DESIGN, ANALYSIS AND OPTIMIZATION OF ROLLER CHAIN LINK … · DESIGN, ANALYSIS AND OPTIMIZATION OF ROLLER CHAIN LINK FOR COAL TRANSPORTATION USING FEA Prashant S. Mulmule1, Prof

DOI:10.21884/IJMTER.2018.5028.F8ESO 185

DESIGN, ANALYSIS AND OPTIMIZATION OF ROLLER CHAIN LINK

FOR COAL TRANSPORTATION USING FEA

Prashant S. Mulmule1, Prof. T. Y. Badgujar

2 and Prof. A. D. More

3

1Department of Mechanical Engineering, Late. G. N. Sapkal College of Engineering,

2Department of Mechanical Engineering, Late. G. N. Sapkal College of Engineering,

3Department of Mechanical Engineering, Sandip Polytechnic

Abstract— Chain conveyors play crucial part in industries. Chains are put into service as pulling or

driving member. In Indian scenario roller chain conveyors are basically used to transport granular

material. Generally the environment where these chains are used is rusty, contaminated with soil,

chemicals, foreign particles etc. Due to which unexpected failure of chain link occur. Also Roller

chain is subjected to tensile force as well as impact forces. Due to tensile forces there is increase in

length of chain which makes the chain ineffectual. Present study deals with static structural analysis

of the roller chain for particular application, selection of the suitable material to enhance corrosion

resistance, weight optimization by changing certain dimensions and experimental validation of the

FEA results obtained.

Keywords— Roller chain Link, Tensile force, Static Structural analysis, Corrosion resistance, FEA,

Weight optimization.

I. INTRODUCTION

As far as the Indian scenario is considered economic growth is dependent on

industrialization. Current picture states that 63% of development of industry is dependent on efficient

use of machinery. In case of industry there is continuous requirement of transportation of material

and this requirement is fulfilled by Conveyor system, Jib crane, Pallet jack, Automatic Guided

Vehicles etc. Taking example of sugar mills there is requirement of transportation of materials like

coal, bagasse, sugar etc. These materials are in granular form and it is necessary to develop a proper

transport system which is long lasting, having less maintenance, which can sustain heavy loading and

shocks in rusty and dusty environment. Chain conveyor has the advantage of high transmission

efficiency for short distance transportation of materials over belt conveyors. Adding to it chain

conveyor has disadvantage of deformation of chain link due to tension force and jerk. Frequent

maintenance and timely lubrication is required to avoid corrosion of roller chain. Basically Solid

Bearing Roller Chain is used in sugar industry for transportation of coal. Vital components of roller

chain are outer and inner link which is also called as strip. The other important components are

roller, pin and bushing. Constructional features of roller chain shows that inner and outer links are

connected to each other by using pin which is press fitted between holes located on link plates. Press

fit constrains a rotary motion of pin. Further pin and bush are assembled together with slip fit

between them. Bushing is basically applied with bending, shock as well as shearing loads which is

transmitted by inner and outer links to it. Bushing and roller are assembled using slip fit. Roller is

subjected to impact loading when tooth of sprocket comes in contact with roller

II. LITERATURE REVIEW

2.1 Huanyu Zhao et.al.(2017)

In this study, the tension of crawler chain link of excavator is measured by experimenting in

horizontal straight, pivot steering, and differential steering conditions. The fracture surface

morphology of chain link crack is analyzed by scanning electron microscopy. Finite element analysis

result indicates that the maximum stress of chain link is lower than the yield strength of material. The

stress of key points in the cracked area and the fatigue life of chain link are obtained from the

International Journal of Modern Trends in Engineering and Research (IJMTER)

Volume 05, Issue 1, [January– 2018] ISSN (Online):2349–9745; ISSN (Print):2393-8161

@IJMTER-2018, All rights Reserved 186

simulation. The comparison between the simulation and experimental data confirms the accuracy of

the established virtual prototype model of excavator. Accordingly, the fatigue life of chain link is

analyzed, which is usually difficult to achieve by experiment.

2.2 Debashis Ghosh et. al.(2015)

This investigation is primarily aimed to examine the probable causes of in-service failure of

cage suspension gear chain used in coal mines. Optical microscopic analysis along with scanning

electron microscopy examinations are carried out to understand the metallurgical reasons for failure.

Detailed stress analyses are also carried out to evaluate the stress generated along the chain

periphery.

2.3 A. B. Sutar et. al. (2016)

Author studied the roller chain for weight optimization under various parameters. Parameter

under study is outer diameter of the link. Also various materials are studied for weight optimization.

2.4 Nilesh Patil et. al.(2015)

Finite Element Analysis of the conveyor chain link is performed to obtain optimum model of

chain link. Experimental investigation is performed using UTM to validate the FEA results.

2.5 S. G. Sapate et. al. (2016)

The present paper reports metallurgical investigation of fractured connecting pins of drag

chain conveyors used for coal conveying from raw coal hopper to grave gate in coal mill of a cement

plant. The failure analysis of two fractured pins was carried out. The analysis of the fractured surface

and fractographic studies by SEM indicated fatigue fracture due to bending stresses and mild to

moderate torsional stresses.

2.6 Cicek Ozes et. al.(2015)

The aim of this study is to examine the effects of various loading conditions on the stress of a

pin-loaded woven-glass fiber reinforced epoxy laminate conveying chain component. A numerical

and experimental study was carried out to determine the stress distribution of composite conveying

chain components used to convey loads.

2.7 Tae-Gu KIM et. al.(2010)

Case study was performed to investigate the effect of chain installation condition on stress

distribution that could eventually cause disastrous failure from sudden deformation and geometric

rupture. FEA analysis was performed to analyze chain under axial, tensile and bending loading.

Material under consideration was AISI 8622 and results were studied using chemical analysis.

2.8 Niels Fuglede et. al. (2015)

Simple roller chain drive consisting of two sprockets connected by tight chain spans is

investigated. A kinematic model of a two-sprocket roller chain drive with straight spans was

presented, along with a procedure for calculating the total chain wrapping length.

Analytical predictions were compared to multi body simulation results and demonstrated that

the total wrapping length of the chain generally varies periodically with the tooth frequency.

2.9 T. H. Bradley (2003)

Static and dynamic simulations of a continuously variable transmission (CVT) chain and

pulley system are developed in the MATLAB environment to determine the effect of a power

transmissions chain with involute inter-element contact surfaces on polygonal action in CVT

systems.

The static models developed here have been used as a tool for design of the inter-element

contact surfaces. Results from the static models show that, with proper design, CVT chains with

involute inter-element contact surfaces display less static mid-span displacement, smaller angle of

incidence at impact




2.10 M. Chew (1985)

The problem of determining the intensity of the pulsative loads, or technically, the impulsive

forces, has been studied in this paper. Also it has been deduced that when a chain engages a sprocket,

the links of the chain form the sides of a polygon. This polygonal structure is identified to be the

cause of the impulsive loads on the chain drive which contribute to excessive noise, excessive

vibration, and premature chain fatigue failure.

2.11 Tushar D. Bhoite et. al. (2012)

Studied the various application aspect and manufacturing aspects of roller chain. As besides

all other parameters author studied the effect of radial variation in outer link of roller chain. Focus of

the author is to reduce the weight of chain link.

2.12 Bahir H. Eldiwany et. al. (1989)

This paper deals with experimental and analytical analysis of roller chain using chain load

distribution test machine. Also effect of lubrication is also studied on stresses occurring in roller

chain.

2.13 Shoji Noguchi et. al. (2009)

This research deals with study of parameters which influence weight of the roller chain. Here

weight reduction in the roller chain is achieved by parameters like centrally located holes,

circumference of the link plate edge. Also materials for link plate of roller chain were varied to study

the effect.

2.14 Li-Xin et. al. (2010)

Dynamic behavior of roller chain is studied in this research by developing dynamic model of

roller chain. It was concluded that impact stress are imparted on roller due to meshing impact

between roller and sprocket.

2.15 M. Sujata et. al. (2006)

Author studied conveyor chain system and found out the reasons for failure of the system.

According to research chain failed due to defects in material like forging defects.

2.16 James C. Conwell et. al. (1995)

Dynamic behavior of roller chain was studied by mounting strain gauge on link side plate. It

was concluded that under quasi static condition dynamic effects can be neglected for roller chain.

The new test machine was designed specifically to investigate roller chains. Parameters under study

were polygonal action, intentional clearances, unintentional dimensional variations due to

manufacturing tolerances, friction.

2.17 Barge P. R. et. al. (2014)

Finite element analysis of the roller chain was performed to reduce unintentional stresses.

Various weight reduction methods like chamfering, filleting on the outer link are studies.

2.18 M. Koray Kesikci et. al. (2004)

Author studied the boundary element method and finite element method for stress analysis of

the link of roller chain. It was found in analysis that maximum stress area is located near boundary of

the holes present on link. Along with this he also concluded that Finite element method is more

superior than Boundary element method as the results founds were more correct. The mechanical

behaviors of a standard roller chain which is loaded by the maximum allowed load are considered.

Comparing the results of the both techniques with each other and the results of literature, the

appropriate method for the roller chain problem is proposed.

2.19 Kyosuke Otushi (1997)

The book consists of complete procedure to design the conveyor chain in step by step

manner. It also includes the standard specification tables for selection of chain.




2.20 Khaled Al-Fadhalah et. al. (2010)

Paper deals with experimental investigation of reason of failure of chain links during towing

operation. Optical emission spectrometry showed that alloying elements like NI, Cr, and Mo are

having lesser percentage than that required by ASTM standards. Also additional reason for failure

was deduced as rusty working condition.

2.21 Prashant Mulmule et. al (2017)

In this paper basic structure of roller chain is studied and various optimization parameters are

studied for weight reduction of roller chain. FEA analysis of roller chain is performed and results are

further utilized for study.

III. PROBLEM STATEMENT

A suitable type of chain is to be selected for horizontal slat conveyor for transportation of

anthracite coal in a sugar factory. Conveyor chain is to be designed, analyzed and optimized for

weight reduction for specific application. Details of problem are as follows:

Material to be transported: Anthracite Coal

Length of conveyor: 19m

Rate of flow of material: 28Tons/hour

Width of conveyor conduit: 320mm

Height of conveyor conduit: 280mm

distribution: Even Roller diameter: 210mm

Number of chains: 1

.

Figure 1. Concept Structure of Chain Conveyor

IV. OBJECTIVES

In this project basically we are dealing with roller chain system for transportation of granular

material and the considered environment is found to be dusty, moist and material is prone to

corrosion. So the objectives of project are

1) Finding a suitable material for roller chain which can withstand stresses and which should be

corrosion free

2) Finding optimized design parameters for roller chain.

3) Weight reduction of the roller chain by using various parameters like thickness of link and

external diameter of roller.

4) Validating the FEA results by testing the specimen on universal testing machine.

V. DESIGN OF ROLLER CHAIN LINK

Material Flow (Q):

Q = 28 Tons/Hour………….. (Given)

Chain Velocity (v):




Where = specific weight of transported material

= 0.7 tons/ m3 [9]

= 0.25m/sec……………… (i)

Weight of transported material (P1):

= 591.11 kg

= 5798.789N

Selection of suitable chain

From design of chain it is clear that weight of transported material will be resisted by selected chain

so we have to multiply by FOS to weight of transported material. Here for general applications FOS

is taken as 8.

Hence, Breaking Load (FB)

FB= P1. k = 5798.789 x 8 = 46390.40 N

From Designer guide for chain, according to DIN 8167 (ISO 19877), MRC 80X 125 is selected.

Now as breaking load = 46390.40 N

Operating load = 2/3 (Breaking Load)….. [9]

=2/3 (46390.40)

= 31525.33 N……………………….. (ii)

As the numbers of sprockets are 13 out of them minimum 6 numbers of sprockets will be engaged

during motion of chain.

Hence, Load on each roller =

=

= 5254.22 N………… (iii)

Table 1. Existing Chain Material Properties

Allowable stress =

=

= 209 Mpa………….. (iv)

VI. DRAWING OF ROLLERT CHAIN

Figure2. 2D Drawing of Roller Chain Link

Material Ultimate

Strength

Tensile Yield

Strength

ASTM -

A53M steel 630 MPa 418 MPa




VII. 3D MODELLING OF ROLLER CHAIN

Figure3. 3D Drawing of Roller Chain

VIII. STATIC ANALYSIS OF EXISTING CHAIN LINK

By static analysis we can compute stresses, displacement, in a component in steady loading

condition. As previously said tension force is basically applied on roller when the conveyor starts

and sudden jerk is experienced by chain link. So it is necessary to analyze stresses generated in the

chain link. For existing chain the material is ASTM-A53M low carbon steel. For analysis of roller

chain link first static structural module is selected in ANSYS 16.0. Then 3D model of roller chain

link created in CATIA V5 is imported in ANSYS 16.0. In next step meshing is done to model by

using tetrahedral and hexahedral elements. In the next step boundary condition is applied to roller

chain link by fixing one end and force of 5254.2 N is applied on roller at other end. Chain link is

then analyzed for deformation and stresses generated in it. Following are the results obtained in

analysis of roller chain link.

Figure 4. Deformation of chain after application of force

Figure 5. Von Misses Stress in the chain after application of force




Table 2: Result Table for Existing Chain Analysis

Sr.

No. Component

Deformation Equivalent

Stress

(MPa) (mm)

1 Roller chain

link 0.010224 32.358

As previously calculated,

Allowable stress = 209 MPa

Generated stress (ANSYS result) = 32.358 MPa

Current FOS = Allowable stress/ Generated stress

= 209/32.358

= 6.4589………………………… (v)

As factor of safety is beyond 6 it is clear that existing roller chain link is beyond safe limit and there

is scope for material removal for weight reduction, change of material and dimensional changes.

IX. ANALYSIS OF ROLLER CHAIN FOR VARIOUS MATERIALS

It is clear that we need to replace the material of the chain to overcome the problem of

corrosion and to give the chain higher strength. Chemical analysis by optical emission spectrometry

showed that existing material for roller chain is having lesser percentage of elements like NI, Cr, Mo

than required as per ASTM standards[10]. This basically results into reduced hardness of component.

For this purpose we have selected following materials for roller chain for analysis.

1. 8620-I (chrome-nickel-moly) Alloy Steel

2. SS 60-A Mild (low-carbon) Hot Dipped Galvanized Steel

3. 1020 Mild (Low-carbon) steel

4. Stainless Steel

Analysis for SS 60-A Mild (low-carbon) Hot Dipped Galvanized Steel

Figure 6. Deformation in the chain link

Figure 7. Von-Mises Stress on the chain links




Figure 8. Frictional Stress on connections of the chain link

Similarly Deformation, Von-Mises Stress and Frictional Stress is found out for other

specified materials also and the results are tabulated as follows.

Table 3. Results for FEA of Roller Chain for Various Materials

Sr.

No. Material

Defor

mation

Von

Misses

stresses

(MPa)

Frictional

Stresses

(MPa)

Weight

(Kg/ m)

(mm)

1

A-53M

(Existing

Material)

0.0102

24 32.358 89.262 157.56

2 SS 60

Mild Steel

0.0096

4 30.51 84.165 133.14

3

8620

Alloy

Steel

0.0091

45 28.945 79.846 139.83

4 1020 Mild 0.0108

97 34.487 95.126 137.87

5 Stainless

steel

0.0116

75 36.95 101.93 129.98

From above table it is clear that compared to A-53M (Low carbon steel) SS 60 (Low carbon)

Hot Dipped Galvanized Steel is having 15.50% less weight. Along with this galvanized steel has the

advantage of higher resistance to corrosion which is basic requirement for working of chain in rusty

and dusty environment. Galvanized steel has advantage of reliability, automatic protection to

damaged area by sacrificial protection, lowest long term cost. Here we can see rise in deformation,

von misses stress and frictional stress. But this rise in stress is under tolerable limit so we have

selected SS 60 (Mild steel) for roller chain for particular application.

X. OPTIMIZATION ON BASIS OF CHANGE IN THICKNESS OF OUTER STRIP

Since the current design of roller chain link is beyond safe limit there is scope for weight

reduction by changing dimensions of link. Up till now weight reduction by reducing diameter of




outer link, centrally located holes, and circumference of the link plate edge is tried. But results can be

better by reducing the thickness of the inner and outer link of the roller chain. Thickness of the link is

5mm. We will reduce thickness in step by step manner with decrement of 0.25mm and will carry out

FEA on the model.

Analysis for 4.00mm thickness of link plate for SS 60


Figure10. Von-Mises Stress on the chain links





Following observations can be made from above Ansys results

Table 4. Results for Analysis of Link for Various Thickness

Sr.

No

Thickness

Dimension,

mm

Deflection,

mm

Von-

misses

Stress,

MPa

Frictional

Stress,

MPa

Weight

of

Link,

kg

1 5 (E) 0.010224 32.358 89.262 0.8769

2 5 (N) 0.0096405 30.51 84.165 0.8623

3 4.75 0.011092 35.103 96.615 0.8568

4 4.5 0.012065 38.182 105.09 0.8368

5 4.25 0.013038 41.261 113.57 0.8167

6 4 0.014594 46.188 127.13 0.7966

From above table it is clear that there is reduction in weight of the link with reduction in

thickness. Though there is significant rise in deflection, von misses stress and frictional stress these

values are under tolerable limit. So we modified the design of roller chain by changing thickness of

inner and outer link from 5mm to 4mm with weight reduction by 9.15%.

XI. OPTIMIZATION ON BASIS OF CHANGE IN DIAMETER OF ROLLER CHAIN LINK

As we studies in previous section further weight reduction is possible in roller chain. Now the

parameter selected for further weight reduction is outer diameter of the roller of the roller chain. As

there is slip fit between roller and pin inner diameter of the roller is fixed. But outer diameter of the

roller can be reduced for weight reduction. Current outer diameter of roller is 30 mm. We are going

to reduce the diameter in step by step manner by decrement of 2.50mm up till 20mm.

Table 5. Steps for Reduction in Outer Diameter of Roller

Sr.

No.

Inner

Diameter mm

Outer

Diameter,

mm

Thickness, mm

1 12 30 9

2 12 27.5 7.75

3 12 25 6.5

4 12 22.5 5.25

5 12 20 4

Analysis for roller outer diameter 20.00 mm





Figure 13. Von-Mises Stress on the chain links





Above results can be tabulated as follow

Table 5. Result Table for Analysis of Roller chain for Various Roller Diameter

Sr

No

OD

mm

Deformation,

mm

Von

Misses

Stress,

MPa

Frictional

Stress,

MPa

Weight,

kg

1 30 0.014594 46.188 127.13 0.7966

2 27.5 0.017543 51.574 131 0.7258

3 25 0.020319 57.763 141.39 0.661

4 22.5 0.029349 93.396 155.59 0.6024

5 20 0.033678 115.92 161.87 0.55

From above table it is clear that as outer diameter of roller of chain link is decreasing weight

is also decreasing. If we consider the initial condition for existing material and link plate thickness

5.00mm, weight was 0.87688 Kg and now for 4mm link thickness and 20mm outer diameter weight

is 0.55004Kg. So percentage reduction in weight is 37.27%. Though there is considerable rise in

deformation, stress and frictional stress but these values are below allowable limit.

Also for SS 60 Yield strength is 470Mpa. And for safe design FOS should be at least 2 [9].

Hence,

Allowable stress for SS 60 (Hot dipped galvanized) =

Yield Strength / Allowable FOS

= 470/2

= 235Mpa

Now Current FOS = Allowable stress / Current Stress

= 235/ 115.92 ……… (Table 12. 2)

= 2.027

As the current FOS is 2.027 > 2. Our design of roller chain is safe.

XII. EXPERIMENTAL TESTING

For validating the results obtained by finite element analysis we have used universal testing

machine (UTM). UTM can be used for tension as well as compression test. As in present case

tension force is acting on the link of roller chain we are going to use UTM for testing the specimen

by tension test.

Specification of the UTM used for experimentation is as follows.

Table 6. Specification of UTM

Sr

No. Parameter

Specification

1 Max Load

Capacity 100 KN

2 Load Accuracy Within +/- 1%

3 Test Space Tensile 650 mm

Compression 600 mm

4 Piston Stroke 280 mm

5 Dimensions 750*600*2500 mm

6 Power Supply

Three-Phase, 240V-

50HZ

Here chain link specimen is fixed in jaws of the machine and then load is applied on the

specimen. Following is the actual setup for tensile testing of the specimen




Figure 15. Actual Test Setup

Following are the results obtained after testing of the existing specimen and newly designed

specimen.

Table 7. Experimental Result Table for Deformation of Chain Link

Sr.

No Condition

Weight

kg

Deformation

mm

Deformation

mm

FEA Result Experimental

1.

Existing Design

(5mm Thickness

of plate, 30mm

Roller Diameter)

ASTM A53M low

carbon steel.

0.88 0.010224 0.0314

1

New Design(4mm

thickness of plate,

20mm roller

diameter) SS 60

Mild Steel

0.55 0.033678 0.0248

From above table it can be seen that experimental deformation and analytical deformation is almost

same

XIII. CONCLUSIONS

From the FEA and Experimental analysis results we can conclude that optimal value of

thickness of outer link in 4mm and that of outer radius of roller is 20mm respectively. Though

weight reduction we obtained for a single link seems tiny but with collective effect for such number

of links is significant. Following specific conclusion can be drawn from results obtained.

1. Experimental testing is done on SS 60 Mild Steel (Newly designed) model of roller chain and

results were found close to FEA results.

2. Weight in the newly designed roller chain link is reduced by 37.27%.

3. Newly selected chain is having von-misses stresses 29.94 %, Frictional Stresses 29.78 % and

deflection 29.95 % greater but is within allowable range.

4. Finally selected model for roller chain is having 4.0 mm thick outer link plate with roller

diameter as 20 mm with SS 60 Mild steel material.




XIV. ACKNOWLEDGEMENT

The report is outcome of guidance, moral support and devotion bestowed on me throughout

my work. For this I acknowledge and express my profound sense of gratitude and thanks to

everybody who have been a source of inspiration during the experimentation. First and foremost I

offer my sincere phrases of thanks with innate humility to, Prof. T.Y. Badgujar (H.O.D) Mechanical

Engineering Department, Late G. N. Sapkal COE, and Nashik for providing help whenever needed.

The consistent guidance and support provided by Prof. T.Y. Badgujar is very thankfully

acknowledged and appreciated for the key role played by him in providing me with his precious

ideas, suggestions, help and moral support that enabled me in shaping the experimental work.

REFERENCES

[1] Huanyu Zhao, Guoqiang Wang, HaotongWang, Qiushi Bi, Xuefei Li (2017), ―Fatigue life analysis of crawler

chain link of excavator‖, Elsevier, Engineering Failure Analysis S1350-6307(16)31252-3

[2] Debashis Ghosh, Shamik Dutta (2015), ―Failure Investigation of a Cage Suspension Gear Chain used in Coal

Mines‖, Springer, s40033-015-0092-6.

[3] A. B. Sutar, G. E. Kondhalkar(2016), ―Optimization of Weight of Roller Chain Inner Link Plate for Typical

Industrial Chain Application‖, International Journal of Innovations in Engineering Research and Technoogy, ISSN:

2394-3696 VOLUME 3, ISSUE3, MAR.-2016

[4] Nilesh Patil, Arun M. (2015), ―A Study on Optimization of Roller Conveyor Chain Link Plate by Using Topological

Approach‖ International Journal for Scientific Research & Development| Vol. 3, Issue 10, 2015 | ISSN (online):

2321-0613

[5] S. G. Sapate, V. K. Didolkar (2016), ‖ Metallurgical investigation of failure of coal mill drag chain pin‖, Elsevier,

Materials and Design 30 (2016) 2623–2629

[6] Cicek Ozes, Mine Demirsoy (2015),‖Stress analysis of pin-loaded woven-glass fiber reinforced epoxy laminate

conveying chain components, Elsevier, Composite Structures 69 (2015) 470–481

[7] Tae-Gu KIM, Seong-Beom (2010), ―A Case Study on Engineering Failure Analysis of Link Chain‖, Safety and

Health at Work, eISSN : 2093-7997.

[8] Niels Fuglede, Jon Juel Thomsen (2015),‖Kinematic and Dynamic Modeling and Approximate Analysis of a Roller

Chain Drive‖, Elsevier, Journal of Sound and Vibration.

[9] T. H. Bardley (2003),‖ Simulation of Continuously Variable Transmission Chain Drives with Involute Inter-element

Contact Surfaces‖, Thesis, UNIVERSITY OF CALIFORNIA.

[10] M. Chew (1985),‖ Inertia Effects of a Roller-Chain on impact Intensity‖, Journal of Mechanisms, Transmissions,

and Automation in Design, Vol. 107/123

[11] Tushar D. Bhoite, Prashant M. Pawar(2012), ―FEA BStudy of Effect of Radial Variation of Outer Link in a Typical

Roller Chain Link Assembly‖, International Journal of Mechanical and Industrial Engineering (IJMIE), Vol‐1,

Issue‐4, ISSN No. 2231 –6477.

[12] Bahir H. Eldiwany, Kurt M. Markshek (1989), ―Experimental Load Distributions for Double Pitch Steel Roller

Chains on Polymer Sprocket‖, Elsevier, Mechanism and Machine theory, Vol 24, No 5, PP 335-349.

[13] Shoji Nogucchi, Kohta Nagasaki, Tohru Kanada, (2009), ―Static Stress Analysis of Link Plate of Roller Chain using

Finite Element Method and Some Design Proposal for Weight Saving‖, Journal of Advanced Mechanical Design,

Systems and Manufacturing, Vol-3, No.-2.

[14] Li-Xin, Yang Yuhu, Chang Zongyu, (2010), ―Dynamic modeling of a roller chain drive system considering the

flexibility of input shaft‖, Journal of Mechanical Engineering, Vol. 23, No. 3.

[15] M. Sujata, M.A. Venkataswamy, M.A. Parameswara, S.K. Bhaumik, (2006), ―Failure analysis of conveyor chain

links‖, Elsevier, Engineering Failure Analysis 13, 914–924

[16] James C. Conwell, G. E. Johnson, (1995), ―Design Construction and Instrumentation of a machine to measure

tension and impact forces in roller chain drives‖ Elsevier, Mech. Mach. Theory, Vol-31, No4, pp. 533-544.

[17] Barge P. R. Waghmare V. H, (2014) ―Roller Chain Link Plate Design Based on FEA‖ Journal on Recent and

Innovation Trends in Computing and Communication, ISSN: 2321-8169, Volume: 2 Issue: 12, 4109 – 411

[18] M. Koray KESİKÇİ, M. Cüneyt FETVACI, C. Erdem İMRAK, (2004), ―Stress distribution of the chain link by

means of boundary element and finite element methods‖ Journal of Engineering and Natural Sciences, sigma 2004-

4.

[19] Kyosuke Otushi, (1997), ―The Complete Guide to Chain‖, U.S. Tsubaki, Inc.

[20] Khaled Al-Fadhalah, Ahmed Elkholy, Majed Majeed, (2010) ―Failure Analysis of Grade-80 Alloy Steel Towing

Chain Links‖, Elsevier, Engineering Failure Analysis 17 (2010) 1542–1550.

[21] Prashant S. Mulmule, Tushar Y. Badgujar, Akshay. G. Tajne (2017) ―FEA Analysis of chain link for finding

optimization parameters‖, International Journal of Advance Research and Innovative Ideas in Education, Volume: 3,

Issue: 2, ISSN: 2395-4396, Paper ID: 4373.




BIOGRAPHIES

Mr. Prashant S. Mulmule received the degree in B.E.

Mechanical from Late G. N. Sapkal College of Engineering,

Nashik, Maharashtra, India in July 2014 and pursuing master

degree in (Mechanical Design Engineering) in Late G.N. Sapkal

College of Engineering, Nasik, Maharashtra, India under

Savitribai Phule Pune University, Pune, and Maharashtra, India

Prof. T.Y Badgujar is an Associate Professor AND Head of the

deaprtment in Late G.N. Sapkal College of Engineering, Nasik,

Maharashtra, India. He received the degree in B.E. Mechanical

and Specialization in M.E. (Advance Production System). He

has 19.5 years of experience in teaching field

Documents

DESIGN, ANALYSIS AND OPTIMIZATION OF ROLLER CHAIN LINK … · DESIGN, ANALYSIS AND OPTIMIZATION OF ROLLER CHAIN LINK FOR COAL TRANSPORTATION USING FEA Prashant S. Mulmule1, Prof