international review of mechanical engineeringsyahruls/publication/2013/7 ireme iman.pdf · ali...

International Review of Mechanical Engineering

(IREME)

Contents:

Experimental Study on the Thermal Performances of a Heat Pipe Solar Collector by S. Maalej, M. C. Zaghdoudi, R. Ramzi

1

Structured Methodology for Implementation of Assistive Domotics by Marcos Corrêa de Carvalho, João Maurício Rosário, Liz Katherine Rincón Ardila, Almiro Franco da Silveira Junior

10

Effect of Parameters Variation on the Performance of Adsorption Based Cooling Systems by H. Z. Hassan

24

A Mild Steel Shear Zone Temperature Minimization Using Genetic Algorithm and Direct Search Toolbox in CNC Turning Operation by Adnan Abbas, Mohamad Minhat, Md. Nizam

38

Orthogonal Least Squares Method and its Application to Nonlinear Modeling of Automotive Engine Fuelled with Palm Oil Methyl Esters by Azuwir Mohdnor, M. Z. Abdulmuin, A. H. Adom

46

Recent Development of Novel Lead-Free Composite Solders Using Microwave-Assisted Sintering Powder Metallurgy Route by M. A. A. Mohd Salleh, A. M. Mustafa Al Bakri, Flora Somidin, H. Kamarudin

53

A Study of an Air-Conditioning Prototype Powered by Solar Energy by Chaouki Ali, Rached Nciri, Kamel Rabhi, Faouzi Nasri, Habib Ben Bacha

60

Effect of Curing System on Properties of Fly Ash-Based Geopolymer Bricks by W. I. Wan Mastura, H. Kamarudin, I. Khairul Nizar, A. M. Mustafa Al Bakri, M. BnHussain

67

Investigation of Palm Fatty Acid Distillate as an Alternative Lubricant of Petrochemical Based Lubricants, Tested at Various Speeds by I. Golshokouh, S. Syahrullail, F. N. Ani, H. H. Masjuki

72

Control of a Dynamic Vibration Absorber Using a Magneto-Rheological Damper by Mahmoud H. Salem, M. N. Anany , M. El-Habrouk , Sohair F. Rezeka

81

Sn and Pb Additives Experimental Influence on Internal Combustion Engine Lubricant Concentration and Viscosity by Slimen Attyaoui, Said Mlik

91

New Adsorption Air Conditioning System Powered by Solar Energy; Operation Principals and Winter Mode Modelling and Simulation by Chaouki Ali, Kamel Rabhi, Rached Nciri, Faouzi Nasri, Habib Ben Bacha

96

(continued on inside back cover)

ISSN 1970-8734Vol. 7 N. 1

January 2013

REPRINT

International Review of Mechanical Engineering (IREME)

Managing Editor: Santolo Meo Department of Electrical Engineering FEDERICO II University 21 Claudio - I80125 Naples, Italy [email protected]

Editorial Board:

Jeongmin Ahn (U.S.A.) Marta Kurutz (Hungary)

Jan Awrejcewicz (Poland) Herbert A. Mang (Austria)

Ali Cemal Benim (Germany) Josua P. Meyer (South Africa) Stjepan Bogdan (Croatia) Bijan Mohammadi (France)

Andrè Bontemps (France) Hans Müller-Steinhagen (Germany)

Felix Chernousko (Russia) Eugenio Oñate (Spain) Kim Choon Ng (Singapore) Pradipta Kumar Panigrahi (India)

Horacio Espinosa (U.S.A) Constantine Rakopoulos (Greece)

Izhak Etsion (Israel) Raul Suarez (Spain) Michael I. Friswell (U.K.) David J. Timoney (Ireland)

Nesreen Ghaddar (Lebanon) George Tsatsaronis (Germany)

Adriana Greco (Italy) Alain Vautrin (France) Carl T. Herakovich (U.S.A.) Hiroshi Yabuno (Japan)

David Hui (U.S.A.) Tim S. Zhao (Hong Kong) Heuy-Dong Kim (Korea)

The International Review of Mechanical Engineering (IREME) is a publication of the Praise Worthy Prize S.r.l.. The Review is published bimonthly, appearing on the last day of January, March, May, July, September, November. Published and Printed in Italy by Praise Worthy Prize S.r.l., Naples, January 31, 2013. Copyright © 2013 Praise Worthy Prize S.r.l. - All rights reserved. This journal and the individual contributions contained in it are protected under copyright by Praise Worthy Prize S.r.l. and the following terms and conditions apply to their use: Single photocopies of single articles may be made for personal use as allowed by national copyright laws. Permission of the Publisher and payment of a fee is required for all other photocopying, including multiple or systematic copying, copying for advertising or promotional purposes, resale and all forms of document delivery. Permission may be sought directly from Praise Worthy Prize S.r.l. at the e-mail address: [email protected] Permission of the Publisher is required to store or use electronically any material contained in this journal, including any article or part of an article. Except as outlined above, no part of this publication may be reproduced, stored in a retrieval system or transmitted in any form or by any means, electronic, mechanical, photocopying, recording or otherwise, without prior written permission of the Publisher. E-mail address permission request: [email protected] Responsibility for the contents rests upon the authors and not upon the Praise Worthy Prize S.r.l.. Statement and opinions expressed in the articles and communications are those of the individual contributors and not the statements and opinions of Praise Worthy Prize S.r.l.. Praise Worthy Prize S.r.l. assumes no responsibility or liability for any damage or injury to persons or property arising out of the use of any materials, instructions, methods or ideas contained herein. Praise Worthy Prize S.r.l. expressly disclaims any implied warranties of merchantability or fitness for a particular purpose. If expert assistance is required, the service of a competent professional person should be sought.

REPRINT

International Review of Mechanical Engineering (I.RE.M.E.), Vol. 7, N. 1

ISSN 1970 - 8734 January 2013

Manuscript received and revised December 2012, accepted January 2013 Copyright © 2013 Praise Worthy Prize S.r.l. - All rights reserved

72

Investigation of Palm Fatty Acid Distillate as an Alternative Lubricant of Petrochemical Based Lubricants, Tested at Various Speeds

I. Golshokouh1, S. Syahrullail1, F. N. Ani1, H. H. Masjuki2 Abstract – Lubricant oils have an important role in manufacturing processes for reducing friction and wear between in-contact rotational pieces with different speeds. Vegetable oils are known as new, clean and renewable sources. Palm Fatty Acid distillate (PFAD) is sourced from the vegetable oil family and is potential as an alternative source of mineral lubricant/Hydraulic oils. This study was performed utilizing various speeds (800, 1000, 1200, 1400 and 1600rpm) and according to the American Society for Testing and Materials (ASTM) with number D 4172 (speed 1200 rpm, load 392N, temperature 75°C and in one hour) using a four ball wear machine tester. To evaluate the PFAD results, similar experiments were done using Engine and Hydraulic oil and the results were compared mutually. The results showed that, the anti-friction and anti -wear ability of PFAD were higher than those of Engine and Hydraulic mineral oils. Also, the value of flash temperature parameter of PFAD oil was higher than other test oils. However, the amount of viscosity oil for PFAD was less than Engine oil. Copyright © 2013 Praise Worthy Prize S.r.l. - All rights reserved. Keywords: PFAD Oil, Four-Ball Tribotester, Wear Scar Diameter, Friction, Flash Temperature

Parameter, Viscosity

Nomenclature ASTM The American Society for Testing and

Materials PFAD Palm Fatty Acid Distillate rpm Revolutions per Minute EP Extra Polish HRC Rockwell Hardness Testing Scales C mm Millimeter CCD Charge-Coupled Device AISI The American Iron and Steel Institute W The load in kilograms d Diameter WSD Wear Scar Diameter FTP Flash Temperature Parameter µ Coefficient of Friction T Frictional Torque IP International Petroleum test methods r Radius

I. Introduction Lubricant oils and Hydraulic oils play a major role in

industrial applications as they are used to reduce the wear and friction. Friction and wear are two major concerns that may disrupt all or part of contact surface. Mineral oil is the main source of Hydraulic and lubricant oils.Every year, more than 12 million tonnes of lubricant waste are released into the environment. Waste lubricant with base minerals can pollute nature by burning or entering the air, drinking water and seas [1],[2],[3].

Alertness is crucial to save the environment from the increasing pollution. Furthermore, the source of mineral oil is limited and it will deplete in the near future. Researches have begun new investigations to find renewable, clean and environment friendly sources to replace Mineral oil. Vegetable oils are potential as alternative sources of lubricant oil [4],[5],[6]. They are renewable, environmental friendly, cheap, nontoxic and clean [7]. The base structure of Vegetable oils is triacylglycerol [8] and the fatty acid in this structure creates better thermal and oxidative stability of vegetable oil [9]. There are several studies about Vegetable oils and its application in lubricant industry and it can replace mineral oil [10],[11],[12],[13],[14].

The anti-wear and extreme pressure of Tribiological behavior of coconut oil were investigated with reference from Jayadas (2006) and the result showed that coconut oil had a good boundary lubricant coefficient of friction and wear rate compared to commercial lubricants [15].

Wear scar, coefficient of friction, and viscosity of pure Jatropha oil with base lubricant were measured and compared with Jatropha oil mix to additive material in ASTM condition [16].

In other research, the Tribological behavior and lubricant ability of Refined, bleached and deodorized palm stearin were investigated at different loads (40, 50, 60kg) and constant speed (1200rpm).

In the first part and second part, the experiments were performed at different speeds (800rpm, 1000rpm, 1200rpm and 1400rpm) and constant load. The results of Refined bleached and deodorized palm stearin were

REPRINT

I. Golshokouh, S. Syahrullail, F. N. Ani, H. H. Masjuki

Copyright © 2013 Praise Worthy Prize S.r.l. - All rights reserved International Review of Mechanical Engineering, Vol. 7, N. 1

73

compared with the additive-free paraffinic mineral oil with base lubricant to value of their results [17]. The Effect of Temperature on Refined bleached and deodorized palm stearin was investigated based on the Tribological Behavior and using the four balls Tribotester machine with load (392N) and speed (1200).

The results also were compared with additive-free paraffinic mineral oil [18]. The wear was measured using respond surface method at different speeds and loads of palm olein oil in lubricant base and the results were compared with stock lubricant [19]. Physical properties e.g. coefficient of friction, viscosity and wear of palm oil and mineral lubricant oil were investigated using the four ball tribotester under the same condition [20]. The physical properties such as anti-wear, anti-friction, viscosity index and flash parameter point of PFAD and Jatropha with base lubricant were investigated according to ASTM condition, number D 4172, method B using four ball Tribotester and the results were compared with the physical properties of two mineral oils with base lubricant [21]. Some parameters such as sliding speeds can affect the performance of the contact parts and the Tribological behavior. Besides that, rotational speed has an important role in increasing or decreasing the friction and wear in manufacturing process, especially in bearing, rolling and rotational parts [22].

There are several studies about the use of Vegetable oils in different applications. Yet, there are still no reported research studies on utilizing PFAD at different rotational speed and in the Lubricant and the Hydraulic application.

The aim of this research is to investigate and evaluate the Tribological properties e.g. wear scar, coefficient of friction, viscosity, extreme pressure condition and flash temperature parameter of PFAD at different speeds (800, 1000, 1200, 1400 and 1600 rpm) with constant load (392N) and temperature(75°C) and also in ASTM condition for lubricant and Hydraulic applications. Each experiment was done four times for each load and to evaluate the experiment; all results were compared with the result of Engine and Hydraulic commercial oils with base lubricant.

II. Experiment The friction and wear of PFAD, Engine and Hydraulic

oils were measured using four ball Tribotester, CCD camera and microscope in this research. Boerlage (1993) described four balls tribotester in measuring friction torque [23] as shown the schematic diagram of a four ball tribotester in Fig. 1.

This machine has two main parts, head and body. Inside the body, there are three balls in the middle part. These balls are fixed together with a ball ring and these collections are clenched together with a lock nut.

Thermocouple and heater are in the body part. The thermocouple is embedded at the bottom of the ball pot and it is responsible for measuring the oil temperature inside the cup.

Fig. 1. Schematic diagram of four ball wear geometry: 1 –stationary ball 2 – Rotating single ball 3 – Rotating gripper for upper ball 4 – Test lubricants 5 – Cup for griping stationary three balls 6-lock nut 7-balls

ring 8- Heater 9-Thermocouple There is a drive motor in the head part of the four ball

Tribotester and one ball is connected to it and driven with the drive spindle of motor. Before starting the experiment, the test oils need to be added into the collection until three balls are immersed in it. Also, the required load is inserted from the underneath ball pot and the balls will be pressed onto the upper ball. The wear scar diameter will be measured using CCD camera and acquisition software. Also, a digital microscope is used to observe abrasives on the specimen balls.

II.1. Ball Model

The specifications of the test ball used in this experiment were of AISI E-52100 and chrome alloy steel type. The diameter of each ball was 12.7 mm. The balls hardness was 64 to 66 Hrc and all balls had extra polish (EP) grade of 25. For each experiment, all balls were cleaned with acetone and fresh lint-free industrial wipe. Also, four new balls were used in each experiment.

II.2. Experimental Oil

The oil palm for the first time was introduced to Southeast Asia in 1848[24]. Nigeria, Indonesia and Malaysia are the biggest palm oil producer countries in the world. Malaysia produced 17.73 million tons of crude palm oil in 2008 and it is about 41% of all palm oil products in the world [25]. Palm fatty acid distillate (PFAD) is a by-product of physical refining of crude palm oil products.

Through neutralization, bleaching, and deodorizing, a refined, bleached, and deodorized palm oil is obtained from crude palm oil and PFAD is produced as a by-product [26]. PFAD is composed of 93wt% free fatty acid and the rest are triglycerides, monoglycerides (MG), diglycerides (DG) and traces of impurities. All chemicals including 99% methanol (MeOH), 98% sulfuric acid (H2SO4), and 99% sodium hydroxide (NaOH) are commercial grade [27],[28]. This oil is solid in temperature room and liquid in higher temperature. Table I shows the Ingredient of free fatty acid. Also for this research, we used Engine mineral oil and hydraulic mineral oil with high quality. Figs. 2 show PFAD at room temperature and crude palm.

REPRINT



74

(a) (b)

Figs. 2. (a). Palm fatty acid distillate in temperature room

(b). Crude palm

TABLE I THE CHEMICAL CHARACTERISTICS

OF PFAD OIL EXTRACTED FROM SEEDS The characteristic Percentage% Ecosenoic 0.2% Ecosanoic 0.3% Linolenic 0.3% Tetracosenoic 0.6% Myristic 1.0% Stearic 3.8% Linoleic 7.7% Oleic 33.3% Palmitic 45.6%

II.3. Experimental Conditions

These tests were carried out at a Variety of rotational speed of four ball tribotester spindle at 800, 1000, 1200, 1400 and 1600 rpm of experimental oils and used the American Society for Testing and Materials (ASTM) condition and according to the ASTM D4172 method test B of Temperature: (75 ± 2)°C, load (392N) and time: (60 ± 1s) [29].

II.4. Experimental Procedure

All parts of four balls tribotester and balls were cleaned with acetone and wiped before starting the experiment and after finishing it. A clean ball was installed at the spindle motor on the head part of the four ball tribotester. Three clean balls were placed in the ball pot and the lock ring was inserted around the three balls and in the ball pot. The lock nut around ball pot was tightened using a wrench with 68 Nm Torque. Around 10 ml of testing oil was added into the ball pot assembly.

The oil level must be over 3 mm from above the tip of the balls. Before each experiment, the four balls Tribotester was set up at current load, speed, temperature and time. The ball pot assembly was inside the machine and under the spindle on the antifriction disk. A thermocouple wire was attached to the ball pot assembly.

The required load test was added to the loading arm.

II.5. Viscosity

The internal friction of liquid is measured with viscosity. It is a resisting motion between liquid molecular layers. Viscosity is a vital lubricant property and has a direct impact onto the ability of oil lubricating

film or to reduce friction and wear. It also has a direct relation with liquid thickness and the wear rate of sliding surface. Absolute viscosity is defined with Newton as the ratio between the resulting shear rate and applied shear stress [30]. It is important to measure physical lubricant properties. Viscosity is measured with rotary viscosity meter that spins inside the containers of the liquid. Viscosity is measured with resistant to rotation and torque [30]. Viscosity index is used to measure the viscosity of liquid at variable temperature and normally is used in industrial applications, especially in the automotive industry.

II.6. Flash Temperature Parameter

Flash temperature parameter is the increase temperature between contacting rubbing pars with friction [31]. It is the lowest temperature where liquid vaporize into vapor and plays a major role in the decision to choose lubricant in industrial application.

Flash point temperature is a starting point to vaporize lubricant and decrease lubricant film between contacting surfaces. It is a limiting factor in the industrial application such as cutting and forming tools. Flash temperature parameter of PFAD, Engine and Hydraulic oils in ASTM condition and different speeds were measured in this study using Eq. (1):

1 4.WFTPd

= (1)

where W is the load in kilograms, and d is wear scar diameter (WSD) in millimeters [32], [33], [34].

II.7. Coefficient of Friction

Coefficient of Friction is a term to describe friction between contacting surfaces that are pressed together with force.The coefficient of static friction and coefficient kinetic counterpart are two kinds of coefficient of friction and are dimensionless scale value.

The coefficients of friction in this study were calculated according to IP-239 standards as shown in Eq. (2):

63T

Wrµ = (2)

where µ is the coefficient of friction, T is the frictional torque (kg mm), W is the applied load (kg), and r is the distance from the center of the contact surface on the lower balls to the axis of rotation, which was determined to be 3.67 mm [35],[36].

II.8. Wear Scar Test

Wear is the erosion movement of material from its original position on a solid surface performed by the action of another surface.

REPRINT



75

There are varieties of wear e.g., adhesive, abrasive, fatigue, erosive, cavitations, oxidative, fretting, melting and diffusive.

In this experiment, the wear was measured according to the ASTM condition method B (temperature 75°C, load 392N, speed 1200 rpm and 60 minutes) and at different speeds (800, 1000, 1200, 1400, 1600). A CCD microscope and scanning electron microscopy (SEM) were used to measure the wear scar on the balls specimen.

III. Result and Discussion The lubricant and hydraulic properties of PFAD oil

were investigated using a Tribotester, CCD camera and microscope.

The PFAD oil was studied at different speeds and in ASTM condition. This study is a good opportunity of discussing about new environmental friendly oil for industrial lubricant oils and alternative source for mineral oils.

III.1. Viscosity

Figure 3 shows the viscosity of PFAD, engine and hydraulic oils in ASTM condition and at different temperatures. This figure illustrates that the viscosity of engine and hydraulic oil were close at 35°C but the PFAD oil had lower viscosity compared to these oils. By increasing the temperature variation, the gap between the PFAD and mineral lubricant oil lessened. At 75°C, the viscosity for PFAD, Engine and Hydraulic oils were close and at higher temperature; the viscosity of PFAD was similar to Hydraulic oil and closely similar to Engine oil.

This figure also shows that viscosity decreased with the increase of the temperature of PFAD, Engine and Hydraulic oils, which showed an inverse relationship between viscosity and temperature. However, the lubricant with higher viscosity could create thicker lubricant film between contacting parts because with the decrease of the viscosity, the fluidity and dilution of lubricant also increased and the lubricant could move easier [37].

0

20

40

60

80

100

120

0 20 40 60 80 100 120 140

visc

osity

(m.p

as)

Temperature(°c)

PFAD oil

Engine oil

Hydraulic oil

Fig. 3. Kinematic viscosity measured for PFAD, engine and hydraulic oil under different tested temperature

III.2. Flash Temperature Parameter

The value of FTP was calculated using Eq. (1) which was obtained from the four balls Tribotester in different conditions. Fig. 4 clearly shows graph of flash temperature parameter of PFAD, Engine and Hydraulic oil at different speeds and in ASTM condition.

This figure also compares the value of flash temperature parameter for these oils. As seen in the figure, in general, the flash temperature for PFAD and Engine oils increased with the increase of test speed.

However, for Hydraulic oil, the opposite results were seen.

The maximum flash temperature for PFAD oil was obtained at 1400 rpm test speed, and for Engine oil and Hydraulic oils, the maximum flash temperature parameter was obtained in 1000 rpm.

This figure also shows that the highest value of flash temperature parameter was of PFAD and the lowest amount was of Hydraulic oil in ASTM condition and at different speeds.

0

20

40

60

80

100

120

140

0 200 400 600 800 1000 1200 1400 1600 1800

F.T.

P

Speed (rpm)

PFAD oil

Engine oil

Hydraulic oil

Fig. 4. Flash temperature parameter on ball bearings lubricated with PFAD, Engine and hydraulic oil under ASTM condition and indifferent

speed

III.3. Effect of Load on Coefficient of Friction

Fig. 5 shows the coefficient of friction for PFAD, Engine and Hydraulic oil at different speed and in ASTM condition.

This figure clearly shows that coefficient of friction decreased with the increase of the speed of PFAD and Engine oils, but there was not a clear tendency of Hydraulic oil; hence this graph had a zig-zag trend with increasing speed. Normally, the accumulation of heat and subsequent thermal instability are caused by the transition of mild wear to be severe mild due to the increase of sliding speed, but not for PFAD and Engine oil. It is assumed that the fatty acid in PFAD oil and additive material in Engine oil were caused by the reduction of thermal energy and protection of lubricant film during the increasing speed at the sliding contact junction.

This figure also shows that Engine oil had lower coefficient of friction than Hydraulic oil at different speeds. However, the average of coefficient of friction for Hydraulic oil was close to the average of coefficient of friction of Engine oil, and this oil had the same value

REPRINT



76

at 1000 and 1400 rpm. Figure 5 confirms that PFAD oil had the lowest coefficient of friction than Engine and Hydraulic oil in ASTM condition and at different speeds.

Furthermore, according to Eq. (2), coefficient of friction has direct relationship with friction. Based on the result, it can be expressed that PFAD oil had better anti friction ability than other test oils [38].

III.4. Wear Scar Diameter

The average of wear scar diameter of PFAD, Engine and Hydraulic oils are shown in Fig. 6. This figure shows that, the WSD of PFAD and Engine oil decreased with the increase of speed. However, the PFAD oil at 1600rpm showed different behavior.

Also, the Hydraulic oil graph had a zig-zag trend with increasing speed. Nevertheless, in overall, the wear scar diameter of Hydraulic oil increased with the increase of speed.

III.5. Wear Scar Surface Characteristics

After the experiments, the wear scar on the ball bearings surface was inspected with a CCD camera and the wear scars diameters of each ball were measured.

Figs. 7 show the ball surfaces of PFAD, Engine and Hydraulic oils at 800 rpm. In this figure, it can be seen clearly that the ball surfaces were covered with rough erosion and deep scratch and grooves.

0

0.01

0.02

0.03

0.04

0.05

0.06

0.07

0.08

0.09

0 500 1000 1500 2000

Coef

fiece

nt o

f Fr

ictio

n

Speed (rpm)

PFAD oil

Engine oil

Hydraulic oil

Fig. 5. Effect of rotational speed on coefficient of friction for PFAD, engine and hydraulic oil in 800, 1000,1200, 1400 and 1600rpm

0

0.2

0.4

0.6

0.8

1

1.2

0 500 1000 1500 2000

WSD

/MM

Speed(rpm)

PFAD oil

Engine oil

Hydraulic oil

Fig. 6. Effect of speed on Wear Scar Diameter (WSD) for PFAD, engine and hydraulic oil in 800,1000,1200,1400 and 1600rpm

The balls dipped in Engine oil were worn with rough erosion and corrosion with small pits of Hydraulic oil (see Fig. 12(a)).

This figure also shows that there were some small pits on the ball surface of PFAD oil and mild abrasions were observed on the ball specimen.

Figs. 8 show the wear scar on the balls specimen at 1000 rpm of PFAD, Engine and Hydraulic oils. In this figure, it can be seen that the wear scar lines of Hydraulic ball surface at 1000 rpm was less than 800rpm, and the edge of the wear scar was slightly ragged and obscured by metal. Light abrasion was observed on the PFAD and Engine oil ball specimen. There were differences between the wear scar on ball specimens for Engine oil at 800rpm and 1000 rpm.

Figs. 9 show the wear scar on the ball specimens of PFAD, Engine and Hydraulic oils in ASTM condition (Speed 1200 rpm). At this speed, circular rough abrasions with light pitting corrosion can be seen on the ball specimen of Hydraulic oil. Also, the ball specimen was ragged and could be obscured by metal (see Fig. 12(b)). Furthermore, there were some shallow grooves and some small pits on the Engine oil ball specimen (see Fig. 12(b)). Also, of PFAD oil, the wear scar was circular and was observed mild abrasion the ball surface specimen.

Figs. 10 show the representative wear scar from the balls surface of PFAD, Engine and Hydraulic mineral oil at 1400 rpm. In this figure, circular wear scars can be seen on all balls surface of test oils. Also, there was a mild abrasion on the ball bearing surface of PFAD and

Engine oils, whereas, there were rough abrasions with shadowy grooves of Hydraulic oil. Figures 11 show the wear scar for PFAD, Engine and Hydraulic oil at 1600 rpm. This figure also shows some shallow grooves on the PFAD and engine balls surfaces, and the wear scars were circular. Furthermore, Hydraulic ball surface abrasion was seen as the dominant wear mechanism and there were some deep grooves of this ball surface oil. Besides that, a fusion of metal between meeting surfaces and rough erosion was observed.

According to the previous studies, the stearic acid in vegetable oils can create affinity to absorb into the steel surfaces.

The communication between acid molecules and steel surface was caused by the chemically polymerized molecules between surfaces. This good affinity plays a major role in reducing friction and wear between surfaces [39]. The corrosion, pits and erosion were observed at different speed on balls area of experimental oils.

A thin layer of lubricant in higher speeds created a smooth surface area to prevent metal to metal contact.

There was observed shallow and deep grooves in balls surface in higher speeds. At lower speeds, with spend time and increase the temperature, the thin lubricant layer was broken and wear scare was obtain to be predominant.

For all test oils was observed the grooves on the contact parts, and was obtain material transfer from one surface to other surface. The chain fatty acid molecules

REPRINT



77

in PFAD structure create a high Inhibitory effect to increase the wear scar during the experiment.

As reported by Farooq (2011), Fatty acid molecules protect the lubricant film from destruction and carry out the boundary lubrication condition that suficiebtly prevents surface contact [39]. In addition, the stearic acid in PFAD oil provide a higher affinity to be absorbed in metal surfaces with a tribochemical reaction, this interaction between the acid molecules and metal surface play a major role to reduce friction and wear during sliding; a similar finding was described by Farooq [39].

In the contact zone of the balls surface for Engine and Hydraulic oil, carbon capacity increases due to the diffusion and in result the breakdown of the hydrocarbon structure.

This caused by increase the temperature and coefficient of friction with increase the load, a similar finding was reported by Jones and Scoot [40]. There was

observed few hills collapsed in Hydraulic and PFAD balls surface.

In microscope view, when the ball bearing is contacting together, the asperities junctions is created in the contact balls surface, and due to increase speed, the contact asperities has a plastically deform, then, the material would be cleaned or plucked from the asperities on the ball specimen.

This kind of adhesive wear was observed on a surface with a blocky shape as explained by Williams [41]. Due to upper ball bearing rotation, the worn materials were swept out to other balls surface and lubricant.

The contact surface is destroyed if the thickness of lubricant film was less than particles size. It should be noted that, this experiment used pure PFAD oil but there were anti-wear additives to reduce adhesive wear in the Engine and Hydraulic oils, and these additives have a major role in wear protection properties [42].

Figs. 7. Optical micrographs of wear area on the balls surface and in 800rpm. (magnification 463X and 50 µm) (a) PFAD oil, (b) Engine mineral oil, (c) Hydraulic mineral oil

(b) Mgnification 463X and 50 µm (c) Mgnification 463X and 50 µm (a) Mgnification 463X and 50 µm

Figs. 8. Optical micrographs of wear area on the balls surface and in 1000rpm. (magnification 463X and 50 µm (a): PFAD oil, (b) Engine mineral oil, (c) Hydraulic mineral oil

REPRINT



78

(a) Mgnification 463X and 50 µm (b) Mgnification 463X and 50 µm (a) Mgnification 463X and 50 µm

Figs. 9. Optical micrographs of wear area on the balls surface and in 1200rpm. (magnification 463X and 50 µm) (a) PFAD oil, (b) Engine mineral oil, (c) Hydraulic mineral oil

(a) Mgnification 463X and 50 µm (c) Mgnification 463X and 50 µm (b) Mgnification 463X and 50 µm

Figs. 10. Optical micrographs of wear area on the balls surface and in 1400rpm. (magnification 463X and 50 µm

(a) PFAD oil, (b) Engine mineral oil, (c) Hydraulic mineral oil

(b) Mgnification 463X and 50 µm (a) Mgnification 463X and 50 µm (c) Mgnification 463X and 50 µm

Figs. 11. Optical micrographs of wear area on the balls surface and in 1600rpm. (magnification 463X and Pome 50 µm)

(a) PFAD oil, (b) Engine mineral oil, (c) Hydraulic mineral oil

REPRINT



79

(a) Mgnification 463X and 50 µm (b) Mgnification 463X and 50 µm

Figs. 12. The pitting corrosion on ball specimen.(a): Hydraulic ball specimen in 800rpm. (b): Hydraulic ball specimen in 1200rpm

IV. Conclusion

This investigation was performed at different speeds and ASTM conditions for PFAD, Engine and Hydraulic oils with a lubricant/hydraulic base using a four ball tribotester.

The highest value for flash temperature parameter was from the PFAD oil. Other conclusions of this study are that the coefficient of friction, friction Torque and wear scar diameter decreased with the increase of speed; and the flash temperature parameter increased with the increase of the speed for PFAD and Engine oils. These physical properties were different from those of Hydraulic oil in each point. PFAD oil had better anti-friction and anti-wear ability compared to Engine oil and hydraulic oil.

The highest value of Viscosity was measured for engine oil. The results showed that the PFAD oil is indeed potential as an alternative source of Hydraulic and lubricant oils. PFAD is solid in room temperature and can only be used at higher temperatures.

Acknowledgements The authors wish to thank the Faculty of Mechanical

Engineering at the Universiti Teknologi Malaysia for their support and cooperation during this study.

The authors also wish to thank Research Management Centre (RMC) for the Research University Grant (GUP) from the Universiti Teknologi Malaysia, Fundamental Research Grant Scheme (FRGS) from the Ministry of Higher Education (MOHE) and E-Science Grant and ERGS from the Ministry of Science, Technology and Innovation (MOSTI) of Malaysia for their financial support.

References [1] O.Deshimaru. Deposition of crude oil in fish meat and its

detection. Bull. Jap. Soc. scient. Fish, PP. 297-301, 1971. [2] M.Ogata and Y.Miyake. Identification of substance in petroleum

causing objectable odour in fish, Water Res, PP.1493-1504, 1973. [3] T.Sudo. Test method of volatile organic substance in industrial

waste, Report of Institute of Hygiene. Mie Prefecture, pp.150-155,

1965. [4] S.Syahrullail, C.S.N.Azwadi and C.I.Tiong. The Metal Flow

Evaluation of Billet Extruded with RBD Palm Stearin, (2011) International Review of Mechanical Engineering (IREME), 5(1): pp. 21-27.

[5] H.Wagner, R.Luther, T.Mang. Lubricant base fluids based on renewable raw materials: their catalytic manufacture and modification. Appl Catal A: General; 221, PP.429–42, 2001

[6] B.Krzan and Vizintin. J. Tribological properties of an environmentally adopted universal tractor transmission oil based on vegetable oil. Tribology Int,36:827-833. 2003

[7] A. Adhvaryu, Z. S. Liu. Synthesis of Novel Alkoxylated Triacylgycerols and Thier lubricant base Oil properties. Industrial crops and products,21(1): 113-119. 2005

[8] Hui YH, editor. Coconut oil. Bailey’s industrial oil and fat products. vol. 2, 5th ed. New York: Wiley;. p. 97–123 [chapter 2], 1996.

[9] A. Zeman, A. Sprengel, D. Niedermeier, M. Spath. Biodegradable lubricants—studies on thermo-oxidation of metal-working and hydraulic fluids by differential scanning calorimetry (DSC);, vol. 268, p. 9–15, 1995.

[10] K. Cheenkachorn and I. Udornthep. A Development of Four-stroke Engine Oil Using Palm Oil as a Base Stock. The 2nd SEE 2006, C-026 (O), Bangkok, Thailand, , November 2006.

[11] I. Gawrilow. Palm oil usage in lubricants. 3rd Global Oils and Fats Business Forum U S A, October, pp. 3–19. 2003

[12] E.O. Aluyor and M. Ori-Jesu, “The use of antioxidants in vegetable oils – A review. A frican Journal of Biotechnology. Vol. 7 (25), pp. 4836-4842, 2008

[13] A. Adhvaryu, G. Biresaw, B.K. Sharma, and S. Z. Erhan. Friction Behavior of Some Seed Oils: Biobased Lubricant Applications. Ind. Eng. Chem. Res. 45, pp. 3735-3740, 2006

[14] R. Sh. Kuliev, F. R. Shirinov, and F. A. Kuliev, .Vegetable oils as a component of lubricant base stocks. Chemistry and Technology of Fuels and Oils. Vol. 31, Nos. (1995) pp.3-4.

[15] N. H Jayadas and K. Prabhakaran, "Tribological evaluation of coconut oil as an environment-friendly lubricant," Tribology International, vol. 40, pp. 350-354, 2007.

[16] A.M. Liaquat, H.H. Masjuki, M.A. Kalam, A. Rasyidi. Experimental Analysis of Wear and Friction Characteristics of Jatropha Oil added Lubricants. Applied Mechanics and Materials Vols. 110-116 pp 914-919, 2012

[17] C.I. Tiong, Y. Azli, M.R. Abdul Kadir, S. Syahrullail. Tribological evaluation of refined, bleached and deodorized palm stearin using four-ball tribotester with different normal load. J Zhejiang Univ-Sci A (Appl Phys & Eng) 13(8), 2012.

[18] C.I. Tiong, A.K.M. Rafiq, Y. Azli, and S. Syahrullail. The Effect of Temperature on the Tribological Behavior of RBD Palm Stearin. Tribology Transactions, 55: 539-548, 2012.

[19] S.Syahrullail, K.Nakanishi and S.Kamitani. Investigation of the effect of frictional constraint with application of palm olein oil lubricant and paraffin oil lubricant on plastic deformation by plane strain extrusion. Journal of Japanese Society of Tribologist, 50(12), pp.877-885, 2005.

REPRINT



80

[20] H.H Masjuki, M.A. Maleque, A.Kubo and T. Nonaka. Palm oil and mineral oil based lubricants- their tribological and emission performance Tribology International; pp. 305-314, 1999

[21] I. Golshokouh, F.N. Ani and S.Syahrullail. Wear Resistance Evaluation of Palm Fatty Acid Distillate Using Four-ball Tribotester, The 4th International Meeting of Advances in Thermofluids - IMAT2011, Melaka, Malaysia, pp.1302-1309, 3-4 Oct 2011.

[22] M.A. Maleque, H.H. Masjuki and A.S.M.A. Haseeb. Effect of mechanical factors on tribological properties of palm oil methyl ester blended lubricant. Wear pp. 117-12, 52000.

[23] G. D. Boerlage, Four-Ball Testing Apparatus for Extreme-Pressure Lubricants. Engineering, 136, pp 46–47, 1933.

[24] The Oil Palm Worldwide, 2007. http://fedepalma.org/world.htm. [25] Malaysian Oil Palm Statistics 2008, Malaysian Palm Oil Board,

February, ISSN 1511-743X; MPOB website (econ. mpob.gov.my), 2009.

[26] J. W. van Gelder, Greasy Palms: European Buyers of Indonesian Palm Oil, Friends of the Earth, The Netherlands 2004.

[27] A.b. Gapor Md Top. Production and utilization of palm fatty acid distillate (PFAD). Lipid Technology January, Vol. 22, No. 1, 2010

[28] S. Chongkhong, C. Tongurai, P. Chetpattananondh, C. Bunyakan. Biodiesel production by esterification of palm fatty acid distillate. Biomass and Bioenergy 31, 563–568, 2007

[29] Y. Wan, L. Cao and Q. Xuet. Friction and wear characteristics of ZDDP in the sliding of steel against aluminum alloy Tribol Int; 30, 767–772, 1997

[30] Munson, B.R., Young, D.F. and Okiishi, T.H. Fundamentals of fluid mechanics, 5th edition, John Wiley & Sons, Inc.2006.

[31] N. Sharma. The Jatropha experience: Andra Pradesh. In:Singh B, Swaminathan R, Ponraj V, editors. Biodiesel Conference towards energy Independence - focus on Jatropha; 9e10 June 2006; Rashtrapati Nilayam, Bolaram, Hyderabad. New Delhi: Rashtrapati Bhawan, p. 9e15; 2006.

[32] W. Piekoszewski, M. Szczerek, W. Tuszynski. The action of lubricants under extreme pressure conditions in a modified four-ball tester, Wear 249 (188–193, 2001

[33] A. Bhattacharya, T. Singh, and V. K. Verma .The Role of Certain Substituted 2-Amino-benzothiazolylbenzoylthiocarbamide as Additives in Extreme Pressure Lubrication of Steel Bearing Balls. Wear, 136, pp 345–357, 1990

[34] T. B. Lane.The Flash Temperature Parameter: A Criterion for Assessing E.P. Performance in the Four-Ball Machine. Journal of the Institute of Petroleum, 43, pp 181–184. 1957.

[35] M. Husnawan, M. G Saifullah, and H. H Masjuki. Development of Friction Force Model for Mineral Oil Basestock Containing Palm Olein and Antiwear Additive. Tribology International, 40, pp 74–81. 2007.

[36] J. M. Thorp. Four-Ball Assessment of Deep Drawing Oils. Wear,33, pp 93–108. 1975.

[37] T.B. Lane. The flash temperature parameter: a criterion for assessing E.P. performance in the four-ball machine J. Inst. Petrol; 43 18,11957

[38] S.M. Hafis, M.J.M. Ridzuan, R.N. Farahana, Amran Ayob and S. Syahrullail. Paraffinic mineral oil lubrication for cold forward extrusion: Effect of lubricant quantity and friction. Tribology International, 60:111-115, 2013.

[39] M. Farooq, A. Ramli, S. Gul, and N. Muhammad.The Study of Wear Behavior of 12-Hydroxystearic Acid in Vegetable Oils. Journal of Applied Sciences, 11(7), pp 1381–1385, 2011

[40] M Jones,. H. and Scoot, D. The Practical Aspectsof Friction, Lubrication and Wear, Elsevier Science Publishing Company. Industrial Tribology,New York,1983.

[41] J. Williams. Engineering Tribology, Cambridge University Press: Cambridge, UK .2005

[42] M.A.A. Hasagaya, M.N.M. Jaafar, M.S.A. Ishak. Investigation of Oil Burner Combustion Performance when utilizing Palm Biodiesel Blends, (2011) International Review of Mechanical Engineering (IREME), 5(3), pp. 548-552.

Authors’ information 1Faculty of Mechanical Engineering, Universiti Teknologi Malaysia, 81310 UTM Skudai, Johor, Malaysia.

2Department of Mechanical Engineering, Faculty of Engineering, University of Malaya, 50603 Kuala Lumpur, Malaysia.

Iman Golshokouh received her B.Sc. and M.Sc. degree from Department of Mechanical Engineering from Khuzestan Azad University, Iran, in 1993 and 1996, respectively. Then he served as an associate lecturer in the same Dept. for 2 years. He is now a Ph.D. candidate in the Faculty of Mechanical Engineering, Universiti Teknologi Malaysia (UTM), Malaysia.

Syahrullail Samion obtained his Ph.D., M.Eng. and B.Eng. from Kagoshima University, Japan, in 2007, 2002, 2000 respectively. He is currently a Lecturer at Department of Thermo Fluids in the Faculty of Mechanical Engineering in Universiti Teknologi Malaysia. His research interests are tribology in metal forming, bio-lubricant, palm oil and fluid mechanics.

Farid Nasir Ani obtained his Ph.D. in 1990 from University of Leeds, United Kingdom, and B.Sc. in 1984 in the faculty of Mechanical Engineering from University of Glasgow, Scotland, UK and his M.Sc. in Thermodynamics and Related Studies from University of Birmingham, UK. He is currently a professor at Faculty of Mechanical Engineering, Universiti

Teknologi Malaysia (UTM), Malaysia. His main research interests are in Thermochemical Conversion of Carboneceous Solid Wastes Combustion, Gasification and Pyrolysis of Biomass.

Masjuki Hassan obtained his Mechanical Engineering degree (B.Sc), at Leeds University, Leeds U.K. in 1977. He continued to pursue his M.Sc. in Tribology and Ph.D. from the same university and graduated in 1978 and 1982 respectively. Upon the completion of his studies, he was being appointed as a lecturer in 1983 at University of Malaya. He is currently appointed

as the Professor at Mechanical Engineering Department, University of Malaya. He is also one of the senate members of University of Malaya and secretary of Council of National Professors- Engineering and Technology cluster. He is the founding President of Malaysian Tribology Society (MyTRIBOS) and the Director of the Centre for Energy Sciences. REPRIN

T

International Review of Mechanical Engineering (IREME)

(continued from outside front cover)

Effect of Geometric and Operating Parameters on Performance of Helical Coiled Tube Heat Exchanger by Pramod S. Purandare, Mandar M. Lele, Rajkumar Gupta

105

Optimization of Wire Electrical Discharge Machining of Hybrid Metal Matrix Composite Material by S. Ramesh, N. Natarajan

110

Determination of Optimum Parameters in Turning of Aluminium Hybrid Composites by P. Suresh, K. Marimuthu, S. Ranganathan

115

Acoustic Modelling of Perforated Tube Mufflers with Experimental Analysis in Automotive Engines by G. Mylsami, N. Nedunchezhian

126

Effect of Heating Rate on Microstructure and Properties of the Iron-Chromium Reinforced with Alumina Particle Produced via Microwave Sintering by W. Rahman,, J. B. Shamsul, M. N. Mazlee

134

Modeling of a Natural Convection Flow Plume - Thermosiphon Interaction by Z. Yahya, Ch. Mbow, A. O. M. Mahmoud, M. L. Sow

140

Design and Construction of an Underwater Robot Based Fuzzy Logic Controller by Ali Jebelli, Mustapha C. E. Yagoub, Ruzairi bin HJ. Abdul Rahim, Hossein Kazemi

147

Analysis and Optimization of Grasping Force in the Case of Multi-Robots Cooperation by A. Khadraoui, C. Mahfoudi, A. Zaatri, K. Djouani

154

The Relationship of Na2SiO3/NaOH Ratio, Kaolin/Alkaline Activator Ratio and Sand/Kaolin Ratio to the Strength of Kaolin-Based Non Load Bearing Geopolymer Brick by M. T. Muhammad Faheem, A. M. Mustafa Al Bakri, H. Kamarudin, C. M. Ruzaidi, M. Binhussain, A. M. Izzat

161

A Review on Thermal Behavior Aspects of Nickel-Tungsten Alloy Coating by U. Arunachalam, P. Veeramani, N. Shenbaga Vinnayaga Moorthi

167

The Effect of Sintering Temperature on Mechanical Properties of Al/SiC Composites by A. B. Sanuddin, H. Azmi, M. S. Hussin, K. L. Chuan, Z. A. Zailani, M. F. M. A. Hamzas

176

Numerical Simulations of a Aluminium Microchannel Condenser for Household Air Conditioner by Vijay W. Bhatkar, V. M. Kriplani, G. K. Awari

181

Analytical and Experimental Investigation on Cutting Temperature in Turning AISI 304 Austenitic Stainless Steel Using AlTiCrN Coated Carbide Insert by Atul P. Kulkarni, Girish G. Joshi, Amit Karekar, Vikas G. Sargade

189

Modelling and Experimentation of Heat Exchanges in a Building with Double Envelope and Straws Bullets by M. Tabarki, S. Ben Mabrouk

198

Transient Free Convective Conjugate Heat Transfer from a Vertical Slender Hollow Cylinder by H. P. Rani, G. Janardhana Reddy

207

(continued on outside back cover) Abstracting and Indexing Information:

Cambridge Scientific Abstracts (CSA/CIG) Academic Search Complete (EBSCO Information Services) Elsevier Bibliographic Database SCOPUS Index Copernicus (Journal Master List): Impact Factor 6.46

Autorizzazione del Tribunale di Napoli n. 6 del 17/01/2007

REPRINT

(continued from inside back cover)

Numerical Investigation of Falling Film Thickness Over Horizontal Tubes by N. U. Korde, A. T. Pise, Rahul H. Salunkhe

217

Flow Model of Pure Water in a Pipeline by A. Elaoud, , S. Chehaibi, M. Ben Amor, E. Hajtaieb

224

Two-Phase Flow in Micro-Channel Heat Sink Review Paper by Ahmed Jassim Shkarah, Mohd Yusoff Bin Sulaiman, Md Razali bin Hj Ayob

231

Numerical Modeling of the Plume - Thermosiphon Interaction in a Vertical Cylinder: Effect of Vertical Displacement of the Heat Source by Z. Yahya, Ch. Mbow, A. O. M. Mahmoud, M. L. Sow

238

Finite Element Analysis and Modeling of Mems Pressure Sensor for Intraocular Pressure by S. Sathyanarayanan, A. Vimala Juliet

243

CFD Analysis of Turbulent Flow Over Centrifugal Pump’s Impeller of Various Designs and Comparison of Numerical Results for Various Models by Rajiv Kaul, S. N. Sapali

248

EXTRACTED BY ICOME 2012 VIRTUAL FORUM – 3RD INTERNATIONAL CONFERENCE ON MECHANICAL ENGINEERING

Investigation About Stress Intensity and Load Confrontation of Axially Cracked ASME Based Pressure Vessel by A. M. Senthil Anbazhagan, M. Dev Anand

261

1970-8734(201301)7:1;1-S

REPRINT

international review of mechanical engineeringsyahruls/publication/2013/7 ireme iman.pdf · ali...

Documents