1) Researchers tested the effects of a new diffuser design and additional tail piece on the performance of an industrial axial-flow pump.
2) Computational fluid dynamics (CFD) analysis and laboratory experiments showed that with an 8-vane impeller, the new diffuser and tail piece improved pump efficiency by 3.9% compared to the original design.
3) However, with a 5-vane impeller, the original pump design performed better due to a mismatch between the impeller and diffuser vane angles with the new design.
International Journal of Engineering Research and Applications (IJERA) is an open access online peer reviewed international journal that publishes research and review articles in the fields of Computer Science, Neural Networks, Electrical Engineering, Software Engineering, Information Technology, Mechanical Engineering, Chemical Engineering, Plastic Engineering, Food Technology, Textile Engineering, Nano Technology & science, Power Electronics, Electronics & Communication Engineering, Computational mathematics, Image processing, Civil Engineering, Structural Engineering, Environmental Engineering, VLSI Testing & Low Power VLSI Design etc.
The objective of this project was to identify various methods for well test in horizontal wells. Well test analysis in horizontal wells is applied to find the reservoir parameters like permeability and skin factor and the result from the chosen methods will be compared to the result of some famous software like Kappa Saphir, PanSystem, etc which are used in oil and gas industries.
International Journal of Engineering Research and Applications (IJERA) is an open access online peer reviewed international journal that publishes research and review articles in the fields of Computer Science, Neural Networks, Electrical Engineering, Software Engineering, Information Technology, Mechanical Engineering, Chemical Engineering, Plastic Engineering, Food Technology, Textile Engineering, Nano Technology & science, Power Electronics, Electronics & Communication Engineering, Computational mathematics, Image processing, Civil Engineering, Structural Engineering, Environmental Engineering, VLSI Testing & Low Power VLSI Design etc.
The objective of this project was to identify various methods for well test in horizontal wells. Well test analysis in horizontal wells is applied to find the reservoir parameters like permeability and skin factor and the result from the chosen methods will be compared to the result of some famous software like Kappa Saphir, PanSystem, etc which are used in oil and gas industries.
Production optimization using gas lift techniqueJarjis Mohammed
After completed the drilling, set the tubing and completed the well successfully, Petroleum engineers realize that the hydrocarbon fluid won't lift up from bottom hole to the surface by its reservoir drives which are mainly gas cap or water drive. Simply the gas lift technique is to reduce the density of hydrocarbon fluid inside the well to lift it to the surface by injecting compressed gas.
Production Optimization using nodal analysis. The nodal systems analysis approach is a very flexible method
that can be used to improve the performance of many well
systems. The nodal systems analysis approach may be used to analyze
many producing oil and gas well problems. The procedure can
be applied to both flowing and artificial
Piping around of pumps needs to some special requirements. Here you can find some of these requirements talked in a class.
You can find more details in piping and plant design academy.
Evaluating performance of centrifugal pump through cfd while modifying the su...eSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology
Evaluating performance of centrifugal pump through cfd while modifying the su...eSAT Journals
Abstract
For operating the pump there are many factor affect pump working which include their speed, suction head, exhaust head,
properties of liquid, and physical arrangement etc. cavitations, vibration, reduced efficiency, and lowered capacity could cause
serious trouble like Suction Head available, Excessive suction lift, shallow inlet submergence. Category of connection and
arrangement are the suction conditions.The conventional suction geometry is not efficient for higher capacity of pump and thus
reduced discharge on the delivery side. Intake manifold is being designed for this work. The previous configuration would be
studied using CFD techniques while pursuing the objective of arriving at the most efficient geometry for the given application.
Key Wors: centrifugal pump, discharge, CFD
Production optimization using gas lift techniqueJarjis Mohammed
After completed the drilling, set the tubing and completed the well successfully, Petroleum engineers realize that the hydrocarbon fluid won't lift up from bottom hole to the surface by its reservoir drives which are mainly gas cap or water drive. Simply the gas lift technique is to reduce the density of hydrocarbon fluid inside the well to lift it to the surface by injecting compressed gas.
Production Optimization using nodal analysis. The nodal systems analysis approach is a very flexible method
that can be used to improve the performance of many well
systems. The nodal systems analysis approach may be used to analyze
many producing oil and gas well problems. The procedure can
be applied to both flowing and artificial
Piping around of pumps needs to some special requirements. Here you can find some of these requirements talked in a class.
You can find more details in piping and plant design academy.
Evaluating performance of centrifugal pump through cfd while modifying the su...eSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology
Evaluating performance of centrifugal pump through cfd while modifying the su...eSAT Journals
Abstract
For operating the pump there are many factor affect pump working which include their speed, suction head, exhaust head,
properties of liquid, and physical arrangement etc. cavitations, vibration, reduced efficiency, and lowered capacity could cause
serious trouble like Suction Head available, Excessive suction lift, shallow inlet submergence. Category of connection and
arrangement are the suction conditions.The conventional suction geometry is not efficient for higher capacity of pump and thus
reduced discharge on the delivery side. Intake manifold is being designed for this work. The previous configuration would be
studied using CFD techniques while pursuing the objective of arriving at the most efficient geometry for the given application.
Key Wors: centrifugal pump, discharge, CFD
Hola mi nombre es Eloy, soy diseñador, sneakerhead y fan de starwars.
Me gradué en la Universidad Nacional de La Plata en Buenos Aires, Argentina y desde entonces trabajo de manera profesional tanto en equipo, como freelance.
Soy versátil, positivo y proactivo.
Influence of number of impeller and diffuser blades on the pressure recovery ...eSAT Journals
Abstract Impeller is a very important element in rotating devices to deliver energy to/from the fluid. The diffusers are essential for effective transformation of the kinetic power produced by the rotor in a centrifugal fan. Hence the flow in the impeller and diffuser passages is the important phenomenon in optimizing the performance. These impeller and diffuser flow passages are the most complex regions to predict the flow behavior. With the advanced development of Particle Image Velocimetry as well as convenient numerical CFD tools, it has become possible to reach at an accurate result well-matched with the real behavior of the flow. Hence, in this work moving mesh technique is used to get a numerical solution for the estimation of actual flow manner. Numerous research works have been done recently to get the physics of fluid flow through impeller and diffuser, both numerically and experimentally. But it is found from the literature that the study on the performance of the fan by changing the number of impeller and diffuser blades together in a combination has not been the emphasis of attention in these works. Hence a numerical analysis has been carried out in this paper to comprehensively lookout the fluid interaction in impeller-diffuser as well as to envisage the flow behavior of the fan by changing the number of impeller and diffuser blades together in combination. For the same number of impeller blades, it is found from the analysis that a higher static pressure rise coefficient is achieved at the outlet of the fan for smaller number of diffuser blades. It is also found that larger the number of impeller blades, larger is the static pressure rise coefficient for the same number of diffuser blades, hence performance gets improved. Key Words: Unsteady flow, Recirculation zone, Turbulence, Impeller vane, Diffuser vane, Static pressure rise.
Jet pump is a type of mechanical device where the extra energy is provide by jet in mixing chamber. This jet is the fluid again circulate from diffuser exit to mixing chamber for better performance. This is also known as motive fluid. So the effects of change in geometrical parameter (Diffuser angle) on its performance were investigated. The set of experiment were carried out to study the effect of diffuser angle on the performance of jet pump. The performance of the jet pump is described by three sets of curves, Discharge vs. Head, Input power vs. Head, and Efficiency vs. Head. Changing the diffuser angle will affect jet pump behavior. Venturi diffuser angle was found to be an important geometrical parameter to characterize the maximum suction lift of the jet pump.
Performance, Optimization and CFD Analysis of Submersible Pump Impellerijsrd.com
To improve the efficiency of submersible flow pump, Computational Fluid Dynamics (CFD) analysis is one of the advanced tools used in the pump industry. A detailed CFD analysis was done to predict the flow pattern inside the impeller which is an active pump component. From the results of CFD analysis, the velocity and pressure in the outlet of the impeller is predicted. CFD analyses are done using ANSYS CFX software. In this research paper we will modified the impeller design by choosing some parameter.
Brimmed diffuser is collection�acceleration device which shrouds a wind turbine.For a given turbine di ameter,the power augmentation can be achieved by brimmed diffuser,p opularly known as wind lens. The present numerical investigation deals with the effect of low pressure region created by wind l ens and hence to analyze the strong vortices formed by a brim attached to the shroud diffuser at exit. Also in this analysis,a c omparative numerical prediction of mass flow rates through the wind turbine has been carried out with various types of wind lens wh ich in turn helps to optimize the torque augmentati on. It has been numerically proved that there is significant increase in the wa ke formation & vortex strength when brimming effect is added to a diffuser
Cavitation Effects in Centrifugal Pumps- A ReviewIJERA Editor
Cavitation is one of the most challenging fluid flow abnormalities leading to detrimental effects on both the
centrifugal pump flow behaviors and physical characteristics. Centrifugal pumps’ most low pressure zones are the
first cavitation victims, where cavitation manifests itself in form of pitting on the pump internal solid walls,
accompanied by noise and vibration, all leading to the pump hydraulic performance degradation. In the present
article, a general description of centrifugal pump performance and related parameters is presented. Based on the
literature survey, some light were shed on fundamental cavitation features; where different aspects relating to
cavitation in centrifugal pumps were briefly discussed.
Numerical Investigation of Flow Field Behaviour and Pressure Fluctuations wit...Mustansiriyah University
this present work, CFD numerical method is applied to analyses the flow field in
an axial flow pump qualitative and quantitative analyses. Qualitative analysis for these
parameters comprise static pressure variations, dynamic pressure variations, velocity magnitude,
turbulent kinetic energy, shear stress. Quantitative analysis including the pressure fluctuations in
frequency domain analysis under different operation conditions. Also, sliding mesh method and
turbulence model type k- epsilon are used. Various monitoring points are stalled in order to
analyses pressure fluctuation mechanism in the impeller blade. The numerical results revealed
that the flow field for pressure and velocity are increase start from the suction side of the pump
to discharge side. Also, the results found that the high pressure occurs at the discharge side
along the axial direction of the impeller. The maximum value of pressure fluctuations is
occurred at tip blade region due to high interaction flow at this particular area. Moreover, the
pressure decreases as flow rate in the pump increases. Additionally, the results shown that the
pressure fluctuations have four peaks and four valleys the similar impeller blades number.
Furthermore, there are different positive and negative pressure regions, the negative pressure
area occurs due to lower pressure zone at inlet impeller area and hence which can lead to cause
occurrence of cavitation in this specific area. The current numerical demonstration results can
help the researches for further axial flow pump design.
Flow analysis of centrifugal pump using CFX solver and remedies for cavitatio...IJERA Editor
In this scholarly thesis pertinent to the working of centrifugal pump, a CFD solver namely CFX is employed in order to simulate fluid flow characteristics with well-defined constraints and boundary conditions defining the problem. Stringent solid model is meticulously prepared encompassing the present day usage and constructional features of a centrifugal pump and is constrained with various boundary conditions having fixed domain in order to evaluate plots and results. To spearhead and facilitate this analysis program a numerical approximation tool with high degree of convergence rate called ANSYS 15.0 software is used. The ASNYS software avoids tedious calculations presumably impending in the design procedure and uses ultimate numerical tool to approximate the solution of the partial differential equations associated with continuity, momentum and energy phases of a flow problem in a 3-D model. This exquisite feature of ANSYS enables designer to optimize the design procedure in an iterative manner based on the final plots of post-processing phase. In addition, the scholarly writing also constitutes the appraisal of the most debilitating and painstaking problem retarding the efficiency of the centrifugal pump known as cavitation. Possible remedies for overcoming this problem will be indirectly inferred from the various plots and figures derived from the post-processing phase of the design process.
DESIGN IMPROVEMENTS OF VARIABLE DISPLACEMENT PUMPS-A REVIEWijiert bestjournal
In Variable displacement pump the displacement or amount of fluid pumped per revolution of
pump‟s input shaft can be varied as per requirement. This paper investigate the different
improvements achieved for increase the efficiency of variable displacement pump .This paper
also discussed about the alternative mechanisms for variable displacement pump to improve
efficiency and cost reduction of pump.
Design and Development of Transonic Axial Flow Compressor Rotor BladeIJERDJOURNAL
Abstract:- This paper is about a new computational fluid dynamics developed for the transonic flow in a compressor rotor. Due to 3-Dimensional blade modification the arrangements satisfying the required boundary condition. Engine compressor towards distorted inflow has to be taken in account which is already in the design phase. Flow separation over the blade surface reduction and elimination can improve better aerodynamic, performance, efficiency and stall margin. NASA transonic rotor tip critical in baseline blade rotor performance energizing the low momentum boundary layer, controlling the inception of stall. A Profile generator are attached on the inner casing of the rotor ahead to the loading edge of the rotor and it is influenced on the overall performance which has been studied.
IRJET- Design and Performance Curve Generation by CFD Analysis of Centrifugal...
conference paper
1. 20th Australasian Fluid Mechanics Conference
Perth, Australia
5-8 December 2016
Effects of a new-design diffuser and a tail piece on an axial-flow pump’s
performance
R.F. Rosier, V.V. Avakian and B.P. Huynh
Faculty of Engineering and Information Technology, University of Technology Sydney, Broadway, NSW 2007, Australia
Abstract
Measurements have been conducted to gauge the effects of a
new-design diffuser and an additional tail-piece on the
performance of an industry-sized axial-flow pump unit. The new-
design diffuser was seen in a previous study to reduce the
swirling motion that would eventually dissipate as lost energy
and was still present in the flow as it exits from the standard
pump-unit that was originally fitted with a conventional conical
diffuser. The additional tail-piece, which is conical with an apex
angle of 20° is fitted to the new diffuser’s exit to allow for a
gradual change in the flow area from the diffuser’s exit to the
discharge pipe, instead of a sudden expansion. Impellers with 5
vanes and 8 vanes have been used. With the 8-vane impeller, an
improvement in performance has been obtained, compared with
the standard pump, when both the new diffuser and the additional
tail-piece are used together. With the 5-vane impeller, however,
the standard pump performs better. CFD (Computational Fluid
Dynamics) analysis using ANSYS CFX has also been conducted;
and this also shows the benefits of the additional tail-piece when
the 8-vane impeller is used.
Introduction
During the 1990’s a new type of diffuser was designed for an
Ornel axial-flow pump, for improving its performance by
reducing the fluid swirl which is still present in the flow as it
exits from the standard pump-unit that was originally fitted with
a conventional stator followed by conical diffuser. This residual
swirl would eventually dissipate as lost energy and hence
reducing pump efficiency.
Previous laboratory research showed there is an increase in
pressure along the new diffuser when compared to the
conventional stator-conical-diffuser, hence a possible reduction
in the fluid swirl. However the overall pump performance was
less than the original equipment manufacturer (OEM) figure. One
main reason was believed to be due to a sudden enlargement at
the outlet of the new diffuser causing much wasteful re-
circulation [1] (see Figure 1)
To better determine the source of degradation of the overall
pump-performance and possible improvements which could be
made to the new diffuser, dimensional investigation,
computational fluid dynamics (CFD) analysis and laboratory
experimentation were conducted.
CFD modelling was used to help predict the flow patterns and
turbulence through the axial-flow pump and also as part of the
design process for a tail-piece component. The tail piece was to
be installed at the outlet of the new diffuser to mitigate the
sudden enlargement’s detrimental effects.
Experimental laboratory testing was then performed using the
test rig located at the University of Technology Sydney. By
using new pump parts combined with the new diffuser and tail-
piece addition, performance of the pump unit was determined.
Analysis and Design
The pump used for this work is an Ornel 300AX axial-flow
pump. The original configuration is a single stage with a
standard stator-conical-diffuser arrangement. The new diffuser
replaces the standard arrangement and was designed to reduce
the residual swirl still present in the flow, as found in a previous
study [1]. However the new design introduced a sudden
enlargement at the outlet of the diffuser which creates flow
separation and a large low-pressure recirculation region resulting
in pump-efficiency reduction, as the CFD analysis shows in
Figure 1.
Figure 1. 2D-streamline flow-pattern and total-pressure distribution
through pump with the new diffuser. Flow direction is from left to right.
A coordinate measurement machine (CMM) was used to measure
the new diffuser by laser scanning the surfaces. From the CMM
scanned-image a 3D model was created to determine the parts’
dimensions and be used with the CFD analysis. From the model
the diffuser-vane inlet-angle α3 was established at three sections
and compared to the impeller’s absolute outlet-velocity angle α2
of both the five-vane and eight-vane impellers. The
recommended tolerance between the two angles is ±5° [2]. It
was discovered there is a mismatch between the angles for the
five-vane impeller, however a good match for the eight-vane
impeller; this is shown in Table 1. This suggests that the new
diffuser is more suited to high-flow applications with the eight-
vane impeller.
To remove the sudden enlargement from the new diffuser outlet
and minimise its detrimental effects, a tail piece was designed
New Diffuser
Guide vanes Impeller
2. Page 2 of 4
with the help of CFD analysis. A number of different design
shapes were analysed using turbulence models within ANSYS
CFX. The turbulence model selected was Shear Stress Transport
(SST) which is a variant of k-ω and k-ε models. The k-ε models
are the standard for fully turbulent flows but studies conducted
by Menter [3] showed that the prediction of boundary layer
separation was not accurate, whereas a k-ω model would give a
more accurate prediction of fluid turbulence close to a wall. All
CFD models were run using the best efficiency point (BEP) from
the OEM pump curves. For the five-vane impeller, flow is 318
L/s and 564 L/s for the eight-vane impeller.
Angle
Section
AA BB CC
5 vane α2 33° 34° 36°
α3 55° 59° 63°
5 vane Δ 22° 25° 27°
8 vane α2 51° 56° 61°
α3 55° 59° 63°
8 vane Δ 4° 3° 2°
Table 1. Impeller’s absolute outlet-velocity angle α2 for 5-vane and 8-
vane impellers, and new-diffuser vane inlet-angle α3. Δ is the difference
between α3 and α2. Sections are at radial distance of 174 mm (AA), 235
mm (BB) and 304 mm (CC). All angles are measured relative to the
tangential direction.
The CFD analysis shows that a conical tail-piece with apex angle
20° results in the least amount of recirculation close to the
diffuser-outlet vane tips and the following area, as shown in
Figure 2. Due to design restrictions with possible interference
between the tail piece and the line shaft coupling, 20° is the
smallest apex angle which could be used.
Comparison of pressure rise between the new-diffuser-only
arrangement and the new diffuser combined with the tail-piece
addition using a five-vane impeller is shown in Figure 3 and
Figure 4. Pressure at seven evenly spaced cross-sectional planes
along the diffuser were constructed through the CFD model. It
was observed that with the tail-piece addition a greater
percentage of the cross-sectional planes has higher pressure.
This thus suggests that the gradual reduction of the flow-
passage’s cross-sectional area thanks to the tail-piece helps to
sustain higher pressure for a prolonged distance through the new
diffuser. This result was also found with an eight-vane impeller,
as shown in Figure 5 and Figure 6.
To manufacture the tail piece a 3D printer was used. This
method was selected over casting due to the low manufacturing
cost. With casting, finish-machining and pattern production are
required, plus the possibility of defects such as porosity, material
shrinkage and poor surface finish. Thus 3D printer was deemed a
more accurate and cost effective option. In Figure 7 the 3D
model of the tail piece and the method of installation are shown.
The material used is Acrylonitrile Butadiene Styrene (ABS)
which has a high impact resistance and corrosion resistance and
is a common material used in the manufacture of clear water
piping and fittings.
Laboratory Testing
The pump testing rig is a closed loop system with the axial-flow
pump mounted in a horizontal position. The net-positive-suction
head (NPSH) for the system is delivered via a booster pump fed
from the under-floor tank and manually controlled via a pressure
control valve. The arrangement is shown in Figure 8.
For this work six different configurations of the axial-flow pump
were assembled and tested at the recommended speed of 1465
rpm as per the OEM pump-curves, and the configurations’
performances are compared. The six configurations are shown in
Table 2.
Figure 2. Five-vane-impeller 2D streamlines of new diffuser and tail-
piece addition
Figure 3. Total pressure on sections through the new diffuser for five
vane impeller. Dimensions 0 mm to 700 mm indicate the distance
downstream from the diffuser’s inlet face.
Figure 4. Total pressure on sections through the combined new-diffuser
and tail-piece for five vane impeller. Dimensions 0 mm to 600 mm
indicate the distance downstream from the diffuser’s inlet face.
3. Page 3 of 4
The pump-test curves for different configurations using the 5-
vane impeller are shown in Figure 9. Test results at peak
efficiency for the different configurations using the five-vane
impeller are shown in Table 3. The table compares results from
the base configuration (with standard stator-conical-diffuse
arrangement), configuration with new-diffuser only, and
configuration wherein both the new diffuser and the tail-piece are
used. Figure 9 and Table 3 show that the new-diffuser
configuration underperforms when compared to the base
configuration with a drop in head of 9.2% but an increase in flow
of 3.8%. With the tail-piece addition, efficiency and pump-head
curves were slightly reduced compared to the new-diffuser only;
however the stall line of the pump was improved (Figure 9).
Also, pump head with new-diffuser plus tail-piece addition is still
lower than the base test’s. The poor performance with the 5-vane
impeller is believed to be due to the mismatch of angles
mentioned above (Table 1)
On the other hand, testing using the eight-vane impeller gave
promising results. Comparison of pump-test curves is shown in
Figure10. Results at peak efficiency for the different
configurations are shown in Table 4. Compared with the base-
test’s (with standard stator and conical diffuser), results of new-
diffuser-only configuration show a slight increase in peak
efficiency (Table 4) but also a reduction in the pump-head curve
(Figure 10). On the other hand, with the tail-piece addition to the
new diffuser, the pump-head curve is relatively the same as the
base-test’s (Figure 10), but peak efficiency is clearly increased by
about 3.9%. The pump stall line remains about the same.
Figure 5. Total pressure on sections through the new diffuser for eight-
vane impeller. Dimensions 0 mm to 600 mm indicate the distance
downstream from the diffuser’s inlet face.
Conclusion
With the 5-vane impeller for medium-flow applications, the new-
diffuser configuration underperforms when compared with the
standard pump having separate stator and conical diffuser, even
with a tail-piece installed. Even though there is an improvement
in the pumps operating limit to the new diffuser when the tail
piece is added, the original pump is still the best performer. Main
reason for the performance degradation is attributed to the
mismatch of the new diffuser’s vane angles.
However, with the 8-vane impeller for high-flow applications the
new diffuser’s vane-angles match the impeller’s. The
combination of new diffuser and a tail piece then greatly
improves the pump’s performance, with efficiency increased by
3.9%.
Figure 6. Total pressure on sections through the combined new-diffuser
and tail-piece for eight vane impeller. Dimensions 0 mm to 600 mm
indicate the distance downstream from the diffuser’s inlet face.
Figure 7. 3D model and installation of printed tail piece. New-diffuser
(red) length is 457 mm, total tail-piece’s 600 mm. Flow direction is from
left to right.
Figure 8. Pump test-rig arrangement (loop) viewed from above; flow
direction counter-clockwise. Loop length 9400 mm, width 3000 mm
(between pipe centre-lines); pipe’s inside diameter 410 mm..
Future Work
Some work which could not be accomplished during this
research would be recommended to further enhance the findings.
The purchase of new pump components, specifically an eight-
vane impeller and a new medium-flow stator. The existing items
are worn and have poor surface finishes adding mechanical
losses to the pump.
4. Page 4 of 4
Laboratory testing using the six-vane impeller. Separate testing
with a medium flow and a high flow stator would be beneficial as
the six-vane impeller crosses over from the medium to high flow
range.
Pump efficiencies of the various configurations using CFD.
Unfortunately it was deemed too time consuming to obtain full
CFD analysis for this research.
An improved diffuser design for the five-vane-impeller assembly,
especially to address the vane-angle-mismatch issue.
Pump Test Configuration
Test
number
Impeller
vanes
Pump configuration
1.04 5 Type standard stator + standard diffuser
2.02 8 Type standard stator + standard diffuser
3.02 5 New diffuser design
4.03 8 New diffuser design
5.02 5 New diffuser design + tail piece
6.01 8 New diffuser design + tail piece
Table 2. Pump test configurations
Figure 9. Pump curves for 5-vane impeller. Test numbers 1.04, 3.02 and
5.02 are explained in Table 2.
Test
Number
Results
Head Flow Efficiency
H (m) ΔH
Q
L/s
ΔQ Η Δη
Base (1.04) 9.80 - 284 - 85% -
New Diff.
(3.02)
8.90 -9.2% 295 +3.8% 77.5% -8.8%
Tail Piece
(5.02)
9.30 -5.2% 280 -1.5% 76.5% -10%
Table 3. Five-vane-impeller pump-test comparison to base test. Test
numbers are explained in Table 2. Data are at peak efficiency.
Figure 10. Pump curves for 8-vane impeller. Test numbers 2.02, 4.03 and
6.01 are explained in Table 2.
Test
Number
Results
Head Flow Efficiency
H (m) ΔH Q L/s ΔQ Η Δη
Base (2.02) 10.70 - 475 - 74% -
New Diff.
(4.03)
11.30 +5.4% 445 -6.3% 75% +1.4%
Tail Piece
(6.01)
11.35 +5.8% 460 -3.2% 77% +3.9%
Table 4. Eight-vane-impeller pump-test comparison to base test. Test
numbers are explained in Table 2. Data are at peak efficiency.
Acknowledgements
Florin Voicu (Industrial Engineer, Weir Minerals), Dr. Luis
Moscoso (Principal Engineer, Weir Minerals), Tony Nelson
(Engineer), Nick Goodall (Regional Manager, LEAP Australia),
Peter Tawadros (Mechanical Lab Manager, UTS) and Peter
Brown (Senior Engineer, UTS).
References
[1] Czlonka, A., Nelson, T., Dibbs, R., Huynh, P., Performance
of a New Stator-Diffuser Design for an Axial-Flow-Pump
Unit, in Proc. 17th Australasia Fluid Mechanics
Conference, Auckland, New Zealand, 2010.
[2] Stepanoff, A., Centrifugal and Axial Flow Pumps: Theory,
Design and Application, 2nd ed., New York, John Wiley &
Sons, 1957.
[3] ANSYS Inc., Innovative Turbulence Modeling: SST Model
in ANSYS CFX, Canonsburg, PA, ANSYS, 2014.