Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)
Hydraulic Power Recovery Turbines 267 tilting the guide vanes (Part #1) about a pivot pin (Part #4) parallel to the runner (Part #6) shaft axis to vary the velocity of the liquid flowing through the assembly at a proper flow orientation angle relative to the runner. Each guide vane is held in position by the pivot pin and by a slide pin (Part #5), which moves the guide vane by its position in the slot through the vane. The pivot pins are located in the two stationary vane rings or stage pieces (Part #2) and the slide pins are assembled to the two rotatable vane rings (Part #3). The stationary and rotatable rings establish the width of the inlet opening. They are the side walls of the vane assembly. The operating position of the vanes and the resultant through-flow cross-section area is dependent on the angular position of the rotatable vane ring in relation to the stationary rings. Between the guide vanes, the rotatable vane rings are shaped in a manner to achieve the correct velocity increase for each through-flow crosssection area. The rotatable vane rings perform the additional function of avoiding undesirable vane flutter, by a clamping action due to developed differential pressure. A reduction in pressure occurs in the flow passages due to the increase in velocity of the fluid, while the pressure acting on the out ward side areas of the rotatable rings is essentially the same as at the en~ trance to the vane passages. Because of the relatively large outward side areas of the rotatable rings, the clamping force is higher than the different hydraulic forces that act on the guide vanes and could cause vane flutter. However, the force is not restricting the adjustment of the guide vane position during operation. The cross-section of this HPRT is shown in Figure 14-16. The turbine is built basically like a multi-stage pump with standard bearing housings. The runner eyes of each stage face all in the same direction and a drum takes care of balancing the axial thrust. Figure 14-17 shows the crossunder in the bottom half. There are no crossovers. The top half contains the yoke assembly, which moves up and down and creates the rotational position of the rotatable rings and subsequently the resultant through-flow cross-section area of the guide vane openings. A crossbeam as shown in Figure 14-18 connects the yokes for synchronous travel. Individual setting of through-flow areas for each stage is possible by adjusting the nuts on the crossbeam. If required, throughflow areas for each stage can be adjusted differently to allow for an increase in the specific volume for compressible liquids, when the pressure reduces from stage to stage. This is another feature to achieve optimum performance. The up-and-down movement of the beam can be achieved by an electric or pneumatic actuator that is mounted on top of the beam cover,
Figure 14-16, of a HPRT of Company).
- Page 232 and 233: Figure 12-11. pump for 4,000 psi In
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Hydraulic Power Recovery Turbines 267<br />
tilting the guide vanes (Part #1) about a pivot pin (Part #4) parallel to the<br />
runner (Part #6) shaft axis to vary the velocity of the liquid flowing<br />
through the assembly at a proper flow orientation angle relative to the<br />
runner. Each guide vane is held in position by the pivot pin <strong>and</strong> by a slide<br />
pin (Part #5), which moves the guide vane by its position in the slot<br />
through the vane.<br />
The pivot pins are locat<strong>ed</strong> in the two stationary vane rings or stage<br />
pieces (Part #2) <strong>and</strong> the slide pins are assembl<strong>ed</strong> to the two rotatable vane<br />
rings (Part #3). The stationary <strong>and</strong> rotatable rings establish the width of<br />
the inlet opening. They are the side walls of the vane assembly. The operating<br />
position of the vanes <strong>and</strong> the resultant through-flow cross-section<br />
area is dependent on the angular position of the rotatable vane ring in<br />
relation to the stationary rings.<br />
Between the guide vanes, the rotatable vane rings are shap<strong>ed</strong> in a manner<br />
to achieve the correct velocity increase for each through-flow crosssection<br />
area.<br />
The rotatable vane rings perform the additional function of avoiding<br />
undesirable vane flutter, by a clamping action due to develop<strong>ed</strong> differential<br />
pressure. A r<strong>ed</strong>uction in pressure occurs in the flow passages due to<br />
the increase in velocity of the fluid, while the pressure acting on the out<br />
ward side areas of the rotatable rings is essentially the same as at the en~<br />
trance to the vane passages.<br />
Because of the relatively large outward side areas of the rotatable<br />
rings, the clamping force is higher than the different hydraulic forces that<br />
act on the guide vanes <strong>and</strong> could cause vane flutter. However, the force is<br />
not restricting the adjustment of the guide vane position during operation.<br />
The cross-section of this HPRT is shown in Figure 14-16. The turbine<br />
is built basically like a multi-stage pump with st<strong>and</strong>ard bearing housings.<br />
The runner eyes of each stage face all in the same direction <strong>and</strong> a drum<br />
takes care of balancing the axial thrust.<br />
Figure 14-17 shows the crossunder in the bottom half. There are no<br />
crossovers. The top half contains the yoke assembly, which moves up <strong>and</strong><br />
down <strong>and</strong> creates the rotational position of the rotatable rings <strong>and</strong> subsequently<br />
the resultant through-flow cross-section area of the guide vane<br />
openings.<br />
A crossbeam as shown in Figure 14-18 connects the yokes for synchronous<br />
travel. Individual setting of through-flow areas for each stage is<br />
possible by adjusting the nuts on the crossbeam. If requir<strong>ed</strong>, throughflow<br />
areas for each stage can be adjust<strong>ed</strong> differently to allow for an increase<br />
in the specific volume for compressible liquids, when the pressure<br />
r<strong>ed</strong>uces from stage to stage. This is another feature to achieve optimum<br />
performance. The up-<strong>and</strong>-down movement of the beam can be achiev<strong>ed</strong><br />
by an electric or pneumatic actuator that is mount<strong>ed</strong> on top of the beam<br />
cover,