ISSN : 2319 – 3182, Volume-2, Issue-4, 2013
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Finite Element Analysis of Inertia Dynamometer
R. A. Gujar
1, S. V. Bhaskar
2 & N. U. Yewale
3
1,2&3
Department of Mechanical Engineering, 1&3
Pimpri Chinchwad College of Engineering, 2Sanjivani Rural Education Society College of Engineering
E-mail : [email protected], [email protected]
3
Abstract – The Dynamometer is a LOAD device. It applies
a load to an engine so we can test the performance of the
engine under a variety of circumstances. System operates
where load (dyno) torque equals that of the Engine. By
varying the engine throttle and load we can test any point
under the engines max torque curve. We design and
modify engines for improved fuel economy and emissions
We need DATA to quantify the improvements in Fuel
savings and Emissions reductions. This data will be used to
help us “tune in” our design.
The Dynamometer is operated at 1000 rpm to generate the
necessary inertia. For different kind of conditions, there is
need of having variable inertia. So the dynamometer is
constructed with removable flywheel.
I. INTRODUCTION
The Dynamometer is a LOAD device. It applies a
load to an engine so we can test the performance of the
engine under a variety of circumstances. System
operates where load (dyno) torque equals that of the
Engine. By varying the engine throttle and load we can
test any point under the engines max torque curve. We
design and modify engines for improved fuel economy
and emissions. We need DATA to quantify the
improvements in Fuel savings and Emissions reductions.
This data will be used to help us “tune in” our design.
The Dynamometer is operated at 1000 rpm to
generate the necessary inertia. For different kind of
conditions, there is need of having variable inertia. So
the dynamometer is constructed with removable
flywheel
II. STATIC ANALYSIS
A. ANALYSIS OF SHAFT
Material Properties for shaft : Steel : FE 410 WA :
IS 2062
Table I : Material Properties for Shaft
Physical Properties Values
Ultimate Strength 410 Mpa (N/mm2)
Yield Strength 230 Mpa (N/mm2)
Young‟s Modulus (E) 2.1x105 N/mm
2
Poisson‟s Ratio (µ) 0.3
Density 7850 kg/ m3
Table II : Chemical Properties for Shaft
Grade Desig
nation
Qua
lity Ladle Analysis, % Max
(CE)
Max
Method
of
Deoxida-tion
C Mn S P Si
FE
410 W A 0.23 1.5 0.045 0.045 .40 0.42
SemiKille
d/ Killed
Table III : Mechanical Properties of Shaft
Grade Designation
Quality Syt
MPa σt
MPa
% Elongation,
A at Gauge Length, LO
5.65√S ,Min
Internal
diam.
Min.
FE 410 W A 410 230-250 23 3t
B. ANALYSIS OF SHAFT BY USING FEA
Fig.1 : CAD Geometry of Shaft
International Journal on Theoretical and Applied Research in Mechanical Engineering (IJTARME)
ISSN : 2319 – 3182, Volume-2, Issue-4, 2013
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Fig. 2 : Deformation in Shaft
Fig. 3 : Von-Mises Stresses in Shaft
Fig.4 : Max.Shear Stress in Shaft
C. STATIC ANALYSIS OF BUSH
FIG. 5 : CAD GEOMETRY OF BUSH
Fig.6 : Deformation in Bush
Fig.7 : Von-Mises Stresses in Bush
International Journal on Theoretical and Applied Research in Mechanical Engineering (IJTARME)
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D. STRUCTURAL ANALYSIS OF PEDESTAL
BEARING
Fig. 8 : CAD Geometry of Pedestal Bearing
Fig. 9 : Deformation in Pedestal Bearing
Fig. 10 : Von-Mises Stresses in Pedestal Bearing
E. STRUCTURAL ANALYSIS OF BASE FRAME
Fig.11 : CAD Geometry of Base Frame
Fig. 12 : Deformation in Base Frame
Fig.13 : Von-Mises Stresses in Base Frame
International Journal on Theoretical and Applied Research in Mechanical Engineering (IJTARME)
ISSN : 2319 – 3182, Volume-2, Issue-4, 2013
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III. MODAL ANALYSIS OF DYNAMOMETER
Operating Frequency of Dynamometer
Rotating Speed (N) = 1000 rpm.
Angular Velocity (ω) = 2πN/60
= 2 x π x 1000/60
= 104.71 rad/s
Operating Frequency = ω / 2π
= 104.71 / 2π
= 16.66 Hz
Natural Frequency of Dynamometer
The product is been solved in ANSYS to find the
Natural Frequency upto first three natural modes.
CASE I – Shaft & Fixed Flywheel
A. Model Shape – I
Natural Frequency: 47.539 Hz
Max. Amplitude: 1.1 mm
Fig.13 : Model Shape – I
B. Model Shape – II
Natural Frequency: 112.25 Hz
Max. Amplitude: 1.09 mm
Fig.14 : Model Shape – II
C. Model Shape – III
Natural Frequency: 117.14 Hz
Max. Amplitude: 1.09 mm
Fig.14 : Model Shape – III
CASE II – Shaft, Fixed Flywheel & Removable
Flywheel.
A. Model Shape – I
Natural Frequency: 36.007 Hz
Max. Amplitude: 0.51 mm
Fig.15 : Model Shape – I
International Journal on Theoretical and Applied Research in Mechanical Engineering (IJTARME)
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B. Model Shape – II
Natural Frequency: 48.711 Hz
Max. Amplitude: 1.077 mm
Fig. 16 : Model Shape – II
C. Model Shape – III
Natural Frequency: 69.494 Hz
Max. Amplitude: 0.5788 mm
Fig. 17 : Model Shape – III
D. DYNAMIC ANALYSIS OF DYNAMOMETER
(High Speed Effect)
Assumption
1. The Fixed, Removable Flywheel & Shaft is
perfectly balanced.
2. This Analysis will consider the centrifugal forces
developed due to high speed.
CASE I – Shaft & Fixed Flywheel
Fig.18 : Stress developed due to centrifugal stress
Fig.19 : Deformation in flywheel due to centrifugal stress
CASE II – Shaft, Fixed Flywheel & Removable
Flywheel.
Fig. 20 : Deformation in flywheel & Removable
Flywheel due to centrifugal stress
Fig.21 : Deformation in flywheel & Removable
Flywheel due to centrifugal stress
International Journal on Theoretical and Applied Research in Mechanical Engineering (IJTARME)
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. IV. RESULTS
XXXX
V. CONCLUSION
The result of Static Analysis for shaft, Pedestal
Bearing & Base frame confirms the safety &
overall rigidity of dynamometer assembly.
The Modal Analysis confirms the safety of product
to operate at 1000 rpm speed, as the operating
frequency doesn‟t meet to natural frequency.
The dynamic analysis confirms the strength
validation of the product. The average induced
stress is lower than the yield strength of material,
the product is safe.
VI. ACKNOWLEDGMENT
I wish to express my sincere thanks to
Prof.S.V.Bhaskar for their technical support and helpful
attitude gave us high moral support .
I am also thankful to Prof. A.G.Thakur (P.G.Co-
ordinator & HOD of Mechanical Department) who had
been a source of inspiration.
Finally, I specially wish to thank my father &
Mother, wife kirti and sweet daughter Sanskriti and all
those who gave me valuable inputs directly or
indirectly.
VII. REFERENCES
[1] Min-Soo Kim, “Vibration Analysis of Tread
Brake Block in the Brake Dynamometer for the
High Speed Train” „International Journal of
Systems Applications, Engineering &
Development‟, 2011, Volume 5, Issue 1.
[2] J. Naga Malleswara Rao, A. Chenna Kesava
Reddy & P.V. Rama Rao, “Design and
fabrication of new type of dynamometer to
measure radial component of cutting force and
experimental investigation of optimum
burnishing force in roller burnishing process”
„Indian Journal of Science and Technology‟,
2010, Vol. 3 No.7, ISSN: 0974- 6846.
[3] Min-Soo Kim, Jeong-Guk Kim, Byeong-Choon
Goo, & Nam-Po Kim, “Frequency Analysis of
the Vibration of Tread Brake Dynamometer for
the High Speed Train” „Vehicle Dynamics &
Propulsion System Research Department‟, Korea
Railroad Research Institute, ISSN: 1792-4618,
ISBN: 978-960-474-217-2.
[4] Ryan Douglas Lake, “Integration of a small
Engine Dynamometer into an eddy Current
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Controlled Chassis Dynamometer” B.S;
University of Cincinnati, 2004.
[5] Brian J. Schwarz & Mark H. Richardson,
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[6] J Michael Robichaud, P.Eng, “Reference
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[8] V.B.Bhandari, Design of Machine Element; Tata
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