Design and Development of Transonic Axial Flow Compressor Rotor Blade

International Journal of Engineering Research and Development
e-ISSN: 2278-067X, p-ISSN: 2278-800X, www.ijerd.com
Volume 13, Issue 4 (April 2017), PP.22-26
22
Design and Development of Transonic Axial Flow Compressor
Rotor Blade
K Balaji1
, S Emilon Zeon Rajan2
, C Ganesan3,
M Jananee4
, S Sanjay Kumar5
1
Assistant Professor, 2,3,4,5
Students
Department of Aeronautical Engineering Karpagam Institute of Technology, Coimbatore.
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.
Keywords: Compressor rotor blade, Numerical investigation, Flow separation, Vortex generators, Stall
margin, Efficiency.
I. INTRODUCTION
Rotating blades are usually attached with hub of the compressor. The blades are tilled with a correct
series with coincidence. This shape is full fill in NASA 0037. Tip span are usually aligned and attached in
starting from rotating stall. A jet engine of high pressure compressor to investigation the effect of inlet total
pressure distortions on rotating stall. It will be occurred in spike type stall. A low momentum area near rotor tip
leading edge causes the flow spillage and leads to stall inception. Turbo machinery and transonic axial flow
compressors have played important role to attain higher pressure ratio at every single stage of compressor. A
high level of aerodynamic performance must be maintained over a wide range of mass flow rate and speed. The
successful operation and reliability of the axial flow compressor is greatly affected by its stability margin. In a
compressor specific speed there is a limit for both higher and lower mass flow which is called its operating
range, the operating range is between the chock limit and stall point. Stall margin of the compressor can be
increased by using various passive and active control techniques.
II. LITERATURE REVIEW
[1] KAMARUL A.A predicted the reduction of flow separation over blade surface can improve better
aerodynamic performance. The design cases studied comprised of compressor operation at 80%, 90%, 105% on
design rotational speed. 3D flow visualization and performance parameters were detailed to study the relative
blade, Mach number distribution created by the model.
[2] AVINASH KUMAR. Found the boundary layer separation and tip leakage flow between wall and
the blade in axial flow compressor. The modeling effect is investigated to vortex generators in transonic axial
flow in compressor stage. The rotor blade performing to energizing the low momentum boundary layer and
controlling the stall. The profile will generate the vortex will be retrofitted.
[3] JIAYE GAN tested jet engine high pressure compressor rotor to investigate the effect of inlet total
pressure distortion on rotating stall which usually starts from tip span.
III. METHODOLOGY
In this work to study the influence of different profiles on airflow in compressor rotor blade using
CATIA and ANSYS fluent for strength following procedure is adopted 1) Modeling and Mesh generation.2)
Flow analysis.
3.1Modeling and Extraction of flow domain
The data points for the rotor model and the computational domain were collected. The 3D model of the
rotor blades are designed by using CATIA. Figure 1 show the circular jets are decided to place on the 3D model
of the rotor blade. Figure 2 shows the 3D model of the rotor blade along with the flow domain in the entire
compressor. The values for the generated mesh near the wall zones are maintained at too which is as per the
turbulence modeling requirements. A single passage approach is modeled and numerically solved with the
assumption that flow is periodic within the passage.
3.2Mesh Generation

Design And Development Of Transonic Axial Flow Compressor Rotor Blade
23
Meshing of the computational domain is made using CFD as shown in Figure 3.Thus, the discretisation
of the Hybrid structured grid elements were generated.
Figure1. Rotor Blade with Circular Jet Enclosure Figure 2. Wheel Rotor Assembly
Figure 3. Mesh Rotor Blade
III. FLOW ANALYSIS
The flow analyses were carried out using a commercial CFD package. The flow fluid was assumed to
be an ideal gas, Shear Stress Transport (SST) turbulence model was equipped for the present study. To conform
that results are independent of the mesh, grid independency studies were carried out and total 1,800,000 cells
were created in the final flow domain. The wall boundaries of the blade, rotor and stator, hub and casing are
specified with no slip condition. It indicates that the fluid sticks to the wall and moves with the same velocity as
the wall. The design speed of the rotor (1800 rad/s).The total pressure and total temperature were imposed at the
inlet (p inlet = 101330 pa, T inlet = 298 k) to recreate the experimental boundary conditions .As an outlet condition,
To find the Design mass flow and chocked mass flow conditions at on design speed. Figure 4.shows the
boundary conditions applied to the flow domain.
Figure 4. Boundary Conditions Applied to the Flow Domain
IV. RESULTS AND DISCUSSION

24
The comparative performance of the baseline compressor and injection compressor at on- design speed
and off-design speed. It is monitored that among the off/on design conditions, the flow follows the consistent
patterns and the highest efficiency, stall margin of the compressor stage is improved by the compressor design
speed. The flow physics of the compressor rotor for different design conditions were studied using velocity
vectors, Mach number contours and velocity streamlines as mentioned below.
Mach number
Figure 5 shows the comparative Mach number contours computed along the on/off design speed
conditions. Concerning the calculated flow field, the plots were computed at span blade to blade Mach number.
It is observed that a strong shock front was created and flow separation was combined along the flow at the
suction side of the rotor blade at design speed. While in the formation of shock and flow separation region was
much weaker compared to previous flows.
In design speed, the flow was much smoother and flow separation was almost unnoticed. The reduction
in shock strength is seen to directly affected the pressure ratio reduction .which disturbs the efficiency of the
compressor rotor blade. It also indicates that the blade boundary layer and its interaction have been properly
captured.
Figure 5. Comparative Mach Number Contours at Various Design Conditions
Velocity
Figure 6 displays the comparative velocity vector plots for peak efficiency condition at baseline rotor’s
on/off design compressor speed. Vector plots are plotted at the span of blade to blade view for the velocity
distribution over the operating conditions. As shown in the contour, high velocity is observed at the inlet
condition which produces shock front where it gets reduced from the blade surface at trailing edge because of
the flow separation. Though there is a difficulty to produce the well-defined tip clearance vortex pattern, its
shock interaction with the flow is captured reasonably well.
(a) (b)
Figure 6. Comparative Velocity Contours at Various Design Conditions
Streamline

25
Figure 7 shows the comparative detailed streamline patterns in suction side of the rotor for various
design speed at maximum efficiency condition. The streamlines discharged from the leading edge and the
separation lines are created at the suction side boundary. The 3D streamline patterns indicate fairly well the
internal flow conditions created at suction of the rotor span. Forms of flow disruption were created because of
the shock and the flow separation near the trailing edge which were also captured in the blade to blade Mach
number contour as seen in Figure 5. Also for the off-design condition at maximum efficiency state, clearly
reveals that there is less flow separation created compared with the design speed.
(a) (b)
Figure 7. Comparative Streamlines on the Maximum Efficiency Rotor State at Various Design Conditions
V CONCLUSION
A computational flow steady analysis for a transonic axial flow compressor rotor at on-design speed
(1800 rad/s) and various design conditions was carried out. The flow pattern analysis for the Mach number
distribution, streamline patterns and Velocity Vector Contours to provide a detailed conclusion. The purpose of
this paper was to study the flow and performance parameters for better understanding over the design
condition.It was found that the efficiency of the rotor has a direct impact from the shock front created. Thus,
there is a reduction in efficiency due to the poorly produced shock front in design speed along with a big
pressure ratio difference. Even though the velocity condition at design speed looks better than on-design speed
(1800 rad/s), due to unstable flow condition along various mass flow rate, reduced efficiency was noted which
negatively impacts the efficiency.
ACKNOWLEDGMENT
With great pleasure and deep gratitude, authors wish and express their sincere gratitude to beloved
Principal Dr. T. Ramachandran for providing an opportunity and necessary facilities in carrying out this work
and express sincere thanks to all the staff members of Aeronautical Engineering whose assistance played a big
role in this work and have been of immense value.
REFERENCES
[1] Moore Royce, D., & Reid, L. (1982). Performance of Single stage Axial Transonic Compressor with
rotor and stator), aspect ratios of 1.19 and 1.26 respectively and with design pressure ratio of 1.82.
NASA Technical Paper, (November 1978), 105. ]
[2] Chen, G. T., Greitzer, E. M., Tan, C. S., & Marble, F. E. (1991). Similarity Analysis of Compressor
Tip Clearance Flow Structure. Journal of Turbo machinery, 113(2), 260.
[3] Freeman, C., & A., C. N. (1992). Method for the prediction of supersonic compressor blade
performance. Journal of Propulsion and Power, 8(1), 199–208.
[4] Law, C. H., & Wadia, A. R. (1993). Low Aspect Ratio Transonic Rotors: Part 1—Baseline Design and
performance. Journal of Turbo machinery, 115(2), 218–225.
[5] Suder, K. L., Chima, R. V., Strazisar, a. J., & Roberts, W. B. (1995). The Effect of Adding Roughness
and Thickness to a Transonic Axial Compressor Rotor. Journal of Turbomachinery,117(4), 491.
[6] Suder,K.L.(1997).Blockage Development in a Transonic, Axial Compressor Rotor.

26
[7] Calvert,W. J., Emmerson,P. R., & Moore, J. M. (2003).Design, Test and Analysis of a High-Pressure-
Ratio Transonic Fan. In Volume 6: Turbo Expo 2003, Parts A and B (pp. 417–427). ASME. http://
doi.org/10.1115/GT2003-38302.
[8] Benini,E.,Biollo,R, & Ponza, R. (2011).Efficiency enhancement in transonic compressor rotor blades
using synthetic Jets: A numerical investigation. Applied Energy, 88(3), 953–962.
[9] Biollo,R, & Benini, E. (2013). Recent advances in transonic axial compressor aerodynamics. Progress
in Aerospace Sciences, 56, 1–18. http://doi.org/10.1016/j.paerosci.2012.05.002.

Design and Development of Transonic Axial Flow Compressor Rotor Blade

More Related Content

What's hot (16)

Similar to Design and Development of Transonic Axial Flow Compressor Rotor Blade (20)

More from IJERDJOURNAL (20)

Recently uploaded (20)

Design and Development of Transonic Axial Flow Compressor Rotor Blade