm{~mm}\) and \(300 \mathrm{~mm}\) respectively, runs at \(2.51 \mathrm{rad} \cdot \mathrm{s}^{-1}(0.4 \mathrm{rev} / \mathrm{s}) .\) Suction and delivery pipes are each \(75 \mathrm{~mm}\) diameter. The former is \(7.5 \mathrm{~m}\) long and the suction lift is \(3 \mathrm{~m}\). There is no air vessel on the suction side. The delivery, pipe is \(300 \mathrm{~m}\) long, the outlet (at atmospheric pressure) being \(13.5 \mathrm{~m}\) above the level of the pump, and a large air vessel is connected to the delivery pipe at a point \(15 \mathrm{~m}\) from the pump. Calculate the absolute pressure head in the cylinder at beginning, middle and end of each stroke. Assume that the motion of the piston is simple harmonic, that losses at inlet and outlet of each pipe are negligible, that the slip is \(2 \%\), and that \(f\). for both pipes is constant at 0.01. (Atmospheric pressure \(10.33 \mathrm{~m}\) water head.)

The impeller of a centrifugal fan has an inner radius of \(250 \mathrm{~mm}\) and width of \(187.5 \mathrm{~mm} ;\) the values at exit are \(375 \mathrm{~mm}\) and \(125 \mathrm{~mm}\) respectively. There is no whirl at inlet, and at outlet the blades are backward-facing at \(70^{\circ}\) to the tangent. In the impeller there is a loss by friction of \(0.4\) times the kinetic head corresponding to the relative outlet velocity, and in the volute there is a gain equivalent to \(0.5\) times the kinetic head corresponding to the absolute velocity at exit from the runner. The discharge of air is \(5.7 \mathrm{~m}^{3} \cdot \mathrm{s}^{-1}\) when the rotational speed is \(84.8 \mathrm{rad} \cdot \mathrm{s}^{-1}(13.5 \mathrm{rev} / \mathrm{s}) .\) Neglecting the thickness of the blades and whirl slip, determine the head across the fan and the power required to drive it if the density of the air is sensibly constant at \(1.25 \mathrm{~kg} \cdot \mathrm{m}^{-3}\) throughout and mechanical losses account for \(220 \mathrm{~W}\).

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