fluid_mechanics
652 Chapter 12 ■ Turbomachines The axial component of this equation applied to the one-dimensional simplification of flow through a turbomachine rotor with section 112 as the inlet and section 122 as the outlet results in The Euler turbomachine equation is the axial component of the momentof-momentum equation. T shaft m # 11r 1 V u1 2 m # 21r 2 V u2 2 (12.2) where T shaft is the shaft torque applied to the contents of the control volume. The “” is associated with mass flowrate into the control volume and the “ ” is used with the outflow. The sign of the V u component depends on the direction of V u and the blade motion, U. If V u and U are in the same direction, then V u is positive. The sign of the torque exerted by the shaft on the rotor, T shaft , is positive if T shaft is in the same direction as rotation, and negative otherwise. As seen from Eq. 12.2, the shaft torque is directly proportional to the mass flowrate, m # rQ. 1It takes considerably more torque and power to pump water than to pump air with the same volume flowrate.2 The torque also depends on the tangential component of the absolute velocity, V u . Equation 12.2 is often called the Euler turbomachine equation. Also recall that the shaft power, W # shaft, is related to the shaft torque and angular velocity by W # shaft T shaft v (12.3) By combining Eqs. 12.2 and 12.3 and using the fact that U vr, we obtain W # # shaft m 1 1U 1 V u1 2 m # 21U 2 V u2 2 (12.4) Again, the value of is positive when and U are in the same direction and negative otherwise. Also, W # V u V u shaft is positive when the shaft torque and are in the same direction and negative otherwise. Thus, W # v shaft is positive when power is supplied to the contents of the control volume 1pumps2 and negative otherwise 1turbines2. This outcome is consistent with the sign convention involving the work term in the energy equation considered in Chapter 5 1see Eq. 5.672. Finally, in terms of work per unit mass, w shaft W # shaftm # , we obtain w shaft U 1 V u1 U 2 V u2 (12.5) where we have used the fact that by conservation of mass, m # 1 m # 2. Equations 12.3, 12.4, and 12.5 are the basic governing equations for pumps or turbines whether the machines are radial-, mixed-, or axial-flow devices and for compressible and incompressible flows. Note that neither the axial nor the radial component of velocity enter into the specific work 1work per unit mass2 equation. [In the above merry-go-round example the amount of work your friend does is independent of how fast you jump “up” 1axially2 or “out” 1radially2 as you exit. The only thing that counts is your u component of velocity.] Another useful but more laborious form of Eq. 12.5 can be obtained by writing the righthand side in a slightly different form based on the velocity triangles at the entrance or exit as shown generically in Fig. 12.5. The velocity component V x is the generic through-flow component of velocity and it can be axial, radial, or in-between depending on the rotor configuration. From the large right triangle we note that or V 2 V 2 u V 2 x V 2 x V 2 V 2 u (12.6) x θ V W V x U V θ F I G U R E 12.5 Velocity triangle: V absolute velocity, W relative velocity, U blade velocity.
12.4 The Centrifugal Pump 653 From the small right triangle we note that Turbomachine work is related to changes in absolute, relative, and blade velocities. By combining Eqs. 12.6 and 12.7 we obtain V 2 x 1V u U2 2 W 2 V u U V 2 U 2 W 2 2 which when written for the inlet and exit and combined with Eq. 12.5 gives w shaft V 2 2 V 2 1 U 2 2 U 2 1 1W 2 2 W 2 1 2 2 (12.7) (12.8) Thus, the power and the shaft work per unit mass can be obtained from the speed of the blade, U, the absolute fluid speed, V, and the fluid speed relative to the blade, W. This is an alternative to using fewer components of the velocity as suggested by Eq. 12.5. Equation 12.8 contains more terms than Eq. 12.5; however, it is an important concept equation because it shows how the work transfer is related to absolute, relative, and blade velocity changes. Because of the general nature of the velocity triangle in Fig. 12.5, Eq. 12.8 is applicable for axial-, radial-, and mixed-flow rotors. F l u i d s i n t h e N e w s 1948 Buick Dynaflow started it Prior to 1948 almost all cars had manual transmissions which required the use of a clutch pedal to shift gears. The 1948 Buick Dynaflow was the first automatic transmission to use the hydraulic torque converter and was the model for present-day automatic transmissions. Currently, in the U.S. over 84% of the cars have automatic transmissions. The torque converter replaces the clutch found on manual shift vehicles and allows the engine to continue running when the vehicle comes to a stop. In principle, but certainly not in detail or complexity, operation of a torque converter is similar to blowing air from a fan onto another fan which is unplugged. One can hold the blade of the unplugged fan and keep it from turning, but as soon as it is let go, it will begin to speed up until it comes close to the speed of the powered fan. The torque converter uses transmission fluid (not air) and consists of a pump (the powered fan) driven by the engine drive shaft, a turbine (the unplugged fan) connected to the input shaft of the transmission, and a stator (absent in the fan model) to efficiently direct the flow between the pump and turbine. 12.4 The Centrifugal Pump One of the most common radial-flow turbomachines is the centrifugal pump. This type of pump has two main components: an impeller attached to a rotating shaft, and a stationary casing, housing, or volute enclosing the impeller. The impeller consists of a number of blades 1usually curved2, also sometimes called vanes, arranged in a regular pattern around the shaft. A sketch showing the essential features of a centrifugal pump is shown in Fig. 12.6. As the impeller rotates, fluid is sucked in through the eye of the casing and flows radially outward. Energy is added to the fluid by the rotating blades, and both pressure and absolute velocity are increased as the fluid flows from the eye to the periphery of the blades. For the simplest type of centrifugal pump, the Discharge Impeller Hub plate Eye Inflow Blade (a) Casing, housing, or volute (b) F I G U R E 12.6 Schematic diagram of basic elements of a centrifugal pump.
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652 Chapter 12 ■ Turbomachines<br />
The axial component of this equation applied to the one-dimensional simplification of flow<br />
through a turbomachine rotor with section 112 as the inlet and section 122 as the outlet results in<br />
The Euler turbomachine<br />
equation is the<br />
axial component of<br />
the momentof-momentum<br />
equation.<br />
T shaft m # 11r 1 V u1 2 m # 21r 2 V u2 2<br />
(12.2)<br />
where T shaft is the shaft torque applied to the contents of the control volume. The “” is associated<br />
with mass flowrate into the control volume and the “ ” is used with the outflow. The sign of the V u<br />
component depends on the direction of V u and the blade motion, U. If V u and U are in the same direction,<br />
then V u is positive. The sign of the torque exerted by the shaft on the rotor, T shaft , is positive<br />
if T shaft is in the same direction as rotation, and negative otherwise.<br />
As seen from Eq. 12.2, the shaft torque is directly proportional to the mass flowrate, m # rQ.<br />
1It takes considerably more torque and power to pump water than to pump air with the same volume<br />
flowrate.2 The torque also depends on the tangential component of the absolute velocity, V u .<br />
Equation 12.2 is often called the Euler turbomachine equation.<br />
Also recall that the shaft power, W # shaft, is related to the shaft torque and angular velocity by<br />
W # shaft T shaft v<br />
(12.3)<br />
By combining Eqs. 12.2 and 12.3 and using the fact that U vr, we obtain<br />
W # #<br />
shaft m 1 1U 1 V u1 2 m # 21U 2 V u2 2<br />
(12.4)<br />
Again, the value of is positive when and U are in the same direction and negative otherwise.<br />
Also, W # V u V u<br />
shaft is positive when the shaft torque and are in the same direction and negative otherwise.<br />
Thus, W # v<br />
shaft is positive when power is supplied to the contents of the control volume 1pumps2<br />
and negative otherwise 1turbines2. This outcome is consistent with the sign convention involving<br />
the work term in the energy equation considered in Chapter 5 1see Eq. 5.672.<br />
Finally, in terms of work per unit mass, w shaft W # shaftm # , we obtain<br />
w shaft U 1 V u1 U 2 V u2<br />
(12.5)<br />
where we have used the fact that by conservation of mass, m # 1 m # 2. Equations 12.3, 12.4, and 12.5<br />
are the basic governing equations for pumps or turbines whether the machines are radial-, mixed-,<br />
or axial-flow devices and for compressible and incompressible flows. Note that neither the axial<br />
nor the radial component of velocity enter into the specific work 1work per unit mass2 equation.<br />
[In the above merry-go-round example the amount of work your friend does is independent of how<br />
fast you jump “up” 1axially2 or “out” 1radially2 as you exit. The only thing that counts is your u<br />
component of velocity.]<br />
Another useful but more laborious form of Eq. 12.5 can be obtained by writing the righthand<br />
side in a slightly different form based on the velocity triangles at the entrance or exit as shown<br />
generically in Fig. 12.5. The velocity component V x is the generic through-flow component of velocity<br />
and it can be axial, radial, or in-between depending on the rotor configuration. From the<br />
large right triangle we note that<br />
or<br />
V 2 V 2 u V 2 x<br />
V 2 x V 2 V 2 u<br />
(12.6)<br />
x<br />
θ<br />
V<br />
W<br />
V x<br />
U<br />
V θ<br />
F I G U R E 12.5 Velocity triangle: V <br />
absolute velocity, W relative velocity, U blade velocity.