ABSTRACT
The journal bearing demonstration rig is an apparatus which is used to study how pressure
would vary around the section of a journal bearing at various speed of the shaft and loading
conditions. The design of the journal bearing was done by the use of standard design
procedures carefully stated within this work. The frame, the journal bearing, the journal shaft,
the base plate and all relevant components of the apparatus were designed. Other parts not
constructed were procured. The fabrication and construction processes were carried out in the
workshop. The shaft to be used was machined on the lathe machine to the design
specification. So also was the bearing to be used. This was all explicitly discussed in this
report. Frame construction was carried out by welding process also stated in the work. The
spring damper support was another constructed part. The assembly was done in such a way
that the eccentricity between the bearing and the shaft would exist so as to get results.
Relevant formulas, derivation and equation models were used in carrying out calculations
used to get mathematical results that can be used to compare the experimental results. It is
observed in the graph plotted from the experimental results, that the speed is proportionally or
linear to the pressure build up in the journal bearing. The pressure tapping (h5), shows the
highest reading on the manometer board, ranging from 76cm for 1144rpm to 25cm for
572rpm due to eccentricity of the two centers (shaft and journal bearing).
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TABLE OF CONTENT
Title page ……………………………………………………………………… i
Certification page ……………………………………………………………… ii
Dedication …………………………………………………………………….. iii
Acknowledgment ………………………………………………………………. iv
Abstract ………………………………………………………………………… v
Table of content ……………………………………………………………… vi
List of figures ………………………………………………………………… x
List of tables ………………………………………………………………… xi
CHAPTER ONE
1.1Introduction………………………………………………………………………………………1
1.2 Historical background……………………………………………………… 3
1.3 Research problem………………………………………………………….. 5
1.4 Aims and objectives of this project………………………………………… 6
1.5 Scope of this project……………………………………………………….. 6
CHAPTER TWO
2.1 Literature review …………………………………………………………. ..7
2.2 Theoretical background……………………………………………………10
2.2.1 Basics of bearings……………………………………………………….10
2.2.2 Classification of bearings ………………………………………………10
2.2.3 Hydrodynamic lubricated bearings…………………………………….11
2.2.4 Terms used in hydrodynamic journal bearing……………………………12
2.2.5 Assumptions in Hydrodynamic Lubricated bearings ……………………14
2.2.6 Important factors for thick oil film……………………………… ………14
2.2.7 Properties of bearing materials…………………………………… ………15
2.3 Basic principle of Journal bearing ………………………………………..18
2.4 Working principle of journal bearing ……………………………………..19
2.5 Applications of Journal bearings…………………………………………. .20
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CHAPTER THREE
DESIGN AND CONSTRUCTION OF THE JOURNAL BEARING
DEMONSTRATION RIG, AND EQUATION MODELS OF VARIOUS
PARTS
3.1 Design of components…………………………………………………… .21
3.1.1 The journal shaft………………………………………………………..21
3.1.1.1 Shaft analysis………………………………………………………….21
3.1.1.2 Design………………………………………………… ……………..23
3.1.1.3 Dimensions……………………………………………… ……………..24
3.1.1.4 Construction…………………………………………. ……………..24
3.1.2 The journal bearing…………………………………………………… 25
3.1.2.1 The design calculation………………………………………………….25
3.1.2.2 Dimensions…………………………………………….. …….……….31
3.1.2.3 Construction…………………………………………. …….……….32
3.1.3 The frame……………………………………………………… ………32
3.1.3.1 Design……………………………………………….. ………………33
3.1.3.2 Dimensions…………………………………………….. ………………33
3.1.3Construction………………………………………………………………34
3.1.4 The Base plate………………………………………………….. ………….35
3.1.4.1 Design……………………………………….……….. ……………..35
3.1.4.2 Dimensions……………………………………………………………………..35
3.1.4.3 Construction…………….….…………………………. …………….35
3.1.5 Electric motor ………………….….……………………………………..36
3.1.5.1 Specification ……………………………………………………………37
3.1.5.2 Reason for selection……………………………………. ……………37
3.1.6 Coupling………………………………………………………….. ……..38
3.1.6.1 Reason for selection …………………………………………………38
3.1.7 Oil pipes/tubes …………………………………………………………38
3.1.7.1 Reason for selection ……………………………………………………….39
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3.1.8 Fasteners …………………………………………………………………39
3.1.8.1 Functions ………………………………………………………………39
3.1.9 Lubricant (oil)………………………………………………………….40
3.1.9.1 Properties of lubricants ……………………………………………….40
3.1.9.2 Specification ………………………………………………………….42
3.1.9.3 Reason for selection…………………………………………………42
3.1.10 Oil collecting pan ……………………………………………………42
3.1.11 Oil reservoir/tank ………………………………………………………..42
3.1.12 Spring damper support ………………………………………………42
3.2 Design consideration and selection of materials ………………………….43
3.3 Assembly of the apparatus ………………………………………………43
3.4 Working principle of the journal bearing test rig …………………………46
3.5 Operating conditions ………………………………………………………46
3.6 Operating instructions ……………………………………………………46
3.7 Mathematical Models and Calculations…………………………………47
3.7.1 Bearing Characteristics number for journal bearing ………………………48
3.7.2 Critical pressure of the journal bearing ……………………………………48
3.7.3 Sommerfeld number …………………………………………………….49
3.7.4 Heat generated in a journal bearing …………………………………….49
3.7.5 Heat dissipated by the journal bearing ………………………………….50
3.7.6 Calculation on pressure head ……………………………………………..51
3.7.7 Derivation of Sommerfeld’s and Reynold’s equation ………………….51
3.7.8 Derivation of Petroff’s equation ……………………………………………..56
CHAPTER FOUR
DISCUSION OF RESULTS, MAINTENANCE INSTRUCTION, SAFETY
PRECAUTIONS AND STORAGE
4.1 Discussion of results..……………………………………………………61
4.2 Maintenance instruction..…..……………………………………………61
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4.3 Safety precautions …………………………………………………………62
4.4 Storage ……………………………………………………………………63
CHAPTER FIVE
PROJECT COST ANALYSIS, CHALLENGES, CONCLUSION AND
RECOMMENDATION
5.1 Project Cost Analysis………………………………………………………64
5.2 Challenges……………………………………………………………….66
5.3 Conclusion ……………………………………………………………………66
5.4 Recommendation………………………………………………………….67
REFERENCES …………………………………………………………………………………….69
APPENDIX A
APPENDIX B
APPENDIX C
APPENDIX D
APPENDIX E
APPENDIX F
APPENDIX G
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LIST OF FIGURES
Fig 2.1 Hydrodynamic Journal Bearing ………………………….………12
Fig 2.2 Journal Bearing During Operation…………………….…………18
Fig 2.3 Oil Film Pressure Distribution in Journal Bearing ………….…20
Fig 3.1 Construction of the journal….…………………………………24
Fig 3.2 Construction of the frame………………………………………33
Fig 3.3 Frame Construction ……………………………………………34
Fig 3.4 Base Plate Construction …………………………………………36
Fig 3.5 Electric Motor………………………………………………….37
Fig 3.6 Oil Pipes …………………………………………………………38
Fig 3.7 First Phase of Assembly ……………………………………….44
Fig 3.8 Second Phase of Assembly …………………………………….45
Fig 3.9 Third Phase of Assembly …………………………………………45
Fig 3.10 Schematic Diagram of a Journal Bearing …………..……………51
Fig 3.11 Plain Journal Bearing Clearance versus Theta ……..……………55
Fig 3.12 Concentric Journal bearing ………………………………………56
Fig 4.1 Graph of speed of rotation against the pressure build up………60
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LIST OF TABLES
Table 2.1 Bearing Material Properties………………………………………17
Table 3.1 Dimension of the shaft…………………………..……………….24
Table 3.2 Journal bearing operating value and parameter…………………26
Table 3.3 Oil Types and Viscosities at Various Temperatures…………….28
Table 3.4 Dimensions of the Journal Bearing…………………………….32
Table 3.5 Dimension of the Frame…………………………………………34
Table 3.6 Dimensions of the Base Plate…………………………………….35
Table 3.7 Specifications of the Electric Motor…………………………….37
Table 3.8 Specification of the Oil………………………………………….42
Table 4.1 Results that shows variation of speed against pressure………..59
Table 5.1 Cost analysis table……………………………………………65
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CHAPTER ONE
1.1 INTRODUCTION
Hydrodynamic journal bearings are typical critical power transmission
components that carry high loads in different machines. In machine design,
therefore, it is essential to know the true or expected operating conditions of the
bearings. These operating conditions can be studied both by experimental and
mathematical means, for example in test rig experiments, in field or laboratory
tests with engines and by calculation or simulation.
Numerous studies of the operating conditions of hydrodynamic journal
bearings have been made during the last decades. Still, the case is far from
closed. For example, there are a limited number of studies that carry out an indepth examination of the true operating conditions of bearings in true-scale
experiments. There is also a need for experimental studies to verify the
theoretical ones.
Fluid friction i.e. viscosity which exists in the lubricant being used is
studied alongside the pressure effect which is being generated in the bearing,
thus the effect of lubricants with different viscosities are considered.
A simple journal bearing consists of two rigid cylinders. The outer
cylinder (bearing) wraps the inner rotating journal (shaft). A lubricant fills the
small annular gap or clearance between the journal and the bearing. The amount
of eccentricity of the journal is related to the pressure that will be generated in
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the bearing to balance the radial load. The lubricant is supplied through a hole or
a groove and may or may not extend all around the journal. The pressure around
the journal is measured on various manometers by means of pressure pipe/tubes.
This is done at various speeds to get the relationship between speed and the
pressure.
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1.2 HISTORICAL BACKGROUND
In the late 1880s, experiments were being conducted on the lubrication of
bearing surfaces. The idea of “floating” a load on a film of oil grew from the
experiments of Beauchamp Tower and the theoretical work of Osborne
Reynolds.
Prior to the development of the pivoted shoe thrust bearing, marine
propulsion relied on a “horseshoe” bearing which consisted of several equally
spaced collars to share the load, each on a sector of a thrust plate. The parallel
surfaces rubbed, wore, and produced considerable friction. Design unit loads
were on the order of 40 psi. Comparison tests against a pivoted shoe thrust
bearing of equal capacity showed that the pivoted shoe thrust bearing, at only
1/4 the size, had 1/7 the area but operated successfully with only 1/10 the
frictional drag of the horseshoe bearing.
In 1896, inspired by the work of Osborne Reynolds, Albert Kingsbury
conceived and tested a pivoted shoe thrust bearing. According to Dr. Kingsbury,
the test bearings ran well. Small loads were applied first, on the order of 50 psi
(which was typical of ship propeller shaft unit loads at the time). The loads were
gradually increased, finally reaching 4000 psi, the speed being about 285 rpm.
In 1912, Albert Kingsbury was contracted by the Pennsylvania Water and
Power Company to apply his design in their hydroelectric plant at Holtwood,
PA. The existing roller bearings were causing extensive down times (several
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outages a year) for inspections, repair and replacement. The first hydrodynamic
pivoted shoe thrust bearing was installed in Unit 5 on June 22, 1912. At start-up
of the 12,000 kW units, the bearing wiped. In resolving the reason for failure,
much was learned about tolerances and finishes required for the hydrodynamic
bearings to operate. After properly finishing the runner and fitting the bearing,
the unit ran with continued good operation. This bearing, owing to its merit of
running 75 years with negligible wear under a load of 220 tons, was designated
by ASME as the 23rd International Historic Mechanical Engineering Landmark
on June 27, 1987.
Since then, there has been series of progressive research carried out on
bearings bringing to the advent of journal bearings which are not so different
from the bearings designed by Osborne Reynolds and Albert Kingsbury which
work on the same hydrodynamic lubrication system.
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1.3 RESEARCH PROBLEM
The operating conditions of hydrodynamic journal bearings can be
described by a set of tribological variables called key operating parameters. For
example, the load level of a hydrodynamic journal bearing is described by two
parameters: the specific load and the sliding speed. The key operating
parameters most directly related to the bearing lubricant-shaft contact are the oil
film temperature, oil film thickness and oil film pressure. These three key
parameters can be determined by experimental or mathematical means with
varying levels of complexity.
Until now, oil film pressure in hydrodynamic journal bearings has been
studied mainly by mathematical means, because the experimental determination
of oil film pressure has been a demanding or even an unfeasible task. Under real
operating conditions, there are typically many practicalities that complicate the
experimental determination of true oil film pressure in a certain point or at a
certain moment. The oil film may be extremely thin and therefore sensitive to
different disturbing factors, for example defects in geometry. In addition, the
level of the oil film pressure may be extremely high or have a high level of
dynamic variability.
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1.4 AIM AND OBJECTIVE OF THE PROJECT
The research into the construction and design of the journal bearing
apparatus has several reasons and purposes which need to be achieved and
justified.
The main aim of the study was to determine the oil film pressure in
hydrodynamic journal bearings carrying realistic loads. In addition, the
relationship between the oil film pressure and other key operating parameters of
journal bearings such as eccentricity and shaft speed was studied.
The study also included the determination of the relationship between the
speed of rotation of the shaft, the pressure around the journal bearing and the oil
thickness.
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