axial load distribution in a jet engine spline coupling justin mcgrath master of engineering project...
TRANSCRIPT
Axial Load Distribution in a Jet Engine Spline
Coupling
Justin McGrath
Master of Engineering Project
Rensselaer Polytechnic Institute
Hartford, CT
Spline Coupling Background
Elongated gear teeth Used in high torque applications Used in jet engines to transfer
torque from disks to shafts The pressure faces of the teeth
distribute the load
Spline Coupling Schematic
Spline Couplings used in several Pratt & Whitney Engines:
•F-119
•F-135
•PW4000
•PW2000
•PW6000
Challenges in Spline Design
Even distribution of the torque load on the pressure face of the spline teeth
Uneven loading causes premature wear and reduces the life of the coupling system
Designers must understand the load behavior of the coupling system to make changes that will even the load
This project looks into analyzing axial load distribution in a representative spline coupling
Theoretical Methodology
Derived equation of axial load distribution using Tatur’s method:
cRNe
e
eee
e
exp x
L
LLx
L
L 1
11
1)(
2
2
2
p(x) – axial load at the root fillet radius
L – Contact length of the coupling system
c – effective tooth height
R – pitch radius
N – Number of teeth
T – tau, the applied torque
α – constant of integration
Finite Element Methodology
Create 3D model of the coupling system:
Import Geometry into ANSYS & apply loads:
Finite Element Methodology
Load data is extracted from the finite element model and compared to the theoretical equation:
Results
Both methods show the load peaking at either end of the contact length
The theoretical solution predicts a higher maximum load
Axial Load Distribution in Spline Coupling
0
20000
40000
60000
80000
100000
120000
0 0.05 0.1 0.15 0.2 0.25 0.3 0.35
Spline Tooth Contact Length (in.)
Co
nta
ct
Lo
ad
(p
si)
Analytical Sol.
Finite Element Sol. Left
Finite Element Sol. Right
Discussion The theoretical solution predicts higher loads because:
Tatur’s Method assumes 100 % transfer of load with no deflection
FE model shows only about 75% of the load is transferred The other 25% is used in bending the teeth, and torsionally
deflecting the coupling system
Discussion
Both methods converge when looking at a normalized plot
Normalized Axial Load Distribution
0
0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
1.8
0 0.05 0.1 0.15 0.2 0.25 0.3 0.35
Spline Tooth Contact Length (in.)
p(x
)/p
(avg
)
Analytical Sol.
Finite Element Sol. Left
Finite Element Sol. Right
This confirms that the boundary conditions used in the FE model agree with the theoretical boundary conditions
Conclusion
The theoretical equation is the more conservative method in analyzing axial load distribution in a spline coupling system as it predicts higher maximum & average loads
The theoretical equation is also a much faster method
The Finite Element solution more accurately predicts the load that will be seen during engine operation, but it is a time consuming apporach
The Finite Element model shows that all else being equal there is more capability in the coupling system when compared to the theorecitcal approach
Back Up Slides
Parameter Value Unit
α 10.67 (lb/in-rad)1/2
A 13.67 -
B 336.3 -
p(x)max 97.66 ksi
pavg 57.61 ksi
PR 1.70 -
Parameter Left Tooth Right Tooth Unit
p(x)max 71.13 68.51 ksi
pavg 47.06 45.34 ksi
PR 1.51 1.51 -
d(x)max 0.00015 0.00015 in
davg 0.0014 0.00014 in
DR 1.1 1.1 -
Analytical Calculations Finite Element Calculations
Back Up Slides
Table 1 – Material Properties of 3D Spline Coupling Model
Specification Symbol Sleeve Shaft Unit
Material - IN-100 INCO718 -
Density p 0.284 0.297 lb/in3
Weight w 0.118 0.173 lb
Modulus of Elasticity E 30.1 31.0 Gpa
Shear Modulus G 11.94 11.10 Gpa
Polar Moment of Inertia J 0.085 0.037 in4
Back Up Slides
Table 2 – Geometric Properties of 3D Spline Coupling Model
Specification Symbol Value Unit
Applied Torque τ 350 in-lb
Contact Length L 0.30 in
Pitch Radius R 0.70 in
Number of Teeth N 56 #
Tooth Height c 0.032 in
Root Fillet Radius r 0.010 in
Pressure Angle θ 30 deg
Torsional Stiffness Cθ 3332488 lb/in-rad