Design of transonic axial compressor
Transcript of Design of transonic axial compressor
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Design of Transonic Axial Compressor
Sai Kiran Goud.M
Transonic axial flow compressors are today widely used in aircraft
engines to obtain maximum pressure ratios per single-stage.
. High stage pressure ratios are important because they make it
possible to reduce the engine weight and size and, therefore,
investment and operational costs.
Performance of transonic compressors has today reached a high
level but engine manufacturers are oriented towards increasing it
further.
Another important target is the improvement of rotor stability
towards near stall conditions, resulting in a wider working range.
Today’s high efficiency transonic axial flow compressors give a total
pressure ratio in the order of 1.7-1.8.
Introduction
Based on multistage axial flow compressor of the M7A-O2 gas
turbine establishes a higher pressure ratio and a large amount of
air flow than the M7A-O1.
By adopting transonic stages with the characteristics of high
pressure ratio, the air flow rate and pressure ratio are increased.
A preliminary design for a nine-stage axial flow compressor was
produced from an initial specification. This design is presented
here, and is criticized. Alterations are then made to the design to
compensate for its deficiencies.
Problem Definition
By considering the initial required conditions for the design of axial compressor the following parameters are designed.
All the blade angles at mean for both rotor and stator of the compressor
Total pressure ratio of each stage and the complete compressor.
Total shaft power.
Assuming every stage has the same mean radius with rotor blade angle changing by ‘12 degree’
Number of stages n 9
Rotating Speed N 9000rpm
Ambient pressure P01 15.7Psia
Ambient temperature T01 519R
Mean axial velocity Va 520ft/s
Radius of the rotor at tip rt 12inches
Radius of the rotor at hub rh 8inches
Change in rotor blade angle per
stage
β1 – β2 12degree
Design Specifications
Initial design specification
Calculate the mean radius rm= rt+ rh/2 = 10. Therefore, hub/tip ratio = 0.83ft.
Calculate the blade velocity ‘Um’ at the mean, by using the formula
Um= 2π.N.rm / 60 = 781.86ft/s Calculate the inlet blade angle β1 ,
Tan β1 = U / V1 = 56.30 degrees As given, Change in rotor blade angle per stage, β1 –
β2= 10, calculate β2 = 46.30 degrees.
From the velocity triangle , find the value of Wu2, Tan β2 = Va / Wu2 = 496.9 ft/s
Procedure / Calculations
Velocity Triangle
In velocity triangle we can get the value of Vu2 by subtracting it from ‘U’ = 284.96ft/s
Using velocity triangle and the value of Wu2 , calculate ‘α2’ , i.e.
Tan α2 = Vu2 / Va = 28.36degree Now find stagnation enthalpy difference
by using the formula,Ϫ hos= U. Vu1 = U (U- Va tan β2) =
7.42btu/lbm
By using Cp (To2-To1) = Ϫ hos, find temperature per stage
T o2 = 539R
Pressure ratio per stage , as T o2 = T03, calculate P03/ P01,
P03/ P01 = ( T03 /T01)k/k-1 =1.145
Calculate the outlet temperature of the compressor, Toe
Cp (Toe-To1) = Ϫ hos = 703.5R
Calculate the overall pressure ratio of the compressor,
Toe / To1 = (Poe / Po1)k-1/k = 2.89
Using the above equation find out ‘Poe’. = 45.5psia
For finding the pressure rise per stage, calculate T1,
T1= T01- V12/ 2 Cp =496.51R
Now calculate P1,
P1/P01 = (T1/ T01)k/k-1 = 13.44psia
Now calculate 𝝆1, by using the equation,𝝆1= P1 / RT1 = = 0.0507
lbm/ft3
Calculate area of the rotor ,A1= π (rt
2- rh2)
=251.2ft2
Calculate the mass flow rate,M .= 𝜌1. V1. A1 = 66.57
lb/s Finally calculate the shaft power,
Ps= m..n. Ϫ hos = 4445.54hp
Inlet blade angle at mean β1 56.30degree
Outlet Blade angle at mean β2 46 degree
Blade angle at mean α2 28.36degree
Pressure ratio per stage P03 / P01 1.145
overall pressure ratio Poe / Po1 2.89
mass flow rate m' 66.57lb/s
shaft power Ps 4445.54hp
Results
Results
Hence, for a transonic axial compressor, determined the following values,
1. Blade angles at mean for both stator and rotor.
2. Total pressure ratio of each stage and the complete compressor.
3. Total shaft power.
Conclusion
Thank You