Upload
vulien
View
221
Download
0
Embed Size (px)
Citation preview
SSRG International Journal of Mechanical Engineering (SSRG-IJME) – volume 2 Issue 9 – September 2015
ISSN: 2348 – 8360 www.internationaljournalssrg.org Page 52
Design and analysis of Gear Shaft SingiReddy Ravinder
#1, Ramesh Banothu
*2
#1 M.Tech student, Mechanical, Vathsalya Institute of Science and Technology, Nalgonda Dist, Telangana, India *2 HoD, Mechanical, Vathsalya Institute of Science and Technology, Nalgonda Dist, Telangana, India
Abstract.A reduction gear box is part of a mechanical
system of gears and shafts used to reduce the rotational
speed of the input shaft to a slower rotational speed of the
output shaft. This reduction in output speed helps to
increase the torque of a system. Reduction gears are widely
used in power transmission devices to reduce the high
rotational speeds. Gears have wide variety of applications.
Gears are the most important component in power
transmission system. The gears generally fail when tooth
stress exceed the safe limit. It is essential to determine the
maximum stress that a gear tooth is subjected to, under a
specified loading. To prevent from failure Analysis is
carried on gears. In this study, visualize the forces, torques,
and bending moments that are created in the shaft during
operation. In the process of transmitting power at a given
rotational speed, the shaft is inherently subjected to a
torsional moment, or torque. Thus, torsional shear stress is
developed in the shaft. Finite element analysis was
performed to obtain the variation of the stress magnitude at
critical locations. Three dimensional model of the gear
shaft was created in Pro-E software. The load was then
applied to the FE model and boundary conditions were
applied as per the mounting conditions of the engine in the
ANSYS. .Also, a shaft usually carries power-transmitting
components, such as gears, belt sheaves, or chain
sprockets, which exert forces on the shaft in the transverse
direction (perpendicular to its axis). These transverse
forces cause bending moments to be developed in the shaft,
requiring analysis of the stress due to bending. In fact, most
shafts must be analysed for combined stress.
Keywords-:Gear shaft, Torque, Stress, Power-
transmission, Ansys, Pro-E
I. INTRODUCTION
Gear box is a speed and torque changing device
between the engine and the driving wheels. It serves
the following purposes in transmission system of an
automobile
1. It exchanges engine power for greater torque and
thus provides a mechanical advantage to drive the
vehicle at different conditions.
2. It exchanges forward motion for reverse motion.
3. It provides a neutral position to disallow power
flow to the rest of the power train.
Automobile requires high torque when climbing hills
and when starting, even though they are performed at
low speeds. On the other hand , when running at high
speeds at level roads, high torque is not required
because of momentum and it would be preferable to
have just the wheels alone turning at high speeds.
The gear box also called the transmission acts in
accordance with the running conditions. When
driving power is required, it reduces the engine speed
and transmits stronger torque to the wheels. In
addition the transmission serves to reverse the
vehicle. Since the engine can turn only in one
direction, the transmission gear can mesh in such a
manner to allow running the vehicle in reverse
direction.
Located at the junction point of a power shaft, the
gearbox is often used to create a right angle change in
direction, as is seen in a rotary mower or a helicopter.
Each unit is manufactured with a specific purpose in
mind and the gear ratio used is designed to provide
the level of force required. This ratio is fixed and
cannot be changed once the box is constructed. The
only possible modification after the fact is an
adjustment that allows the shaft speed to increase,
along with a corresponding reduction in torque.In a
situation where multiple gear speeds are needed, a
transmission with multiple gears can be used to
increase torque while slowing down the output speed.
This design is commonly found in automobile
transmissions. The gear transmission mechanism is
one of themost widely used transmission mechanism,
which canbe used to transmit the motion and force
between tworandom shafts in space of transmission,
characterizinglarge power range, high efficiency,
accuratetransmission ratio, long service life, safe and
reliable,has been widely used in various industries
(Wang et al.,2010). In which, gear shaft is the main
transmissionpart in the most general machinery and
its intensity hasa great influence on the service life of
the machine.Because the geometric structure of gear
shaft is morecomplex than the ordinary transmission
shaft, todetermine and check the actual damage
location of gearshaft by the conventional method is
SSRG International Journal of Mechanical Engineering (SSRG-IJME) – volume 2 Issue 9 – September 2015
ISSN: 2348 – 8360 www.internationaljournalssrg.org Page 53
more cumbersome,it results in a bigger error (Li et
al., 2000). In order toprovide the theoretical basis for
structural design ofgear shaft, especially for new
structural measures takenfor the dangerous position
in time, the strength of gearshaft should be clearly
understood after the preliminarystructural design is
completed. Based on the abovesituation, this paper
uses the transmission systemanalysis software
MASTA to complete the strengthanalysis and
calculation for gear shaft of a certainautomobile
transmission.
II. THEORETICAL SHAFT DESIGN AND
ANALYSIS
A shaft is the component of a mechanical device that
transmits rotational motion and power. It is integral
to any mechanical system in which power is
transmitted from a prime mover, such as an electric
motor or an engine, to other rotating parts of the
system. There are many examples of mechanical
systems incorporating rotating elements that transmit
power: gear-type speed reducers, belt or chain drives,
conveyors, pumps, fans, agitators, household
appliances, lawn maintenance equipment, and parts
of a car, power tools, machines around an office or
workplace and many types of automation equipment.
Visualize the forces, torques, and bending moments
that are created in the shaft during operation. In the
process of transmitting power at a given rotational
speed, the shaft is inherently subjected to a torsional
moment, or torque. Thus, torsional shear stress is
developed in the shaft. Also, a shaft usually carries
power-transmitting components, such as gears, belt
sheaves, or chain sprockets, which exert forces on the
shaft in the transverse direction (perpendicular to its
axis). These transverse forces cause bending
moments to be developed in the shaft, requiring
analysis of the stress due to bending. In fact, most
shafts must be analysed for combined stress.
Because of the simultaneous occurrence of
torsional shear stresses and normal stresses due to
bending, the stress analysis of a shaft virtually always
involves the use of a combined stress approach. The
recommended approach for shaft design and analysis
is the distortion energy theory of failure. Vertical
shear stresses and direct normal stresses due to axial
loads also occur at times, but they typically have such
a small effect that they can be neglected. On very
short shafts or on portions of shafts where no bending
or torsion occurs, such stresses may be dominant.
A. Procedure for Design and analysis of a Shaft
1. Determine the rotational speed of the shaft, n
(rpm).
2. Select the material from which the shaft will be
made, and specify ultimate tensile strength Su,
yield strength Syand its surface condition:
ground, machined, hot-rolled and as-forged. At
the moment, due to lack of database for
endurance strength, this module should be used
in the design and analysis of steel shafts only.
Use the database in selection of a material.
3. Apply a desired reliability for definition of
reliability factor, CR.
4. Apply a design factor, N (we prefer to use ηd).
5. Propose the general form of the geometry for the
shaft, considering how each element on the shaft
will be held in position axially and how power
transmission from each element to the shaft is to
take place. Design details such as fillet radii,
shoulder heights, and key-seat dimensions must
also be specified. Sometimes the size and the
tolerance for a shaft diameter are dictated by the
element to be mounted there. For example, ball
bearing manufacturers' catalogs give
recommended limits for bearing seat diameters
on shafts.
6. Specify the location of bearings to support the
shaft. The reactions on bearings supporting radial
loads are assumed to act at the midpoint of the
bearings. Another important concept is that
normally two and only two bearings are used to
support a shaft. They should be placed on either
side of the power-transmitting elements if
SSRG International Journal of Mechanical Engineering (SSRG-IJME) – volume 2 Issue 9 – September 2015
ISSN: 2348 – 8360 www.internationaljournalssrg.org Page 54
possible to provide stable support for the shaft
and to produce reasonably well-balanced loading
of the bearings. The bearings should be placed
close to the power-transmitting elements to
minimize bending moments. Also, the overall
length of the shaft should be kept small to keep
deflections at reasonable levels.
7. Determine the design of the power-transmitting
components or other devices that will be
mounted on the shaft, and specify the required
location of each device.
8. Determine the power to be transmitted by the
shaft.
9. Determine the magnitude of torque at point of the
shaft where the power-transmitting element is.
T = 30 H/π n [N-m]
where:
H = transmitted power, W
T = torque, N-m.
n = rotational speed, rpm.
10. Determine the forces exerted on the shaft.
Spur and helical gears, tangential force
Wt = 60 000 H / π d n
[N]
where: d = pitch diameter of gear in [mm];
H = Power in [W];
N = Rotational Speed in [rev/min]
Radial force ; Wr = Wt. tan φn / cos ψ [N]
where: = normal pressure angle for helical
gears, and pressure angle for spur gears; and
ψ = helix angle
11. Preparing a torque diagram.
12. Resolve the radial forces into components in
perpendicular directions, vertically and
horizontally.
13. Solve for the reactions on all support bearings in
each plane.
14. Produce the complete shearing force and bending
moment diagrams to determine the distribution of
bending moments in the shaft.
15. Analyze each critical point of the shaft to
determine the minimum acceptable diameter of
the shaft at that point in order to ensure safety
under the loading at that point. In general, the
critical points are several and include those
where a change of diameter takes place, where
higher values of torque and bending moment
occur, and where stress concentrations occur.
If a vertical shearing force V is the only significant
loading present, this equation should be used to
compute the required diameter for a shaft.
where:
Kt = stress concentration factor at the shoulder;
1.5 to 2.5;
V = Vertical Shear Force [N];
N = Factor of Safety / Design Factor
(you may use ηd);
D or d = Diameter of the Shaft at the
section considered [mm];
S’n = modified endurance strength [MPa],
(Which depends on ultimate tensile strength Su).
where:
Cs = size factor;
CR = reliability factor;
Sn = endurance strength [MPa]
In most shafts, the resulting diameter will be much
smaller than that required at other parts of the shaft
where significant values of torque and bending
moment occur. Also, practical considerations may
require that the shaft be somewhat larger than the
computed minimum to accommodate a reasonable
bearing at the place where the shearing force V is
equal to the radial load on the bearing.
Most shafts are subjected to bending and torsion. The
power being transmitted causes the torsion, and the
transverse and radial forces on the elements cause
n
'
.
n
t
S
NVKD
942
RSnn CCSS '
SSRG International Journal of Mechanical Engineering (SSRG-IJME) – volume 2 Issue 9 – September 2015
ISSN: 2348 – 8360 www.internationaljournalssrg.org Page 55
bending. In the general case, the transverse forces do
not all act in the same plane. In such cases, the
bending moment diagrams for two perpendicular
planes are prepared first. Then the resultant bending
moment at each point of interest is determined.
A design equation is now developed based on the
assumption that the bending stress in the shaft is
repeated and reversed as the shaft rotates, but that the
torsional shear stress is nearly uniform.
Where:
M = Bending moment (a resultant obtained
from bending moment diagrams; (this creates
reversed bending stresses on the shaft) [N-mm];
T = Torsion or twisting moment (usually
steady) [N-mm];
N = Factor of safety; (We shall usually use η.)
D = Diameter of the shaft at the section under
investigation; in [mm].
Also, Sy and Sn are to be taken as [MPa]
III. DESIGNING OF GEAR SHAFT
A. Shaft Design
A shaft is the component of a mechanical device
that transmits rotational motion and power. It is
integral to any mechanical system in which power
is transmitted from a prime mover, such as an
electric motor or an engine, to other rotating parts
of the system. There are many examples of
mechanical systems incorporating rotating
elements that transmit power: gear-type speed
reducers, belt or chain drives, conveyors, pumps,
fans, agitators, household appliances, lawn
maintenance equipment, and parts of a car, power
tools, machines around an office or workplace
and many types of automation equipment.
Preprocessor
• Member length.
• Member position.
• Member material.
• Element type -- SOLID 8 NODE 185
• Material model -- AL ALLOY
• Real constants -- NONE
• Meshing -- TETRA FREE
• Loads -- MODAL LOADS
Solution
• Load position.
• Load magnitude.
• Load direction.
• SOLUTION --- Solve - current L.S (Solves
the problem)
Post-processor
• Get displacement member force detain both
graphical and text output.
•Plot results – contour plot -- nodal solution
IV. RESULTS OF ANSYS MODEL
3
1
22
4
332
yn
t
S
T
S
MKND
'
SSRG International Journal of Mechanical Engineering (SSRG-IJME) – volume 2 Issue 9 – September 2015
ISSN: 2348 – 8360 www.internationaljournalssrg.org Page 56
INPUT GEAR SHAFT ANSYS MODEL
MESHED MODEL
SHAFT NODAL SOLUTIONS
MAXIMUM ABSOLUTE VALUES
NODE 7061 8212 930
VALUE 0.31897
E-04
0.14851E-
05
0.15517E-
03
SHAFT STRESS INTENSITY
MINIMUM VALUES
NODE 1542 1542 1542
VALUE 0.12954
E+06-0
0.16107E+
06
0.44095E+
06
VON MISES STRESS
V. CONCLUSIONS
.The model that is created in Pro/Engineer wildfire
5.0 and analysed in Ansys V12.1. The model created
in Pro/Engineer is transferred to Ansys through IGES
(Initial Graphics Exchange Specification) format.
The structural analysis has been performed on the
model by applying the proposed material properties,
boundary conditions and loads. By viewing the
results that has been discussed in the early chapter, it
can be said that the input gear shaft model can
SSRG International Journal of Mechanical Engineering (SSRG-IJME) – volume 2 Issue 9 – September 2015
ISSN: 2348 – 8360 www.internationaljournalssrg.org Page 57
withstand the proposed loads with considering a
factor of safety as 1.2. So, thereafter the designed
model can be manufactured or fabricated with
extensive testing.
References
1. Design of machine elements – v.m faires
2. Machine design –schaum series
3. Machine design –Pandya& shah
4. Design data book-psg
5. Mech engg design – j.e shigley
6. Automotive mechanics – kripal singh
BIODATA
AUTHOR1
SingiReddy Ravinder has received the
B.Tech (MechanicalEngineering) Degree
fromAVN institute of Science and
Technology, Rangareddy and
pursuingM.Tech (Machine Design) in
VIST, Bhoingiri, Nalgonda, Telangana, India.
AUTHOR2
Ramesh Banothu has 5 years experience
in teaching in
graduate and post graduate level and he
presently working as Associate Professor
and HOD of Mechanical Department in
VIST, Bhoingiri, Nalgonda, Telangana,
India.