MONITORING GAS DISTRIBUTION PIPELINES A thesis submitted to the University of Manchester for the degree of Doctor of Philosophy in the Faculty of Science and Engineering 2017 Linan Tao School of Electrical and Electronic Engineering
MONITORING GAS DISTRIBUTION
PIPELINES
A thesis submitted to the University of Manchester
for the degree of Doctor of Philosophy
in the Faculty of Science and Engineering
2017
Linan Tao
School of Electrical and Electronic Engineering
Contents
List of Figures 10
Abstract 16
Declaration 17
Copyright Statement 18
Publications 19
Acknowledgments 20
Glossary 23
1 Introduction 29
1.1 General introduction . . . . . . . . . . . . . . . . . . . . . . . . . . . . 29
1.2 Introduction to APR technique . . . . . . . . . . . . . . . . . . . . . . 30
1.3 Aims, objectives and contributions . . . . . . . . . . . . . . . . . . . . 31
1.3.1 Thesis aims and objectives . . . . . . . . . . . . . . . . . . . . . 31
1.3.2 Thesis contributions . . . . . . . . . . . . . . . . . . . . . . . . 32
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1.4 Layout of the thesis . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 37
1.5 Summary . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 38
2 Defects Detection in the Pipeline System 39
2.1 Defects in the pipeline system . . . . . . . . . . . . . . . . . . . . . . . 39
2.2 Defect detection methods . . . . . . . . . . . . . . . . . . . . . . . . . . 41
2.2.1 CCTV method . . . . . . . . . . . . . . . . . . . . . . . . . . . 42
2.2.2 Cross-correlation method . . . . . . . . . . . . . . . . . . . . . . 43
2.2.3 Pressure transients method . . . . . . . . . . . . . . . . . . . . 45
2.2.4 APR based detection method . . . . . . . . . . . . . . . . . . . 46
2.2.5 Comparison among different detection methods . . . . . . . . . 48
2.3 Summary . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 49
3 Literature Review 50
3.1 Uses of APR . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 50
3.1.1 Seismic surveys . . . . . . . . . . . . . . . . . . . . . . . . . . . 50
3.1.2 Medical application . . . . . . . . . . . . . . . . . . . . . . . . . 52
3.1.3 Musical instrument bore reconstruction . . . . . . . . . . . . . . 54
3.1.4 Detection of features and defects in pipelines . . . . . . . . . . . 55
3.1.5 Detection of features and defects in small bore tuning . . . . . . 58
3.2 Reviews on approximation models . . . . . . . . . . . . . . . . . . . . . 59
3.2.1 Model equations . . . . . . . . . . . . . . . . . . . . . . . . . . 59
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3.2.2 Zwikker and Kosten approximation . . . . . . . . . . . . . . . . 60
3.2.3 Kirchhoff approximation . . . . . . . . . . . . . . . . . . . . . . 61
3.2.4 Keefe approximation . . . . . . . . . . . . . . . . . . . . . . . . 63
3.2.5 Comparisons among different approximation models . . . . . . . 67
3.3 Reviews on numerical simulation models . . . . . . . . . . . . . . . . . 68
3.3.1 Finite Difference Time Domain Model . . . . . . . . . . . . . . 68
3.3.2 Layer peeling Model . . . . . . . . . . . . . . . . . . . . . . . . 70
3.3.3 Summary of the two models . . . . . . . . . . . . . . . . . . . . 71
3.4 Summary . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 72
4 Attenuation of the Acoustic Wave 73
4.1 Related theory . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 73
4.1.1 Speed of sound . . . . . . . . . . . . . . . . . . . . . . . . . . . 73
4.1.2 Boundary of plane wave . . . . . . . . . . . . . . . . . . . . . . 75
4.1.3 Window function comparison . . . . . . . . . . . . . . . . . . . 78
4.2 Experiments validation . . . . . . . . . . . . . . . . . . . . . . . . . . . 82
4.2.1 Previous research results . . . . . . . . . . . . . . . . . . . . . . 82
4.2.2 Experimental apparatus . . . . . . . . . . . . . . . . . . . . . . 83
4.2.3 Analysis . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 87
4.3 Experimental results . . . . . . . . . . . . . . . . . . . . . . . . . . . . 90
4.3.1 Different length tests . . . . . . . . . . . . . . . . . . . . . . . . 90
4.3.2 Different diameters tests . . . . . . . . . . . . . . . . . . . . . . 98
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4.3.3 Different temperature tests . . . . . . . . . . . . . . . . . . . . . 98
4.4 Summary . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 100
5 Feature/Defects Characterisation 102
5.1 Method for the detection of the defects . . . . . . . . . . . . . . . . . . 102
5.1.1 Holes . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 104
5.1.2 Blockage and erosion . . . . . . . . . . . . . . . . . . . . . . . . 106
5.2 Experimental apparatus . . . . . . . . . . . . . . . . . . . . . . . . . . 108
5.2.1 Holes detection . . . . . . . . . . . . . . . . . . . . . . . . . . . 109
5.2.2 Erosion and blockage detection . . . . . . . . . . . . . . . . . . 111
5.3 Application to the real-world . . . . . . . . . . . . . . . . . . . . . . . . 113
5.4 Summary . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 115
6 Pipe Simulators and Experimental Validation 117
6.1 Background . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 117
6.2 The single pipeline simulator . . . . . . . . . . . . . . . . . . . . . . . . 119
6.2.1 Reflection and transmission coefficients . . . . . . . . . . . . . . 119
6.2.2 Digital waveguides . . . . . . . . . . . . . . . . . . . . . . . . . 121
6.2.3 The cylindrical model to build pipeline . . . . . . . . . . . . . . 122
6.2.4 Attenuation filter . . . . . . . . . . . . . . . . . . . . . . . . . . 125
6.3 The pipeline network simulator . . . . . . . . . . . . . . . . . . . . . . 127
6.3.1 Reflection and transmission coefficients at joints . . . . . . . . . 127
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6.3.2 The network model . . . . . . . . . . . . . . . . . . . . . . . . . 130
6.3.3 Summary of the pipe simulators . . . . . . . . . . . . . . . . . . 132
6.4 Laboratory validation of the single pipeline simulator . . . . . . . . . . 133
6.4.1 Experimental setup for single pipeline simulator . . . . . . . . . 133
6.4.2 Results and analysis . . . . . . . . . . . . . . . . . . . . . . . . 134
6.4.3 Further demonstration of experimental tests . . . . . . . . . . . 136
6.5 Laboratory validation of the network pipeline simulator . . . . . . . . . 143
6.5.1 Experimental setup for the network pipeline simulator . . . . . 143
6.5.2 Reflection and transmission coefficients validation tests . . . . . 143
6.5.3 Results and analytics . . . . . . . . . . . . . . . . . . . . . . . . 144
6.5.4 Network Pipeline simulator validation tests . . . . . . . . . . . . 146
6.6 Summary . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 153
7 Industrial Case Studies 154
7.1 A case study for an industrial pipeline - Case 1 . . . . . . . . . . . . . 154
7.1.1 Description of the test . . . . . . . . . . . . . . . . . . . . . . . 154
7.1.2 Results of the industrial testing . . . . . . . . . . . . . . . . . . 156
7.2 A case study for an industrial pipeline - Case 2 . . . . . . . . . . . . . 160
7.3 A case study for an industrial pipeline - Case 3 . . . . . . . . . . . . . 161
7.4 A case study for an industrial pipeline - Case 4 . . . . . . . . . . . . . 164
7.5 A case study for an industrial pipeline - Case 5 . . . . . . . . . . . . . 166
7.6 A case study for an industrial pipeline - Case 6 . . . . . . . . . . . . . 168
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7.7 Summary . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 170
8 Discussions, Conclusions and Future Work 171
8.1 Discussions . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 171
8.2 Conclusions . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 175
8.3 Future work . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 176
Bibliography 178
7
List of Tables
2.1 Comparison of Different Methods . . . . . . . . . . . . . . . . . . . . . 48
3.1 Review of Analytical Solutions to the Signal Propagation . . . . . . . . 68
4.1 Extrema: Bessel Functions of the First Kind . . . . . . . . . . . . . . . 76
4.2 Pipe Size vs Cut-frequency . . . . . . . . . . . . . . . . . . . . . . . . . 78
4.3 Comparison Among Different Window Functions . . . . . . . . . . . . . 80
4.4 Details of the Test Pipes . . . . . . . . . . . . . . . . . . . . . . . . . . 84
5.1 Details of the Features in the Test . . . . . . . . . . . . . . . . . . . . . 109
5.2 Hole Size Estimation Results . . . . . . . . . . . . . . . . . . . . . . . . 111
5.3 Hole Size Estimation Results (Short Pipes) . . . . . . . . . . . . . . . . 112
5.4 Erosion Size Estimation . . . . . . . . . . . . . . . . . . . . . . . . . . 113
5.5 Blockage Size Estimation . . . . . . . . . . . . . . . . . . . . . . . . . . 114
6.1 Test Rig Feature Table . . . . . . . . . . . . . . . . . . . . . . . . . . . 137
6.2 Equipment Used in the Tests . . . . . . . . . . . . . . . . . . . . . . . 143
6.3 Peak Values at Each Location . . . . . . . . . . . . . . . . . . . . . . . 145
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6.4 Errors Between the Simulation And Experiment Results . . . . . . . . 146
6.5 Locations That Caused Each Feature in Different Layouts . . . . . . . 149
7.1 Gas Composition . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 155
7.2 Maximum Detected Distances When Pressure = 6.1 MPa And Temper-
ature = 8.9◦C, with the Distances Measured in Meter . . . . . . . . . . 159
7.3 Features in Layout of Trial Haylie Gardens . . . . . . . . . . . . . . . . 164
7.4 Features in Layout of Trial Newmains Rd, Renfrew . . . . . . . . . . . 166
7.5 Features in Layout of Trial Harburn Ave . . . . . . . . . . . . . . . . . 169
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List of Figures
1.1 The Schematic Diagram of APR [5] . . . . . . . . . . . . . . . . . . . . 30
1.2 Response of a Straight Pipe . . . . . . . . . . . . . . . . . . . . . . . . 33
1.3 Response of a Pipe with Diameter Changes . . . . . . . . . . . . . . . 34
1.4 The Response of a Pipe with Cross-sectional Changes . . . . . . . . . . 35
1.5 The Response of a Pipe with a Blockage Defect . . . . . . . . . . . . . 36
1.6 The Comparison Between Simulated And Recorded Results . . . . . . . 36
2.1 Gas Hydrate . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 40
2.2 Schematic View of a Cleaning Pig . . . . . . . . . . . . . . . . . . . . . 41
2.3 A Diagram of the Optical Detection Method . . . . . . . . . . . . . . . 43
2.4 Setup for Cross-correlation Method . . . . . . . . . . . . . . . . . . . . 44
2.5 Diagram of Cross-correlation Method . . . . . . . . . . . . . . . . . . . 44
2.6 Acoustic Ranger . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 46
3.1 Applications of APR History . . . . . . . . . . . . . . . . . . . . . . . . 51
3.2 Schematic Diagram for Medical Application . . . . . . . . . . . . . . . 53
3.3 Interleaved Grids of Pressure And Velocity . . . . . . . . . . . . . . . . 69
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3.4 The Schematic Diagram of Setup . . . . . . . . . . . . . . . . . . . . . 70
4.1 Acoustic Modes in a Cylindrical Pipe . . . . . . . . . . . . . . . . . . . 76
4.2 Kichhoff Attenuation Restrictions . . . . . . . . . . . . . . . . . . . . . 79
4.3 Rectangular Window . . . . . . . . . . . . . . . . . . . . . . . . . . . . 80
4.4 Bartlett Window . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 81
4.5 Hamming Window . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 81
4.6 Hanning Window . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 82
4.7 The Set up of the Experiment in the Lab . . . . . . . . . . . . . . . . . 85
4.8 Coiled Pipes for the Experiments . . . . . . . . . . . . . . . . . . . . . 86
4.9 Data Transmission Order of the Test System . . . . . . . . . . . . . . . 86
4.10 RMS Value and Peak Value . . . . . . . . . . . . . . . . . . . . . . . . 89
4.11 50 m Pipe Attenuation Results When D = 39.8 mm . . . . . . . . . . 91
4.12 Error Results When D = 39.8 mm . . . . . . . . . . . . . . . . . . . . . 91
4.13 Error Results of RMS Value . . . . . . . . . . . . . . . . . . . . . . . . 92
4.14 Attenuation Results When D = 25 mm . . . . . . . . . . . . . . . . . . 92
4.15 Error When D = 25 mm . . . . . . . . . . . . . . . . . . . . . . . . . . 93
4.16 Attenuation Results When D = 15.17 mm . . . . . . . . . . . . . . . . 93
4.17 Error When D = 15.17 mm . . . . . . . . . . . . . . . . . . . . . . . . 94
4.18 Attenuation Results When D = 39.8 mm . . . . . . . . . . . . . . . . . 94
4.19 Attenuation Results When D = 25 mm . . . . . . . . . . . . . . . . . . 95
4.20 Attenuation Results When D = 15.17 mm . . . . . . . . . . . . . . . . 95
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4.21 175 m Pipe Recordings When D = 39.8 mm and f = 500 Hz . . . . . . 97
4.22 175 m Pipe Recordings When D = 39.8 mm and f = 1500 Hz . . . . . 97
4.23 Attenuation Results for Different Size of Pipes . . . . . . . . . . . . . . 98
4.24 Attenuation Changes When the Temperature Changes . . . . . . . . . 99
4.25 Temperature Gradient Model . . . . . . . . . . . . . . . . . . . . . . . 99
5.1 (a) Clean Pipe (b) A Hole Defect in the Pipe (c) An Erosion Defect in
the Pipe (d) A Blockage Defect in the Pipe . . . . . . . . . . . . . . . . 103
5.2 Test Rig . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 110
5.3 A Reflection Signal Caused by a Hole in the Pipeline . . . . . . . . . . 111
5.4 A Reflection Caused by a 300 mm Erosion in the Pipeline . . . . . . . 112
5.5 50 mm Blockage . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 113
5.6 Illustrated Pipeline with a Feature . . . . . . . . . . . . . . . . . . . . 114
6.1 Layout of a Pipe Network . . . . . . . . . . . . . . . . . . . . . . . . . 118
6.2 The Response of the Pipe Network . . . . . . . . . . . . . . . . . . . . 118
6.3 Pressure Transmission in a Pipeline Unit . . . . . . . . . . . . . . . . . 119
6.4 Waveguide Filter Structure . . . . . . . . . . . . . . . . . . . . . . . . 121
6.5 Discretizing a Pipeline . . . . . . . . . . . . . . . . . . . . . . . . . . . 123
6.6 Signal Propagating Along the Pipe . . . . . . . . . . . . . . . . . . . . 123
6.7 Space-time Diagram . . . . . . . . . . . . . . . . . . . . . . . . . . . . 124
6.8 Attenuation Comparison Between Kirchhoff’s And Keefe’s Equation . 125
6.9 Pipeline with Branches Discretization . . . . . . . . . . . . . . . . . . 128
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6.10 A Generic Y-piece-branch . . . . . . . . . . . . . . . . . . . . . . . . . 128
6.11 A Generic Pipeline Network . . . . . . . . . . . . . . . . . . . . . . . . 131
6.12 Signals Change at the Junction . . . . . . . . . . . . . . . . . . . . . . 131
6.13 Experimental Setup . . . . . . . . . . . . . . . . . . . . . . . . . . . . 133
6.14 Attenuation Results for Pipe with ID = 39.8 mm . . . . . . . . . . . . 135
6.15 Error Between the Simulation And Experiment Results . . . . . . . . . 135
6.16 Layout of the Prototype Hardware . . . . . . . . . . . . . . . . . . . . 136
6.17 Diagram of the Prototype System Used for Testing Air Filled Pipes . . 137
6.18 Layout of the 50 mm Pipework Used in Laboratory Testing; L1, L2 and
L4 Represent Pipe Feature Locations While L3 And L5 Are Open Ends,
All Lengths Are in meters . . . . . . . . . . . . . . . . . . . . . . . . . 137
6.19 Comparison Results Between Simulation Results And Experimental Re-
sults in Test 1 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 138
6.20 Comparison Results Between Simulation Results And Experimental Re-
sults in Test 2 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 139
6.21 Comparison Results between Simulation Results And Experimental Re-
sults in Test 3 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 140
6.22 Comparison Results Between Simulation Results And Experimental Re-
sults in Test 4 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 140
6.23 Comparison Results Between Simulation Results And Experimental Re-
sults in Test 5 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 141
6.24 Comparison Results Between Simulation Results And Experimental Re-
sults in Test 6 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 142
6.25 Pipe Layout A . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 144
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6.26 Pipe Layout B . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 145
6.27 Layouts of the Pipe Network Setup . . . . . . . . . . . . . . . . . . . . 146
6.28 Comparison Between Simulation And Experiment Results for Layout (a)148
6.29 Comparison Between Simulation And Experiment Results for Layout (b)148
6.30 Comparison Between Simulation And Experiment Results for Layout (c) 149
6.31 Comparison Between the Simulation And Experiment Results for a
Three-branches Pipeline . . . . . . . . . . . . . . . . . . . . . . . . . . 150
6.32 Layout of a Pipe Main Containing a Loop And a Branch . . . . . . . . 150
6.33 Comparison Between the Simulation And Experiment Results for the
Layout in Figure 6.32 . . . . . . . . . . . . . . . . . . . . . . . . . . . . 151
6.34 Layout of a Pipe Main with 4 Branches . . . . . . . . . . . . . . . . . . 152
6.35 Comparison Between the Simulation and Experiment Results for the
Pipe Main with the Layout Depicted in Figure 6.34 . . . . . . . . . . . 152
6.36 Comparison Between the Simulation and Experiment Results When a
Partial Blockage Was Located in a Pipeline Branch, as per the Layout
in Figure 6.34 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 153
7.1 Raw Data with the First Distinguished Feature . . . . . . . . . . . . . 156
7.2 Recovered Input Excitation Signal . . . . . . . . . . . . . . . . . . . . 157
7.3 Reflection Signals from the Pipeline . . . . . . . . . . . . . . . . . . . 158
7.4 A 50% Blockage Interpreted by the Simulator . . . . . . . . . . . . . . 158
7.5 Reflection From the End of the Pipe . . . . . . . . . . . . . . . . . . . 159
7.6 Layout of the Testing at Alba . . . . . . . . . . . . . . . . . . . . . . . 161
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7.7 Comparison Between the Simulation And Experiment Results . . . . . 161
7.8 Test Equipment . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 162
7.9 Layout of Trial Haylie Gardens . . . . . . . . . . . . . . . . . . . . . . 163
7.10 Impulse Response of Trial Haylie Gardens . . . . . . . . . . . . . . . . 164
7.11 Layout of Trial Newmains Rd . . . . . . . . . . . . . . . . . . . . . . . 165
7.12 Impulse Response of Trial Newmains Rd . . . . . . . . . . . . . . . . . 166
7.13 Layout of Trial Crocus Grove . . . . . . . . . . . . . . . . . . . . . . . 167
7.14 Impulse Response of Trial Crocus Grove . . . . . . . . . . . . . . . . . 168
7.15 Layout of Trial 31 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 169
7.16 Impulse Response of Trial 31 . . . . . . . . . . . . . . . . . . . . . . . . 170
15
AbstractPipelines are a vital tool for transporting materials, such as natural gas, oil, and water.However, in extreme circumstances, defects such as blockages and leakages can occur.To limit the economic loss and environmental consequences of such events, it is impor-tant that any defects can be detected and located at an early stage, preferably beforefailure occurs. Research at the University of Manchester has led to the development ofa tool that uses acoustic pulse reflectometry (APR) to locate and characterise defectsand features in tubes and pipes.
The work described in this thesis began with the modelling and validation of acousticattenuation in pipes. Previously published validation studies focused on short pipes(< 40 m) where high frequencies are dominant. The present work focuses on muchlonger pipelines where low frequencies play a much larger role. As such, comprehensivelaboratory experiments were conducted to measure the attenuation of acoustic signalsof varying frequencies in pipes with lengths of up to 200 m and inner diameters between15 mm and 39.8 mm. The results of these experiments showed that theoreticallyobtained attenuation functions fitted measured results to within 5%. This providedevidence to suggest that, in theory, APR could be applied to high-pressure gas pipelinesto detect full blockages with lengths of up to 100 km. This result was supported bythe successful application of the theory to a pipe with a distance exceeding 12 km.
A major weakness that restricts the deployment of APR technology is that even whenapplied to single pipes with only a few axial features, the results can be difficult tointerpret. To aid the interpretation of the recorded APR measurements, a numericalsimulator was developed, which was able to estimate the acoustic attenuation as ittravels inside a pipe. This simulator models the propagation of acoustic waves in acylindrical tube (waveguide) by considering the effects of both viscous and thermalattenuation, as well as changes in the internal cross section of the tube. The simulatordivides the tube into discrete cylindrical segments, each segment being characterised bya digital filter that defines transmission and attenuation. By comparing the expectedresults from the simulator with those obtained from the real system, defects, such aspartial blockages can be detected and located. The simulator’s ability to characterise arange of defects, such as different forms of blockage, holes and erosion was thoroughlyassessed utilising a number of pipes with lengths of up to 200 m and inner diameters of39.8 mm in the laboratory. These results showed that when there were no uncertaintiesin the pipe layout, the experimental and simulated results were consistent to withinapproximately 3%. As final validation of the simulator, it was applied to an industrialpipeline with a length of more than 12 km. The simulator was able to accuratelyestimate the attenuation of the acoustic signal in the pipe and was also able to locatea blockage within this pipe with an accuracy of less than 5 m.
The single pipe simulator was extended such that it was capable of modelling thebehaviour of acoustic signals in pipeline networks. This is important if APR is tobe applied to pipeline networks, such as those used for gas distribution. A networkmodel was used to build the pipe network simulator; the model considered time, axiallocation and branch number. To validate the accuracy of the pipe network simulator,a series of laboratory tests were conducted using different pipeline network layouts.Data collected from a series of field tests were also used to verify the accuracy of thepipe network simulator. These tests showed that the network simulator was able toaccurately detect and locate a number of features located within pipeline networks.The size of the pipes used in evaluating the simulator ranged from 50 mm to 200 mmwith lengths of 60 m to 400 m.
16
Declaration
No portion of the work referred to in the thesis has been submitted in support of an
application for another degree or qualification of this or any other university or other
institute of learning.
17
Copyright Statement
i. The author of this thesis (including any appendices and/or schedules to this thesis)
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18
Publications
1). Tao, L., Groves, K., Lennox, B. and Gardner, R. Characterisation of defects in pipe
systems using a newly developed tubular acoustic reflection simulator, Proceedings
of the 26th Leuven Conference on Noise and Vibration, Leuven, Belgium, 15–17
Semptember, (2014).
2). Tao, L., Groves, K. and Lennox, B. The simulation of acoustic wave propagation
within networked pipe systems development and experimental validation, The 22nd
International Congress on Sound and Vibration, Florence, Italy, 12–16 July, (2015).
19
Acknowledgments
I would like to express my sincere appreciation to Professor Barry Lennox for his su-
pervision during the past four years. Without his supervision and help, I would not
complete the whole PhD research and thesis. He did not only offer me the help for
research, but also offer me advice regarding career development. I really enjoyed work-
ing and learning with him. Without the support and encouragement from Professor
Lennox, I would not be able to work and write my thesis at the 4th year. I cannot
say thanks enough to him. He is my real role model no matter in the research filed or
daily life. What I learned from him will inspire me for the rest of my life.
I also would like to appreciate the help from Dr Keir Groves. Dr Groves offered a
lot of advice and suggestions to the construction of the simulator theoretically and
experimentally. Thanks a lot to Richard Gardner for his help in the attenuation test.
Besides, I am glad to work with Omar Aldughayem in the team. Without his help for
the setup in some tests, I would not complete all the tests in time.
Sincere appreciation must go to all control system centre lectures/professors, especially
Dr Zhengtao Ding, who encouraged me a lot during the whole PhD learning process
as my co-supervisor.
All my thanks go to my fellow colleagues, who accompanied me during the past 4
years, especially Shuai Wang, Harun Tugal, Salvador Pacheco Gutierrez and Chunyan
Wang. Also many thanks go to my friends in UK, my colleagues at Continental in
Germany and my families and friends in China for their encouragement and support.
Deepest appreciation to the Vice-president at the University of Manchester, without
the financial support from the PDS Award, I would not be able to accomplish my
20
21
study in UK.
I am glad working and living in Manchester. All the memories at the University of
Manchester would be the best in my life. Thanks again for all the people who helped,
loved and encouraged me during the past four years.
Glossary
Chapter 2
Symbol Meaning Units
L distance from feature to optical system m
A illuminated area m2
t time s
x1(t) signal recorded by sensor 1
x2(t) signal recorded by sensor 2
ω angular frequency radians/s
X1(jω) Fourier transform of signal x1(t)
X2(jω) Fourier transform of signal x2(t)
ρ12 correlation coefficient
R11(t) auto-correlation of signal x1(t)
R22(t) auto-correlation of signal x2(t)
R12(t) correlation of signal x1(t) and x2(t)
τm time delay s
c speed of sound m/s
d distance m
23
24
Chapter 3
Symbol Meaning Units
ω angular frequency radians/s
P (z, ω) acoustic pressure
V (z, ω) particle velocity
Z acoustic impedance
Y shunt admittance
a tube radius m
ν2 Prandtl number
η shear viscosity coefficient
rv, rt dimensionless parameter
ρ density kg/m3
c speed of sound m/s
s shear wave number
ρs mean density kg/m3
c0 =√γps/ρs undisturbed velocity of sound
µ absolute fluid viscosity
γ = Cp/Cv ratio of specific heats
Cp specific heat at constant pressure J/kg K
Cv specific heat at constant volume J/kg K
Γ = Γ′ + jΓ′′ propagation constant
Γ′ attenuation per unit distance in ξ direction
Γ′′ phase shift per unit distance in ξ direction
f frequency Hz
j =√−1 imaginary unit
Jn Bessel function of first kind of order n
k reduced frequency
n kind of polytropic constant
σ the square root of the Prandtl number
25
Chapter 3 (Continued ...)
ps mean pressure
s shear wave number
t time
µ shear viscosity N· s/m2
αc attenuation Neppers/m
Pr Prandtl number
κ thermal conductivity (W/m)K
α(ω) absorption coefficient
ϑp(ω) phase velocity
fs sampling frequency Hz
k(from (3.60)) time step s
h Position step m
p(z, t) pressure in time domain
v(z, t) velocity in time domain
S cross section are m2
26
Chapter 4
Symbol Meaning Units
ω angular frequency radians/s
η shear viscosity coefficient
ρ density kg/m3
c speed of sound m/s
K coefficient stiffness
p gas pressure
R molar gas constant J·mol−1· K−1
T absolute temperature K
M mass of gas kg/mol
ϑ = T − 273.15 temperature ◦C
µ absolute fluid viscosity
γ = Cp/Cv ratio of specific heats
Cp specific heat at constant pressure J/kg K
Cv specific heat at constant volume J/kg K
m circumferential wave mode
n radial mode
kz wave number
Jn Bessel function of first kind of order n
j′mn the extrema of Jm
f frequency Hz
R ID m
δν viscous acoustic boundary layer m
αp attenuation in experiment dB/m
α attenuation in theory dB/m
p1, p2 pressure signals recorded by two microphones
l12 length between the two microphones m
27
Chapter 5
Symbol Meaning Units
p0 amplitude of the reflected signal from end
p amplitude of the reflected signal
p1 amplitude of the input signal
D ID of tested pipe mm
a radius of the hole mm
λ wavelength mm
W pipe wall thickness mm
ρ density kg/m3
c speed of sound m/s
fc centre frequency Hz
L distance between the leak and the input m
L0 full length of the pipe m
α attenuation in theory dB/m
A cross section change mm2
l length of the defect mm
F function factor
pnoise noise level
M noise parameter
R diameter of pipe m
28
Chapter 6
Symbol Meaning Units
pi sound pressure
Ui particle velocity
a pipe radius m
c speed of sound m/s
D pipe diameter m
f frequency Hz
fs sampling frequency Hz
k wave number
l segment length m
Z acoustic impedance
A amplitude of input signal
B amplitude of reflection signal
p+i,i(nT ) pressure of the forward input signal at the ith segment
p−i,i(nT ) pressure of the backward input signal at the ith segment
p+i,o(nT ) pressure of the forward output signal at the ith segment
p−i,o(nT ) pressure of the backward output signal at the ith segment
p+i (nT ) pressure of the forward signal at the ith pipe branch
p−i (nT ) pressure of the backward signal at the ith pipe branch
si cross-section area m2
ri,j reflection coefficient from segment i to j
ti,j transmission coefficient from segment i to j
ri reflection coefficient at ith pipe branch
ti transmission coefficient at ith pipe branch
T = lfs
one-way travel time s
xi(nT ) attenuation filter in ith segment
α attenuation coefficient dB/m
αp experimental attenuation coefficient dB/m
γ(ω) complex wavenumber
Chapter 1
Introduction
This chapter introduces the background and motivation for this research that was com-
pleted in the area of Acoustic Pulse Reflectometry (APR). The aims, objectives and
contributions of the thesis are introduced. A roadmap of methodologies is presented
at the end of this chapter.
1.1 General introduction
Pipeline systems are invaluable tools, for both delivering utilities and facilitating in-
dustrial processes, such as transporting heating or cooling fluids. However, they often
operate in harsh environments and as such they are frequently subject to defects such
as holes, blockages and corrosion. To avoid the economic loss and environmental conse-
quences that these defects can cause, it is important that any defects can be detected,
located and characterised at an early stage, preferably before failure occurs. To de-
tect defects in pipelines, University of Manchester researchers have been using APR
based technique for several years [1–4]. APR technique is now becoming an established
technique for identifying, locating and characterising defects and features in tubular
systems.
29
CHAPTER 1. INTRODUCTION 30
1.2 Introduction to APR technique
The APR technique is based on measuring the acoustic signal resulting from the re-
flection and transmission of an acoustic signal from the input as it propagates along
the length of a tubular pipe. A schematic diagram of APR is shown in Figure 1.1. A
typical APR probe comprises a loudspeaker, an amplifier, (a) microphone(s), a source
tube and a data acquisition system. In an APR application test, a pulse, containing
a broad range of frequencies, is used as the injected acoustic signal. The signal is
defined using a computer and then transmitted by a digital-to-analog (D/A) converter
and amplifier to a loud speaker. The amplified signal is injected into the gas inside
the pipe and the reflected signal is recorded using the microphone, which is inserted
into the source tube. The injected pulse travels along the gas within the pipe and is
partially reflected back towards the excitation source whenever it encounters a change
in cross sectional area, which may be caused by the usage of a valve and the existence
of a blockage or a branch for example. The first change in cross sectional area in the
object tube leads to a reflection. To distinguish this reflection from the input signal,
a source tube is used. The reflected signal is stored in the computer after being con-
verted to a digital signal using an analog-to-digital (A/D) converter. As the acoustic
signal travels at the speed of sound inside the pipe, features and defects within a tube
can be characterised and located by analysing the recorded reflected signal.
COMPUTER
D/A A/D
AMPLIFIER
MICROPHONE
LOUDSPEAKER SOURCE TUBE OBJECT
Figure 1.1: The Schematic Diagram of APR [5]
CHAPTER 1. INTRODUCTION 31
1.3 Aims, objectives and contributions
1.3.1 Thesis aims and objectives
APR technique has been used by a lot of researchers to find defects in pipelines. Pre-
vious work has shown the challenge of interpreting the acoustic response of a pipeline
system, because even for a simple pipeline setup, the response can be relatively com-
plex. The research presented in this thesis aimed to develop a simulator to help
interpret results obtained when APR is used to locate and monitor pipeline defects.
The designed simulator was to serve as a reference regarding which APR data could
be compared to ease the interpretation of the measurements. To build the simulator,
modelling the attenuation played an important role in this process. In the meanwhile,
the characterisation of reflections caused by different features could help estimate the
defects identified by the simulator quickly.
The objectives of this PhD research project were the following.
• To fully review the importance of using pipeline monitoring systems to detect
and locate any unexpected defects.
• To understand how acoustic signals are attenuated in pipes and to identify which
theories have been developed to explain this.
• To use measurements obtained using APR to estimate the size of a defect de-
tected within a pipe or tube.
• To build a single pipe simulator to help interpret the results obtained using APR.
• To expand the single pipe simulator so that the acoustic response of a pipeline
network can be simulated.
• To validate and quantify the developed simulators using data from both labora-
tory experimental setups and industrial gas distribution pipeline systems.
• To determine the capability and limitations of using a simulator when applying
APR to real pipelines.
CHAPTER 1. INTRODUCTION 32
1.3.2 Thesis contributions
There has been a considerable amount of work investigating the attenuation of acoustic
signals in pipes and the use of APR as a tool for surveying such pipes. However, this
research has focused on relatively short lengths of small-bore pipes. For example, Lewis
provided experimental validation of the attenuation of acoustic signals in pipes with
lengths of 34.5 m and diameters of 50 mm [2]. Furthermore, work reported in [5–7]
demonstrated the successful use of APR in detecting holes in musical instruments.
APR is currently being considered as a tool for surveying the long lengths (tens or
even hundreds of kilometres) of offshore gas pipelines [4] and gas distribution networks
[8]. In contrast to the previous work, which has considered relatively short length of
pipes, this thesis mainly focuses on long and complex pipeline setups. The major
contributions of this study are presented below.
(1) Attenuation validation
The main target of the research is to build a pipeline simulator, how to describe the
attenuated signal is fundamental to build the simulator.
An example of the acoustic response measured from a straight length pipe is shown in
Figure 1.2. The acoustic signal is attenuated along the length of the pipe and is then
reflected by the closed end of the pipe. This reflected signal is subsequently attenuated
as it travels back to the loudspeaker and microphone. Hence the amplitude of the
reflected signal is less than that of the input signals. Attenuation theory, proposed by
Kirchoff [2, 9], is typically used to define acoustic attenuation in pipes. However, this
theory has only been validated over relatively short lengths of small-bore pipes. In
this study, Kirchoff’s theory was evaluated using a comprehensive set of experimental
tests with various lengths of pipe (75 m to 225 m) with diameters ranging from 15 mm
to 40 mm. Furthermore, the theory was evaluated using a broad range of frequencies
from 50 Hz to 2000 Hz and a variety of lengths of pipes from 50 m to 225 m. The
experimental work demonstrated that the theory matched the experimental results to
within approximately 5% in the frequency range of 50 Hz to 200 Hz, which is the main
frequency range of interest when APR is applied to long lengths of pipes.
CHAPTER 1. INTRODUCTION 33
Inp
ut
Res
po
nse
Time
(a) Pipe Layout
Input Impulse Reflected Impulse
(b) Recorded Response
Loudspeaker
Microphone
Pipe
Figure 1.2: Response of a Straight Pipe
(2) Feature detection and characterisation
The characterisation of features contained within an APR signature is fundamental to
determining the size of a defect within the pipe. For example, Figure 1.3 shows a pipe
containing a small reduction in diameter. The lower graph in Figure 1.3 shows the
response when APR is applied to this pipe. Two reflected features can be seen in the
APR response. The positive part of the first reflection is caused by the reduction in
pipe diameter and the negative part by the subsequent expansion of the pipe diameter.
The second reflection (end part in the plot) is caused by the end of pipe. Chapter 5
describes the work that was conducted using Morgan’s technique [10] to characterise
the size of defects based on the APR measurements. Compared to Morgan’s experi-
ments, a more thorough series of validation tests were performed on a group of pipes
with different sizes of features (e.g. hole, blockage, erosion) machined in the pipe.
The validation was in a more systematic method, which will offer a way to calculate
the size of features in the pipe. Experimental validations showed that the developed
techniques were able to provide accurate sizing of holes and other defects (such as the
length of a section of erosion). The size of the feature which can be detected by APR
is relevant to the length of the pipe and the Signal-to-Noise Ratio (SNR).
CHAPTER 1. INTRODUCTION 34
Inp
ut
Res
pon
se
(a) Pipe Layout
Microphone
Pipe
Input Impulse Reflected Impulse
(b) Recorded Response
Reflected features
Loudspeaker
Reduction
Time
Figure 1.3: Response of a Pipe with Diameter Changes
(3) Single pipe simulator
Based on the attenuation theory, how a signal is transmitted in a pipeline is modelled
by a pipe simulator.
A major goal for APR is for it to be used to detect and locate defects as they form
in pipes. For a pipe network, if the acoustic response of the pipe was measured and
recorded before and after the defect was formed, then the defect can be detected and
located by comparing the two responses. However, there are no procedures in place
for this type of test to be completed, nor are there any standards or expectations
of what information should be stored. Hence, when using APR to characterise a
defect, there will typically be no reference signal recorded prior to the defect forming.
Chapter 6 describes the development of a simulator that offers a means of estimating
the idealised response of a pipe for situations when no reference signature exists.
Although simulators have been developed before, the simulator in this thesis covers
a detection length of up to 12 km, which has never been applied by our researchers
before based on the author’s knowledge. The simulator can simulate the response of
a pipeline over any distance theoretically. However, the restriction for applications
lies in the SNR from the recorded signal. When the reflection signal from a defect
CHAPTER 1. INTRODUCTION 35
is under the level of the background noise, the simulation results will not help the
identification of the defect in the pipeline any more. Therefore, the application of
the APR for detecting defects along the pipeline is restricted to the SNR in the real
situation.
The pipes in Figures 1.2 and 1.3 can be characterised with relative ease as there are
very few reflections emanating from them. However, the system in Figure 1.4 is much
more challenging to survey because more reflections and re-reflections are produced
within the pipe. If a defect is present within the pipe, then as shown in Figure 1.5,
the reflected signal is so complex that it is difficult to detect it.
Inp
ut
Res
pon
se
Microphone
Pipe
Loudspeaker
(a) Pipe Layout
Input Impulse
Reflected Impulse
(b) Recorded Response
Reflected features
Time
Figure 1.4: The Response of a Pipe with Cross-sectional Changes
The benefit of the developed simulator is shown in Figure 1.6. In this figure the
response of the actual pipe is compared with that predicted by the simulator. A slight
difference between the two signals can be identified in Figure 1.6 and this difference is
the result of the defect, which can be readily detected with the use of the simulator.
In the research described in Chapter 5, both laboratory and industrial results were
used to determine the accuracy of the simulator. The industrial results validated the
accuracy and feasibility of the simulator when used to detect a blockage in a pipe with
CHAPTER 1. INTRODUCTION 36
a length of approximately 12 km and an inner diameter (ID) of 200 mm. Furthermore,
the single pipe simulator was used to predict the longest distance over which the APR
technique is likely to be capable of detecting defects in the presence of background
noise.
Microphone
Pipe
Loudspeaker
(a) Pipe Layout
Input Impulse
Reflected Impulse
(b) Recorded Response
Reflected features
Time
Inp
ut
Res
po
nse
Defect
Figure 1.5: The Response of a Pipe with a Blockage Defect
Time
Reference signal
Actual signal
Inp
ut
Res
po
nse
Figure 1.6: The Comparison Between Simulated And Recorded Results
CHAPTER 1. INTRODUCTION 37
(4) Network simulator
To expand the single pipe simulator so that a complex network can be modelled, a
network simulator is built.
Current work at the University of Manchester is exploring the use of APR to survey
pipeline networks. The acoustic signature of such networks is much more complicated
than for single lengths of pipe and to aid in the interpretation of APR signals, the
simulator was extended to provide estimates of the acoustic response of pipe networks.
The networked simulator used a network model to describe the complex connection
among different pipe branches, so that the pipeline network can be expressed in a
mathematical way. Experimental tests in the laboratory and using industrial mea-
surements were used to validate the accuracy of the simulator. The laboratory tests
consisted of a series of tests using pipe networks containing a single branch, multiple
branches, a loop, a loop with branches and a branch with a loop. Further evaluation
was performed using measurements collected from a number of on-site gas distribution
networks.
1.4 Layout of the thesis
There are seven chapters in this thesis. Following this introduction,
Chapter 2 reviews typical defects, such as holes, erosions and blockages, in the pipeline
and relevant detecting methods for respective defects.
Chapter 3 reviews APR and its applications discussed in the literature, identifies gaps
in research and explains where the research in this thesis fits in to existing technologies.
Some typical methods in this area are introduced and some promising methods are
detailed.
Chapter 4 introduces Kirchoff’s theoretical analysis of acoustic attenuation in pipes
and shows the results, which were obtained using experimental tests to determine the
accuracy of this theory. The validation tests were performed using a range of pipe
CHAPTER 1. INTRODUCTION 38
lengths with different internal diameters using a variety of frequencies. The chapter
compares the results of these tests with related facts published previously.
Chapter 5 characterises the defects (e.g. holes, blockages and erosion) in pipelines
based on equations proposed by Morgan [10]. The tests were performed on a set of
15 pipes with a range of features (e.g. holes, expansion and reduction of the pipe
diameters) in seamless tubes that were 5 m in length. The experiment results and
theoretical results were compared and the errors were analysed.
Chapter 6 describes the development of the single pipe simulator which approximates
the attenuation of acoustic signals along the length of a straight pipe and the pipe
network simulator which generates the response of a network system. The idealised
impulse response generated by the simulators were used to aid in the interpretation
of the recorded reflections by APR. The validation for the transmission and reflection
coefficients at T-pieces was discussed. A variety of laboratory tests were performed to
validate the simulator.
Chapter 7 presents the industrial cases as the application and validation the pipe
simulators introduced in Chapter 6. The industrial results were validated using the
designed simulators. All the industrial cases were used to determine the accuracy of
the simulators and to determine their capabilities.
Finally, Chapter 8 concludes this research and suggests future research directions.
1.5 Summary
Chapter 1 gave an overview about what motivated the author to conduct the research.
Because of the difficulty in interpreting APR data, it was essential that a simulator
was developed to aid the interpretation. Thesis contributions, objectives and aims
were also included in this chapter. Finally, a roadmap of each chapter was described.
Chapter 2
Defects Detection in the Pipeline
System
This chapter will describe some of the typical defects found in pipelines. Before moving
to the detailed introduction, a feature is defined as any anomaly in the pipe such as
joints, blockages, diameter change etc. and a defect is defined as a feature in the pipe
that should not be there or is undesired such as dents, blockages, holes, etc. The
effects of these defects are also introduced. There are many methods for detecting
defects in pipelines. Some typical detecting methods such as closed circuit television
(CCTV) and cross-correlation, are described in this chapter.
2.1 Defects in the pipeline system
According to the investigation conducted by Transportation Research Board (2004),
a pipeline is one of the safest ways to transport fluids [11]. However, the defects, i.e.
leakages, blockages, and erosion, exist along pipelines, which may lead to financial
losses, environmental damage and human injuries.
Leaks in the transport pipelines are causes for concern, as they may lead to severe
damages or accidents both environmentally and economically. In the worst case, the
pipe system could stop working because of the huge amount of leakage from the pipe.
39
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 40
For example, billions of dollars have been spent on the water loss from the leakage
of pipelines according to the White Paper from the United States (US) [12]. In some
underwater situations, contamination resulting from foreign objects may cause outage
of the system leading to expensive damage.
Erosion may occur inside the pipeline after some time under conditions (eg. corrosion
of the metal material) even with proper maintenance. When erosion occurs over a
period of time, this could lead to pits formatting in the pipe, which can lead to
leakage. Furthermore, erosion may occur both inside and outside of metal pipelines.
Some of them may cause severe damage to the transportation of gas or liquids.
Blockage is another major problem in the pipeline system. Deep water environments
were developed to produce more oil and gas energy to fulfil energy demand. However,
the high pressure and cold surroundings could lead to the blockage of pipelines with the
formation of hydrate [13]. In the underwater natural gas pipeline system, gas hydrates
can form because of the low temperature and high pressure [14]. For example, hydrates
are formed when the gas molecules contact come in water at a pressure of over 600 kPa
and a temperature under 300 K. The gas hydrate is a solid form of water that contains
gas molecules, e.g. CH4, C2H6 and CO2.
Figure 2.1: Gas Hydrate
In Figure 2.1, it illustrates that a full gas hydrate was formed, which caused the full
blockage of the pipeline [3]. This caused severe problem as no flow would pass the
hydrate. If the hydrate can be identified before it is fully formed into a blockage,
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 41
possible actions can be taken such as injecting an inhibitor, to decrease or diminish
the hydrate [15].
Normally cleaning pigs are used to clean the internal surface of pipes to reduce ac-
cumulation of blockages. As shown in Figure 2.2 [16], a cleaning pig is a cylindrical
plug and the flat disk cup is attached to the pig body. The flat disk cup can either
be conical or cylindrical. The cleaning pig is inserted in the pipe and moved along
by flowing fluids [17]. The fluid flow pressure forces the pig to remove the deposits.
The bypass port is used to control the velocity of the pig and to avoid the deposits
accumulating downstream. However, the pig may become stuck in the pipeline under
some circumstances, which causes a blockage in the pipeline.
Flow
deposits
Pig
body
Flat disk cup
Spacer
(rigid)
Bypass port
Figure 2.2: Schematic View of a Cleaning Pig
2.2 Defect detection methods
Defects detection in pipelines is an active topic in the research and industry area.
According to one study by Kristiansen [18], reliability, sensitivity, accuracy and ro-
bustness are the four standard requirements for a detection system.
There are two categories of pipeline monitoring methods, the non-technical and tech-
nical detection methods.
• Non-technical methods
The non-technical methods are those that do not use any equipment and only
rely on people or animal normal senses, such as seeing, hearing and smelling [19].
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 42
In some complicated circumstances, this is unrealistic, for example when the
pipelines are under water or beneath a building; in these circumstances, it is dif-
ficult to use normal senses. Hence, it is necessary to develop technical detection
methods.
• Technical methods
The technical methods are those relying on detection devices and equipment or
monitoring changes of the pipeline parameters, such as pressure or flow rate.
2.2.1 CCTV method
For optical detection, CCTV was used to monitor the inside feature of the pipelines [20]
in 2002. The CCTV-based method used optical sensors inside the pipe to monitor the
inner wall conditions. However, there were two limitations to this method: the interior
of the pipe lacked visibility, and it was sometimes difficult to have enough lighting to
obtain images. Based on the CCTV idea to monitor the inside of the pipe, a new
laser-based inspection system was proposed to inspect the inner surface wall of a pipe.
The location of defects could be detected by analysing the intensity of the projected
laser generated ring [21]. Furthermore, the intensity-based optical system proposed
by Safizadeh et al. consisted of a light ring projector, a pre-calibrated charge coupled
device (CCD) camera and an optical diffuser that was used to expand the laser beam
into a light ring. The schematic diagram is shown in Figure 2.3.
Parameter L is the distance from the location of the surface under investigation to the
optical system and A is the illuminated area. Both of the parameters can be calculated
based on the pipe radius and the diffuser projection angles [21]. A surface map of the
inside pipe wall was generated by extracting the intensity information existed in the
pipe images. The laser light rings were projected onto the pipe wall and the light
signals were received by a CCD camera. The light intensity from the projected rings
helped to identify defects in the pipeline. When defects occurred, the intensity in the
image changed because of the scattered laser light.
However, the optically based technology was restricted by the length of the pipe as it
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 43
L A
CCD
Laser
diode
Pipe
Ring
of
light
PC
Figure 2.3: A Diagram of the Optical Detection Method
was difficult to install optical sensors along a long pipeline and the limited range of
the optical sensor was also a problem. The system was only used for a test in a pipe
182 m long with an ID of 0.152 m. Pipes with longer length have not been verified
yet. Another restriction was that the intensity of the projected laser ring may not be
strong enough for the inspection.
2.2.2 Cross-correlation method
The Cross-correlation method [22–24] was developed as a key way to locate leaks
along pipelines. Figure 2.4 shows a typical arrangement for leak detection in a buried
pipe. Two access points around the suspected leaking point were required to install
sensors: either listening rods or hydrophones. Two sensors were used to record the
vibration of acoustic signals. The noise correlator computed the cross-correlation of
the two transmitted signals from sensors and transmitted the results to the operator.
For example, two sensors were attached to each side of the leak with the distances
of d1 and d2. The assumption for the pipe length was infinite so that no reflecting
discontinuities could affect the fluid-borne wave.
The process for the cross-correlation function is shown in Figure 2.5. The two recorded
signals x1(t) and x2(t) from two sensors were transformed using the Fourier transform
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 44
d1 d2
d
Sensor
x1(t)
Sensor
x2(t)Leak
Figure 2.4: Setup for Cross-correlation Method
operator to X1(jω) and X2(jω) respectively. The expected correlation result R12 was
the inverse Fourier transform of X∗1 (jω)X2(jω) with ∗ denoting conjugation. Normally
the cross-correlation function is expressed in the normalised form with a scale from -1
to 1. Equation (2.1) defines the correlation coefficient ρ12, where R11(0) and R22(0)
are the results of auto-correlation R11(t) and R22(t) when t = 0. The way to calculate
the correlation R12 of two signals x1(t) and x2(t) was expressed in Figure 2.5
ρ12(τ)
=R12
(τ)√
R11
(0)R22
(0) (2.1)
Fourier
Transform
Fourier
Transform
Inverse
Fourier
Transform
Sensor
x1(t)
Sensor
x2(t)
X1(jω)
X2(jω)
X1*(jω)X2(jω)
R12( )
Sensors inputs Implementation of cross-correlation
Figure 2.5: Diagram of Cross-correlation Method
If there was a leak between the two sensors, a distinguished change could be identified
in the cross-correlation function. The time delay τm could be calculated based on
the difference in arrival time between each sensor and c is the speed of sound being
transmitted in the pipe. With the layout in Figure 2.4,
d2 − d1 = cτm (2.2)
d2 + d1 = d (2.3)
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 45
The leak position can be calculated by substituting (2.3) for (2.2) , which is found to
be
d1 =d− cτm
2. (2.4)
There were several limitations to the cross-correlation method.
• The access point of the test sensors was sometimes difficult to find. Not all of
the tested pipeline systems were equipped with many access points for external
devices.
• The prediction of the location of the suspected leak was difficult and could require
extra effort.
• The assumption for the cross-correlation method was that the lengths of the
tested pipe were infinite. However, in practice, there are no infinite pipe systems
available.
• The accuracy of locating the leak was not verified. This method was found to
be accurate within 0.3 m to 0.6 m (one to two feet) according to the American
Water Works Association [25].
2.2.3 Pressure transients method
The pressure transient method [26, 27] was used to detect the existence of blockage
in the pipeline using the interaction between transients and blockages. The transient
was initially produced using inlet flow variation. This was achieved by momentarily
altering the rate of fluid incursion into the pipeline which kept transient propagating
in the pipe. When the transient reached the blockage, some portion would be reflected
and propagated upstream. The characteristics of this reflected transient, which were
monitored at the pipe inlet, gave the profile of pipeline internals. The monitored
signal then became a window for observing the pipelines interior. Sorely it gave a
pressure measurement which could be analysed to determine this profile. Numerical
tests showed that pipeline blockages could be detected from the reflected transients
up to a distance of 1.6 km. However, the detection in real condition would be difficult
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 46
because the transient amplitude was only 0.0005% of the base pressure. When too
much fluid was suddenly transmitted to the pipe, the rise of such pressure could cause
the pipe to rupture within a short period of time [27].
2.2.4 APR based detection method
APR based detection method is a non-destructive method for pipeline detection. In the
late 1970s, the Central Electricity Generating Board developed an acoustic instrument
named the Acoustic Ranger that was used to monitor the blockage and leakage of a
tube filled with fluid. The Acoustic Ranger was applied to short length and small bore
pipes [10, 28].
As shown in Figure 2.6, Acoustic Ranger used the pulse echo technique, which was
the fundamental application of APR in pipeline detection.
Source
TubeSeals
Microphone
Test Tube
Signal Generation
Circuit
Amplifier
Filter
Display
Loudspeaker
Figure 2.6: Acoustic Ranger
The initial acoustic ranger equipment was large because of actual size of transmitters
and receivers in 1970s. The transmitter (e.g. loudspeaker) and receiver (e.g. micro-
phone) were connected to one end of the pipe and an acoustic signal was injected,
and any discontinuity, e.g. changes of the pipe’s internal diameter or a hole would
cause an echo (reflection) that would be measured by the receiver and displayed in
the recordings. Because the sound wave was transmitted through the gas (e.g. air or
methane) in the pipe, the location of the discontinuity could be calculated using the
speed of sound inside the pipe and the time recorded by the receiver (usually shown
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 47
in the oscilloscope at that time).
The input impulse was generated by discharging a capacitor in the circuit which was
operated manually or repeatedly. The input sound from the signal generation circuit
was amplified by the loudspeaker mounted on one end of the source tube, which was
used to connect to the test pipe and helped to separate the input signal and reflected
signal. The source tube was required to have the same internal diameter as the test
tube with a length of 3 m in operation [10] and to connect to the test tube with air
tight seals. The microphone was located close to the loudspeaker and worked as the
receiver of the equipment. The received signal was passed through the swept gain
amplifier and then filtered to remove noise that came from the high frequency. Finally
the filtered signal could be shown in the display unit.
Two versions of the Acoustic Ranger equipment were AR 100 and AR 1000, which
were in commercial production according to Morgan [10]. The AR 100 instrument
could only detect a range of 30 m of a tube with an internal diameter of 25 mm due
to the restriction of the design. The equipment was designed so that it could be used
by a lowly skilled operator.
Because of this limitation of the test range, AR 1000 was produced. The detection
range was extended to 300 m depending on the internal diameter in a range from 6
mm to 250 mm. Unlike the AR 100 with its own display, the AR 1000 could be used
to a separate oscilloscope so that the details of the recorded signal could be examined.
The AR 1000 was used on both conventional and nuclear power generation plants to
help detect blockages in pipeline systems. It was also used in the civil engineering
field to check the water level of sewers and the location of branch pipes. Another
application was to find the presence of debris in ducting pipes after completing a
bridge building project. As deposits of water inside the pipe could also cause the
reflected wave depending on the depth of the water, the Acoustic Ranger was also
used to identify the water level accumulated inside oil tankers, bore holes and coils.
By introducing the Acoustic Ranger, Morgan [10] also compared the response of a
clean pipe, which acted as a benchmark to the response of the dirty pipe so that
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 48
subtle changes in the response could be identified. However, the clean condition of
the detected system might not have been tested earlier and the reconstruction of the
same clean system would incur extra time and costs.
Papadopoulou et al. [1] demonstrated that APR can locate the defect of a 5 km pipe
with a 1 m diameter. For example, when a leakage occurs in the middle of the pipe,
the reflected signal shows a sudden spike compared to the standard one when the pipe
was in the condition without any defects. In this way, by comparing the differences
between the acoustic signal reflected from the change and the standard signal with no
damage at all, researchers have a new way to analyse the condition of the pipelines and
industries, and therefore to decrease the loss caused by damage in pipelines. APR-
based technology can be used to identify and localise the defects in time, even for a
distance of over 5 km. This technology overcomes the limitations of the noise cross-
correlation [29] which is restricted by the length of pipelines and the accessibility of
pipeline system.
2.2.5 Comparison among different detection methods
As stated above, Table 2.1 is a summary of different methods with theory and limita-
tions.
Table 2.1: Comparison of Different Methods
Method Verified detection length Location of sensorsCCTV [20,21] 182 m Tested pipe
Cross-correlation [22–24] 102.6 m Tested pipePressure transient [26, 27] 1.6 km Tested pipe
APR [1,10,28] Over 5 km Source tube
In the CCTV method, optical sensors are used to monitor the inner wall conditions of
a pipe. The location of defects is identified by analysing the intensity of the projected
laser ring. It is limited to the detection length of the pipe regardless of the difficulties
to install the optical sensors. The intensity of the light becomes weaker after 50 m.
The theory of cross-correlation method is that two sensors are installed around the
leak point to record the vibration or acoustic signals. The cross-correlation of the two
CHAPTER 2. DEFECTS DETECTION IN THE PIPELINE SYSTEM 49
signals is computed so that the leak can be located. This method is restricted by
the prediction of the possible defect and sometimes it is almost impossible to install
the sensors close to the defects under extreme conditions, for example, deep down the
ocean or underground. In pressure transient method, the transient is produced using
inlet flow variation. The characteristics of this reflected transient show the profile
of pipeline internals. This is also restricted to the detection length as the transient
amplitude is only 0.0005% of the base pressure.
Overall, the primary restrictions among all aforementioned methods for defects detec-
tion include:
• Detection of the distance and size of the pipe;
• Accessibility of installation of the sensors.
APR overcomes both restrictions by offering a solution with longer detection length
and by installing the sensors at the source tube instead of on the tested pipes. All of
these make APR a particularly promising non-destructive approach that is worthy of
further investigation.
2.3 Summary
Chapter 2 listed defects along the pipeline and the potential impacts they may cause.
To identify the defects inside pipelines, a great deal of detection methods was proposed
in the literature. Four typical methods were introduced and their limitations were
listed. Overall, it was shown that APR was a useful and non-destructive tool for
pipeline detection.
Chapter 3
Literature Review
Since originally applied in seismic research by Ware and Aki [30] in 1969, APR has been
widely used in various applications, such as reconstruction of the bore profile of musical
instruments [5–7] and industrial pipelines [1–4]. In this chapter, the applications
of APR in different industrial areas are described. A short summary is shown in
Figure 3.1.
3.1 Uses of APR
APR technique is based on analysing the reflection signal from the acoustic impedance
changes inside the pipe medium. There are several use cases which apply the APR to
different applications. All the following applications are the illustrations for what APR
can do in the real life and show that APR can be applied in a variety of fields, including
the pipeline industry. Because of the success of APR used in different aspects, it is
promising to research on APR further and deeper.
3.1.1 Seismic surveys
Detection based on changes in acoustic impedance of a medium was originally applied
in seismic surveys, pioneered by Ware and Aki [30]. Although the term APR was
50
CHAPTER 3. LITERATURE REVIEW 51
Ware and Aki 1969
Jackson 1977
CEGB 1970s
Fredberg 1980
Brook 1984
Smith 1988
Watson 1989
Marshall 1992
Sharp & Campbell 1997
Horoshenkov 2003
Papadopolou 2008
Wang et al. 2012
...
Ware and Aki estimated the
location of the seismic source.
CEGB used Acoustic Ranger to
find defects in the heat exchangers.
Jackson et al measured the airway
geometry to help the investigation
of ENT and sleep apnoea etc.
Amir 1996 Sharp et al reconstructed the bore
profile of musical instruments.
Horoshenkov et al detected
damages in the sewage pipelines.
Wang et al applied APR in
monitoring gas pipelines.
Figure 3.1: Applications of APR History
known, it was used to solve inverse-scattering problems. This solution shared the
same idea as APR used in the other areas. The earth is made up of different layers
with a variety of types of rock. These rocks can be regarded as different mediums
that propagate the acoustic signal. The properties of different rocks vary greatly, such
as the impedance of the medium. In both the continuous and discrete time domains,
the impedance of the medium can be regarded as a function of travel time, and the
transfer function used to describe the characteristics of the medium was obtained from
the impulse response. When an impulse pressure wave was produced by a dynamite
source, pressure wave reflections were generated because of the impedance change
between different seismic layers. This formed the basis of the application of APR.
CHAPTER 3. LITERATURE REVIEW 52
Ware and Aki [30] pointed out that analysing the medium properties of reflected waves
through the medium was an inverse-scattering problem. When the elastic parameters
did not vary significantly over one wavelength, the reduced Helmholtz equation [36]
was the estimation of the seismic problems. The expected results of distance could be
achieved by recovering the impedance of each layer based on the function of delay time.
The assumption for the target area should be considered as cylindrically symmetrical.
In 1970, the forward and inverse discrete time problems on a layered elastic medium [31]
were extended to a more general case by adding the dimension of the matrices from
previous methods. Later on, several methods of inferring the acoustical impedance
of a medium using the reflection response were proposed [32–37]. Weglein et al. [38]
presented the key mathematical-physics framework behind the algorithms for seismic
exploration, considering both the forward and inverse-scattering series construction.
Specifically, the following seismic applications were included:
• In exploration seismology, a wave generated by human beings was given on the
earth surface. As the wave propagated into the subsurface, a sharp change of the
signal meant that some percentage of the signal was reflected back to the surface
instead of continuing to move downwards opposite to the surface. This often
indicated changes in the earth material properties, i.e. impedance differences
between the layers.
• In marine exploration, a series of receivers, such as hydrophones, were placed
below the airwater boundary so that rich information in the reflected signal was
recorded. This information was used for further analysis based on forward and
inverse scattering series methods and appropriate algorithms.
3.1.2 Medical application
APR was also used in the medical field to measure the airway dimensions [39]. The
schematic diagram was shown in Figure 3.2.
CHAPTER 3. LITERATURE REVIEW 53
Amplifier10kHz Low Pass
Filter
AD
MIC
Wave Tube
Trigger module
Spark gap
Data analysis
Figure 3.2: Schematic Diagram for Medical Application
The spark source generated the acoustic impulse by discharging the high-voltage elec-
trical pulse from the trigger module. A microphone (Bruel & Kjaer 4135) recoded this
acoustic impulse transmitted via the wave tube to the airway and the reflected acoustic
wave caused by the impedance changes. The acoustic signal passed the low-pass filter
and analog-to-digital converter(AD) in Figure 3.2 and was ready for analysis. The
inversion technique helped to find the airway geometry by measuring and analysing
the acoustic response. The first test was performed on a dog to determine the airway
geometry of its trachea and lungs. After that, Fredberg et al [40] used the high fre-
quency acoustic data recorded at the mouth to identify features of upper airway and
tracheal geometry. They extended the research to human patients. Brooks repeated
the same experiment on 10 males to show the reproducibility and accuracy of the
CHAPTER 3. LITERATURE REVIEW 54
airway area measurements by acoustic reflection [39].
APR offered a non-invasive way to measure human airways, and had more advantages
than computerised tomography (CT) scanning and X-ray cephalometry. The acous-
tic wave reflections at the mouth could help to reconstruct the airway. APR could
help the investigation of ENT (ear, nose and throat) problems and sleep apnoea, and
in the management of anaesthetic usage [41]. Apart from this, the APR technique
was also used for the non-invasive assessment of lungs [42], tracheal stenosis [43], and
nasal airways [44–47]. On routine clinical experiments [48], both acoustic and mag-
netic resonance imaging (MRI) methods were applied to assess pharyngeal and glottal
areas, and the results were compared to show the effectiveness of the acoustic method.
In Louis’ research [49], a two-transducer system was developed, implemented, and
tested with computational algorithms to reconstruct airway dimensions from acoustic
reflection data using a strategy with two transducers.
3.1.3 Musical instrument bore reconstruction
The application of APR in musical instrument aroused interests of researchers. Stud-
ies and experiments were performed to measure the acoustic properties of specific
types of musical instruments, for example bassoon by Sharp [50]. The effectiveness of
the acoustic approach was determined by whether audients could tell the differences
between sounds produced using different crooks. Related studies included those on
tubular instruments by Amir [6, 51] and brass instruments by Kemp [52,53]. Accord-
ing to the characteristics of different musical instruments, researchers showed a special
preference for the work on trumpets and cornets [54] and horns [55]. Measurements
based on APR were also applied on musical instruments [56].
Experiments based on APR were conducted on ducts to measure the input impulse
response of a wind instrument [57,58]. The reconstruction of the internal bore profile
of the musical instrument could be evaluated by the input impulse response using a
proper reconstruction algorithm [59]. Sharp and Campbell [60] used a similar method
to detect the position and size of the leakage in musical instrument.
CHAPTER 3. LITERATURE REVIEW 55
The pulse reflectometry was used by Sharp and Campbell [7,60,61] to reconstruct the
bore of the musical instrument and the detection of the leak along the instrument. The
schematic diagram of the instrument layout was the same as in Figure 1.1. The impulse
used was generated by a D/A converter of a frequency of 12.5 kHz and a voltage of
5 V. A 6-m long copper source tube was used in the layout. The microphone was
located in the middle of the source tube to avoid the overlap of the input signal and
the first reflected signal.
The reflection coefficients caused by the impedance changes could be calculated from
the IIR. It then was only the geometry knowledge to work out the diameter along the
bore because the object was usually assumed to have a cylindrical symmetry. With a
sampling frequency of 50 kHz, a 356 mm long instrument with a diameter expanding
from 9.4 mm to 12.4 mm to 18.5 mm was reconstructed.
The small diameter source tube and object restricted the reconstruction length of
the instruments because of the high attenuation inside the tube. Furthermore, the
application of the pulse reflectometry was mainly used to reconstruct the musical
instruments, that fell within a certain length (usually less than 1 m). The emphasis
was on the accuracy of the reconstruction shape. Sharp and Campell [60] also used the
impulse reflectometry to find the leak inside the pipe, as the leak could be regarded
as an expansion in the bore. The location of the leak could be identified using the
speed of sound and the reflected time. Under favourable conditions, the size of the
leak could also be estimated depending on the selection of the frequency.
3.1.4 Detection of features and defects in pipelines
Another area in which APR was greatly applied was in the detection of the features
and defects of pipelines. Horoshenkov et al [62] showed that the APR could be used
to detect the damage in sewage pipelines with a series of theoretical and practical
examples. Yunus [63] detected holes in the wall by sending out a relatively short pipe
with a chirp signal and processing the reflected signal with a correlator. Podd [64,65]
monitored sewer pipes using the APR technique with an inside diameter of up to 0.6m
and successfully detected the blockage and water pools inside the pipe. Beck [66–69]
CHAPTER 3. LITERATURE REVIEW 56
developed a similar method to detect the small features in a number of relatively
short pipes. A similar acoustic reflectometry method has also been demonstrated to be
transferable to liquid-filled (e.g. water and petroleum) pipes, even though the presence
of liquid introduces complexity, and features may not be easily identified directly. For
example, Gao [70] introduced the acoustic-related methods to find the leakage in the
water distribution pipelines and Taghvaei [71] used a special piezoceramic transducer
to detect leakage in a fluid-filled pipeline network.
Furthermore, Papadopoulou [1] used this technique to find small holes in pipe walls
and deposits of water inside the pipe with a distance of up to 500 m. He also showed
that APR could allow some characterisation of a blockage. Similarly, it was confirmed
that solid blockages and pools of water (water blockage) could be located and detected.
Lennox et al. got a patented technique known as Acoustek [4]. This technique could
be used to detect blockages and leakages inside the gas pipelines. The basic idea of this
technique was that an impulse signal was injected into some point of the pipeline (which
is usually the beginning in experiments). At another point of the pipe, a microphone
was inserted to record the obtained signal for future analysis. The received signal
was usually a combination of both the normal inputted signal passing by and the
reflected signal because of features/defects inside the pipeline. If there was no specific
feature/defect in the pipeline and the signal was transmitted from one point to the
other in the same direction, the signal received by the microphone was expected to
be the input pulse and the reflection from the end of the pipe. In this condition, the
pipeline can be considered as a clean pipe. If some features/defects existed in the
pipe, no matter what kind of features/defects they were, the recorded signal from the
pipeline would be different from the clean pipe, with a reflected signal being added.
With the knowledge of the speed of sound, the distance between the microphone and
the feature/defect could be calculated and then it was straightforward to know the
location of the defect in the pipeline.
With acoustic analysis and proper mathematical formulation being applied, certain
types of defects, leakages or hydrates could be identified. In some cases that are
slightly more complex than the normal case, for example, when there is a 90 degree
CHAPTER 3. LITERATURE REVIEW 57
angle in the pipe, there will be some reflections of the signal because of the shape and
set up of the pipeline itself. Then if there were some reflections in the signal obtained
by microphone, it may be the reflection of the joints instead of the defect itself. This
means that, in order to determine whether there are defects along the pipe, the re-
flection generated by the joint should be predicted before analysing the signal further.
After that, if there is still reflected signal in the obtained wave, this indicates some
features in the other parts of the pipe. Similarly, if other features were included in
the pipe, such as couplings, fittings, or other fillings placed into the pipe for measure-
ment, control, or experimental purposes, the reflected signal could be generated and
added into the microphone detected signal accordingly. This information should all
be considered in acoustic analysis, which increases the difficulty of the application of
this technology.
APR provides a solution to a great number of industrial pipeline problems worldwide.
However, there are still some limitations to the above method.
Firstly, as described above, it is not difficult to apply the method when the overall
environment of the pipe is not complex, however given more than one joint with
different angles, or given multiple locations of couplings, fittings, or fillings, it may
be difficult to know each reflection signal and to remove these signal before acoustic
analysis.
Secondly, only considering the speed of the sound, although it brings great convenience
to measure and calculate the location of the defects, how large the defect is remains
unknown. This could also be solved by making the best use of all information regarding
the sound wave, such as the energy of the signal, or in other words, the strength or
magnitude of the sound wave.
Thirdly, the detected length of a pipe is uncertain. Once the length of the pipe is
increased, the reflected signal will be weak: especially when the energy of the reflective
signal is similar to environmental noise, it is difficult to recognise whether reflection
exists, or which part is reflection and which part is noise. More advanced instruments
for measurement and analysis should be used to increase the accuracy of detection. The
application of both hardware and software filter will also lead to some improvement
CHAPTER 3. LITERATURE REVIEW 58
in solving this problem.
3.1.5 Detection of features and defects in small bore tuning
The initial APR instrument originated from the research by the Central Electricity
Generating Board UK in the 1970s [10, 28]. An instrument was developed to record
the partial reflections from the leakage or blockage after a small acoustic wave was
injected into the pipe. This instrument was shown to work in pipes with an inside
diameter up to 1m and with a length of up to 300 m [28]. However, there were few
detailed publications or data regarding this instrument and a list of questions were left
unanswered. For example, the distance of the pipe to be detected was not validated
and how to distinguish the defects among all existing features (eg. T-pipe) of the pipe
system, etc. The details of the acoustic ranger have already been explained in the
Section 2.2.4.
The company Acoustic Eye has developed a series of patented products for the de-
tection of a heat exchanger which has contributed to the automation of the whole
detection and analysis procedure. The objects for detection are a branch of small
objects, usually a bundle of tubes. In order to identify the bundle of tubes automat-
ically, a computing device has been developed [72], with the ability to obtain images
and identify which bundle is the objects are the ones that need to be tested. Then the
tester is instructed by this exemplary embodiment. The guidance of this equipment
contributes greatly to the detection. The tester includes a base signal that could be
used as the input signal for testing [73]. The next test signal is then selected from the
data base according to the effectiveness of the previous signal. The reflected signal
is saved in storage for future analysis. The algorithm of this application is similar to
the one used in the detection of features and defects in pipelines, but this is a more
complex case when dealing with multiple tubes in a bundle [74]. Each bundle should
be injected with an input signal and the output in each pipe of this bundle needs to be
collected and saved accordingly. The Acoustic Eye has successfully used this technique
to make a prediction regarding the remaining number of cleaning cycles of a branch
of tubes during the cleaning process. This information is obtained with respect to the
CHAPTER 3. LITERATURE REVIEW 59
state of the branch of tubes in the current cleaning cycle and is re-assessed every one
or several cleaning cycles.
Another recent application of APR on heater exchangers is a patented PACT-04 de-
vice [75]. It was developed by the Irkutsk Research and Design Institute of Chemical
and Petrochemical Engineering. This product is used to detecting defects of inner
sections of pipes. It has been successfully used in industry. It is reported that the fast
speed of APR forms an obvious advantage with full checking of 1000 heat exchanger
pipes taking roughly 40 min in the test.
3.2 Reviews on approximation models
The problem of the propagation of sound waves in gases contained in cylindrical tubes
is a classical one, to which famous name are connected like Zwikker and Kosten [76],
Kirchhoff [9] and Keefe [77]. There are typically two groups for the solutions of the
propagation problem. The representative of the first group was mainly from the an-
alytical approximation from Kirchhoff [9] . The second group was obtained directly
from Zwikker and Kosten [76], Kerris [78] and Iberall [79], etc. It is often related to
studies dealing with the dynamic response of pressure transmission lines.
3.2.1 Model equations
The equation describing the motion of gas in a circular cylinder is the Navier-Stokes
equation in the axial direction [80]. To build up the mathematical model of the
bore based on impedance formulation, the relationship between the acoustic pressure
P (z, ω) and particle velocity V (z, ω) is used according to earlier results in [81], [82],
and [76]. Given a uniform cylindrical tube with a length of L, axial coordinate z
direction along the tube and angular frequency ω,
∂P
∂z+ ZV = 0 (3.1)
∂V
∂z+ Y P = 0 (3.2)
CHAPTER 3. LITERATURE REVIEW 60
where Z and Y represent the acoustic impedance and shunt admittance.
Applying partial differentiation on both sides of (3.1) with respect to z,
∂2P
∂z2+ Z
∂V
∂z= 0 (3.3)
Apply (3.2) to (3.3),
∂2P
∂z2= ZY P. (3.4)
This forms a single second-order equation in P in the frequency domain [55].
For z ∈ [0, L], standard forms for Z and Y [83] are
Z(jω) =jωZc
c(1− Fv)(3.5)
Y (jω) =jω
cZc(1 + (γ − 1)Ft). (3.6)
To provide a detailed explanation on the above equations, c denotes the speed of the
wave, followed by Zc = ρc being the characteristic impedance with air density ρ. The
ideal gas constant in air is represented by γ, and
Fv =2J1(√−jrv)√
−jrvJ0(√−jrv)
(3.7)
Ft =2J1(√−jrt)√
−jrtJ0(√−jrt)
(3.8)
with J0 and J1 being the Bessel functions of the 0th and 1st-order, and the dimen-
sionless parameter rv and rt are
rv = a
√ρω
η(3.9)
rt = νa
√ρω
η. (3.10)
Here a is the tube radius, ν2 is the Prandtl number and η is the shear viscosity
coefficient.
3.2.2 Zwikker and Kosten approximation
Zwikker and Kosten’s model is usually expressed in frequency domain in terms of
acoustic impedance. It was demonstrated that nearly all the approximation solutions
CHAPTER 3. LITERATURE REVIEW 61
are covered by the solution obtained by Zwikker and Kosten. This is the solution
designated as the ’low reduced frequency solution’ when reduced frequency k and
shear wave number s are k � 1 and k/s� 1. k and s are defined as below.
s = a√ρsω/µ (3.11)
k = ωR/c0. (3.12)
ρs, mean density
c0 =√γps/ρs, undisturbed velocity of sound
µ, absolute fluid viscosity
γ = Cp/Cv, ratio of specific heats
Propagation constant Γ of the acoustic signal in frequency domain can be described
as
Γ =
√J0 〈j3/2s〉J2 〈j3/2s〉
√γ
n
with
n =
[1 +
γ − 1
γ
√J0 〈j3/2s〉J2 〈j3/2s〉
]−1.
where J0 and J2 are the 0th and 2nd-order Bessel functions, which can be found in
the Appendix of Kinsler’s book [84].
According to Tijdeman [80], most of the analytical solutions depend on the shear wave
number s only and are covered completely by the “low reduced frequency solution”,
obtained for the first time by Zwikker and Kosten [76]. This confirms that as the
Newton-Raphson method requires an initial value to start the iterative process, it can
be provided by the approximate solution of Zwikker and Kosten.
3.2.3 Kirchhoff approximation
The full solution of the problem has been obtained by Kirchhoff [9] in the form of a
complicated, complex equation. The complex form itself does not reveal itself to any
CHAPTER 3. LITERATURE REVIEW 62
analytical treatment. The equation in (3.13) is rewritten in the terms of shear wave
number s. The estimation was based on the value from Zwikker and Kosten [76].
Γ = j +1 + j√
2[γ − 1 + σ
σs] (3.13)
The real part of Γ represents the attenuation over a unit distance and the imaginary
part represents the phase shift. γ = Cp/Cv is the ratio of specific heats.
For representative liquids and gases, the classical absorption coefficient is defined
by (3.14) [84]. This equation was conventionally used to describe viscous losses and
heat conduction losses in an unconstrained fluid [84].
αc =ω2µ
2ρc3[34
+γ − 1
Pr
](3.14)
αc attenuation, Neppers/m
ω angular frequency, radians/s
µ shear viscosity, N· s/m2
ρ density, kg/m3
c speed of sound, m/s
γ ratio of specific heats
Pr Prandtl number
This equation has been shown to be valid when the gas is monotonic but when the
gas is polyatomic it will not be suitable [84]. Kirchhoff [9] investigated propagation
of sound waves inside a pipe by considering both the viscous and thermal losses. The
deviations that resulted in the equations are described in [2]. In 1974, the English
translation of Kirchhoff’s work became available in [85] which led to the theory being
studied more widely.
If K0, a propagation constant, is defined as shown in (3.15).
K0 = 1 +1− j
a√ρω/µ
(1 +
γ − 1√Pr
)(3.15)
CHAPTER 3. LITERATURE REVIEW 63
Then the attenuation (3.16) of the signal wave, is equal to the negative imaginary part
of K0 multiplied by wave number k.
α =ω
cR
[√ µ
2ρω+ (γ − 1)
√K
2ρωCp
](3.16)
a radius of the pipe, m
κ thermal conductivity, (W/m)K
Cp specific heat constant, J/kg K
Based on Kirchhoff’s estimation, Rayleigh [86] had the estimation for “narrow” pipes.
Later on, higher order approximations have been given by Weston [87] for the tran-
sition pipes, which belonged to narrow-wide, wide-narrow, etc. The full analysis of
Kirchhoff’s estimation can be found in Tijdeman [80].
3.2.4 Keefe approximation
Because of thermal and viscous losses, energy loss exists in the propagation of signal.
In order to have a model with acceptable accuracy in practical application, an approx-
imation is needed to deal with these losses. The approximation approaches of losses
inside the pipe have been discussed in [77,81,88].
The real and imaginary parts of the impedance Z = R + jωL are given by
R = − ωρ
πa2Fv sinφvD2
, (3.17)
ωL =ωρ
πa21− Fv cosφv
D2(3.18)
where
D2 = (1− Fv cosφv)2 + (Fv sinφv)
2. (3.19)
The analogous expressions for the real and imaginary parts of the admittance Y =
G+ jωC are
G = −ωπa2
ρc2[(γ − 1)Ft sinφt], (3.20)
ωC =ωπa2
ρc2[1 + (γ − 1)Ft cosφt] (3.21)
CHAPTER 3. LITERATURE REVIEW 64
where φt and φv are the phase angle which are based on tables provided by Abramowitz
and Stegun [89].
At low frequencies or small tubes, where rv � 1 and rt � 1 with rv and rt given in
(3.9) and (3.10) respectively, the approximation [81] is given as
R→ ωρ
πa28
r2v; (3.22)
ωL→ ωρ
πa24
3; (3.23)
G→ ωπa2
ρc2(γ − 1)
r2t8
; (3.24)
ωC → ωπa2
ρc2(γ) (3.25)
Let s = πa2. Applying (3.22) and (3.23) to (3.1), i.e.
∂P
∂z+ (R + jωL)V = 0 (3.26)
forms∂P
∂z+(ωρs
8
r2v+jωρ
s
4
3
)V = 0. (3.27)
Apply (3.24) and (3.25) to (3.2),
∂V
∂z+[ ωsρc2
(γ − 1)r2t8
+jωs
ρc2γ]P = 0, (3.28)
∂V
∂z= − ωs
ρc2(γ − 1)
r2t8P − jωs
ρc2γP. (3.29)
Applying partial differentiation on both sides of (3.27) with respect to z,
∂2P
∂z2+( ωρπa2
8
r2v+jωρ
πa24
3
)∂V∂z
= 0. (3.30)
By substituting (3.29),
∂2P
∂z2−(ωρs
8
r2v+jωρ
s
4
3
)[ ωsρc2
(γ − 1)r2t8P +
jωs
ρc2γP]
= 0, (3.31)
∂2P
∂z2−(8ω
r2v+j4ω
3
)[ ωc2
(γ − 1)r2t8
+jωγ
c2
]P = 0, (3.32)
∂2P
∂z2+[4ω2γ
3c2− j8ω2γ
r2vc2− ω2(γ − 1)r2t
r2vc2
− jω2(γ − 1)r2t6c2
]P = 0, (3.33)
CHAPTER 3. LITERATURE REVIEW 65
∂2P
∂z2+
4ω2γ
3c2P − jω2
c2
[8γ
r2v+j(γ − 1)r2t
r2v
]P = 0. (3.34)
Keefe [77] gives the complex function of frequency that is necessary to predict atten-
uation:
Γ = e−α(ω)e−jω/ϑp(ω) (3.35)
where ω is the angular frequency, α(ω) is the absorption coefficient, which represents
the attenuation and ϑp(ω) is the phase velocity.
α(ω) =(ωc
)(2√γ
rv
){1− 1
2
[(rv
2
6
)− γ − 1
γ
(rt
2
8
)](3.36)
ϑp−1(ω) = c−1
(2√γ
rv
){1 +
1
2
[(rv
2
6
)−(γ − 1
γ
)(rv
2
8
)]}(3.37)
The power series expansions in the above equations have been truncated so as to give
the best fit in the transition region, where rv is of order unity.
Thermodynamic constants are listed below for air at standard pressure. The temper-
ature difference relative to 26.85 ◦C (300 K) is ∆T [90].
ρ = 1.1769× 10−3 (1− 0.00335∆T ) g · cm−3 (3.38)
γ = 1.4017 (1− 0.00002∆T ) (3.39)
ν = 0.8410 (1− 0.0002∆T ) (3.40)
c = 3.4723× 104 (1 + 0.00166∆T ) cm · s−1 (3.41)
At high frequencies or big tubes, where rv � 1 and rt � 1 with rv and rt given in
(3.9) and (3.10) respectively, the approximation [81] is given as
R→ ωρ
πa2
√2
rv; (3.42)
ωL→ ωρ
πa2[1 +
√2
rv]; (3.43)
G→ ωπa2
ρc2[(γ − 1)
√2
rt]; (3.44)
ωC → ωπa2
ρc2[1 + (γ − 1)
√2
rt]. (3.45)
Let s = πa2. Applying (3.42) and (3.43) to (3.1), i.e.
∂P
∂z+ (R + jωL)V = 0 (3.46)
CHAPTER 3. LITERATURE REVIEW 66
forms∂P
∂z+[(ωρ
s
√2
rv
)+jωρ
s
(1 +
√2
rv
)]V = 0. (3.47)
jωρV
s+∂P
∂z+(√2ρω
srv+
√2jρω
srv
)V = 0 (3.48)
jωρV
s+∂P
∂z+
√2ρω
srv(1 + j)V = 0 (3.49)
Apply (3.44) and (3.45) to (3.2),
∂V
∂z+{ ωsρc2
(γ − 1)
√2
rt+jωs
ρc2
[1 + (γ − 1)
√2
rt
]}P = 0. (3.50)
∂V
∂z+jωs
ρc2P +
[ ωsρc2
(γ − 1)
√2
rt+jωs(γ − 1)
ρc2
√2
rt
]P = 0 (3.51)
∂V
∂z= −jωs
ρc2P −
√2ωs(γ − 1)
ρc2rt(1 + j)P (3.52)
Applying partial differentiation on both sides of (3.49) with respect to z,
∂2P
∂z2+[jωρs
+
√2ρω
srv(1 + j)
]∂V∂z
= 0 (3.53)
By substituting (3.52),
∂2P
∂z2−[jωρs
+
√2ρω
srv(1 + j)
][jωsρc2
P +
√2ωs(γ − 1)
ρc2rt(1 + j)P
]= 0 (3.54)
∂2P
∂z2−[jωρ+
√2ρω
rv(1 + j)
][ jωρc2
+
√2ω(γ − 1)
ρc2rt(1 + j)
]P = 0 (3.55)
∂2P
∂z2+[ω2
c2− j√
2ω2
rvc2(1 + j)− j
√2ω2(γ − 1)
c2rt(1 + j)
]P = 0 (3.56)
∂2P
∂z2+ω2
c2P − j
√2ω2
c2(1 + j)
[ 1
rv+γ − 1
rt
]P = 0 (3.57)
The above approximation was based on the Taylor expansion of series. In [88] and [77],
other approximations were used with the same first-degree Taylor polynomial but with
different types of remainder. Similarly, the absorption coefficient α(ω) and the phase
velocity ϑp(ω) can be expressed in (3.58) and (3.59).
α(ω) =(ωc
){(rv−1√2
)(1 +
γ − 1
ν
)(3.58)
+ rv−2[1 +
γ − 1
ν− 1
2
γ − 1
ν2− 1
2(γ − 1
ν)2]
+rv−3√
2[7
8+γ − 1
ν− 1
2
γ − 1
ν2− 1
8
γ − 1
ν3− 1
2(γ − 1
ν)2
+1
2
(γ − 1)2
ν3+
1
2(γ − 1
ν)3]}
CHAPTER 3. LITERATURE REVIEW 67
ϑp−1(ω) = c−1
{1 +
(rv−1√
2
)(1 +
γ − 1
ν
)(3.59)
− rv−3√
2[7
8+γ − 1
ν− 1
2
γ − 1
ν2− 1
8
γ − 1
ν3
− 1
2(γ − 1
ν)2 +
1
2
γ − 12
ν3+
1
2(γ − 1
ν)3]}
Keefe [77] summarised the different approximations for the frequency response of an
acoustic tube. All expressions listed in the paper were valid for the continuous fre-
quency domain. However, the majority of the modern equipment could only deal with
the digital signal. Therefore, the discrete measurement is more practically used. Amir
explained the problems encountered when transforming the continuous frequency do-
main to the discrete time domain were explained in detail [6]. Amir pointed out that
the time domain response had more advantages than the frequency one. Only pressure
data needed to be recorded and the time for a single measurement was short in the
time domain. Keefe [77] took Benade’s analysis [90] and applied it to the situation
when the inner wall of the pipe is not isothermal. However, to increase the accuracy,
more terms were retained in the asymptotic expansion of the Bessel functions.
3.2.5 Comparisons among different approximation models
As described above, the three main approximation models are summaried in Table 3.1.
Most of the analytical solutions depend on the shear wave number s only and are cov-
ered completely by the ’low reduced frequency’ by Zwikker and Kosten. The full
Kirchhoff equation can be solved with the help of the Newton-Raphson procedure.
The simplified format in Table 3.1 can be used for ’wide tube’ situation. These ap-
proximations work for tubes under different conditions defined by k and s. Keefe’s
approximation can be written in two formats under the condition of rv and rt, which
was discussed in Section 3.2.4. Keefe’s approximation is based on the conclusions of
acoustic impedance from Kirchhoff to get the approximation for cylindrical gas duct.
CHAPTER 3. LITERATURE REVIEW 68
Table 3.1: Review of Analytical Solutions to the Signal Propagation
Author Year Formula for the constant of propagation
Kirchhoff (’wide tube’) 1868 [9] Γ = j + 1+j√2
[γ−1+σσs
]
Zwikker and Kosten 1949 [76,79]
Γ =
√J0〈j3/2s〉J2〈j3/2s〉
√γn
with n =
[1 + γ−1
γ
√J0〈j3/2s〉J2〈j3/2s〉
]−1Keefe 1984 [77] Γ = e−α(ω)e−jω/ϑp(ω)
3.3 Reviews on numerical simulation models
3.3.1 Finite Difference Time Domain Model
Bilbao [91] developed the finite difference time domain methods for the simulation of
brass instrument bore. The dynamics of the acoustic bore are simulated based on the
model of musical instrument, with viscothermal and radiation losses being considered.
Define
k =1
fs(3.60)
where fs is the sampling frequency.
Given a time step k equal to the inverse of sampling rate and a position step h = LN
for a known length L, the interleaved grids [92] in Figure 3.3 is used to show
• the pressure p(z, t) at different location z = lh and time t = nk for nonnegative
integer n and l ∈ [0, N ].
• the velocity v(z, t) at different location z = (l + 12)h and time t = (n + 1
2)k for
nonnegative integer n and l ∈ [0, N − 1].
For convenience, the following forwards and backwards shift operators are defined with
respect to a given grid function gnl at the time n and location l:
• forwards and backwards time shifts: et±gnl = gn±1l ;
• forwards and backwards spatial shifts: ez±gnl = gnl±1;
CHAPTER 3. LITERATURE REVIEW 69
p
p
p
p
p
p
p
p
p
p
p
p
v
v
v
v
v
v
v
v
v
z=0h z=0.5h z=h z=1.5h z=2h z=2.5h
t=nk
t=(n-0.5)k
t=(n-1)k
t=(n+2)k
t=(n+1.5)k
t=(n+1)k
t=(n+0.5)k
Figure 3.3: Interleaved Grids of Pressure And Velocity.
• forward and backward difference operators in time: δt± = ∓ 1k(1− et±);
• forward and backward difference operators in space: δz± = ∓ 1k(1− ez±);
• averaging operations: µt± = 12(1 + et±).
Using these operations, the model can be written as
ρδt−v + δz+p+ qµt−v + fδt12µt−v = 0 (3.61)
S
ρc2δt+p+ δz−(Sv) + gδ
t12µt+p = 0. (3.62)
with
Sl =1
2(Sl+ 1
2+ Sl− 1
2) (3.63)
and an approximation of δt12.
Time domain methods are another approach to model the wave propagation in acoustic
tubes. A tube is numerically integrated using a time-stepping method. One of the
advantages is the impulse response can be calculated directly. Another advantage is
the possibility of generalizations to the case of nonlinear wave propagation.
CHAPTER 3. LITERATURE REVIEW 70
3.3.2 Layer peeling Model
Amir et al [6, 51] presented two discrete loss models (short cylindrical and conical
models [90, 93]) for tubular acoustics systems. The pipeline system was discretised
to small cylindrical segments or conical segments in each modeling. The waveguide
filter was described to account for the losses inside the segments. The basis for the
algorithm used by Amir was the layer peeling algorithm in seismic applications. The
experiment apparatus used is shown in Figure 3.4.
As the conical model is more complicated in a simulation, especially for a tube with
a longer length and fewer cross sectional changes, the cylindrical model can be conve-
niently used in a pipeline system. In addition, the conical model can also complicate
the calculation according to the way to obtain the reflection coefficients between the
conical segments.
A trumpet bell was used as an experimental example to show the accuracy of the
simulation results.
Figure 3.4: The Schematic Diagram of Setup
Amir’s discrete model has been widely applied by different groups of researchers, in-
cluding Sharp [60], Kemp [52] and Amir himself [6]. In Sharp’s study [60], Pipe #1
(2m) and Pipe # 2 (2 m) in Figure 3.4 were used as source tubes to ensure that the
IIR could be recorded directly by the microphone without the interference of the in-
put reflections and system reflections of the test instruments (longest up to 1m). The
sampling frequency was 12 kHz because of the excitation pulse spectrum was up to 6
kHz. In this way, the resolution of the reconstruction of the instrument, which was the
CHAPTER 3. LITERATURE REVIEW 71
length of each segment, was around 0.028 m depending on the speed of sound during
the test [60].
In previous papers [52,55], researchers developed and validated a simulator that models
the transmission and reflection of acoustic waves within a single pipe. After that, the
single pipe simulator was expanded to the one that models the behaviour of acoustic
waves in networked pipe systems. By comparing the signals from an experimental test
with those generated by the simulator, any defects could be identified quickly.
All of the simulators that have been developed in the literature have been configured to
model the behaviour of acoustic signals over relatively short lengths (2.5 m) of limited
bore (50 mm) piping. The focus of the present work is to explore the use of APR over
extended distances of large diameter pipe.
Amir et al [6] built the simulators to reconstruct musical instruments, but a simulator
could also be used widely for industrial applications. The biggest difference between
the pipe simulator and those for musical instruments is the measured length. Generally,
a pipe simulator is required to simulate pipes as long as 10 km, whereas a musical
simulator only works for about a 2.5 m tubular instrument.
Numerical simulations of input impedance are compared with measurement for a va-
riety of musical instruments. The complexity of this method is determined by its
application background - complex model of brass instruments with constraints. This
is the reason for the fact that a number of mathematical approximations are applied
in the model and analyze. Both the pressure and the velocity are considered in simu-
lation, which gives more useful information.
3.3.3 Summary of the two models
Both the FDTD model and layer peeling model essentially used time domain approx-
imation. In the layer peeling model [6,51], it focused on the step by step model using
the cylindrical or conical segements. In FDTD model [91, 94], the bore profile was
treated as a unit to obtain a more complete view of the internal bore of the musical
CHAPTER 3. LITERATURE REVIEW 72
instruments.
The pipeline simulators, which will be introduced in Chapter 6, will develop and
evaluate the application of the layer peeling model in the pipeline system. As the
signal at each feature segment is important for the analysis of APR, especially when
trying to simulate the defect features, using a step by step model is more applicable.
3.4 Summary
Chapter 3 introduced some typical applications for APR including seismic research,
medical application, tubular musical instrument reconstruction and pipeline detection
and analysed their limitations. Three classical approximation models were reviewed.
At the end of the chapter, two typical models for building a simulator were explained
and compared. Layer peeling model is focused on the step by step model using the
cylindrical or conical segments while FDTD considered the bore, both the mouthpiece
and bell as a unit.
Chapter 4
Attenuation of the Acoustic Wave
Acoustic waves propagating along a pipeline over a short distance, such as a distance
equal to the diameter of the pipe, can be regarded as lossless when the dissipation is
slight. However, in long pipelines, the dissipative terms cannot be neglected because
of the existence of viscous and thermal losses, with all of acoustic energy converted to
thermal and viscous energy in the end when the length of the pipeline is long enough.
In this chapter, Kirchhoff’s wave equations are introduced and used to describe the
attenuation of an acoustic signal in a pipe. In this chapter, the wave equation is
introduced together with the boundary conditions. Lossless sound propagation is
then explained followed by the derivation of the attenuation of the acoustic signal. In
addition, experimental results are provided which validate Kirchhoff’s equation. Using
these data, a comparison is made between previously published data investigating
acoustic attenuation in pipelines and the results obtained in this work.
4.1 Related theory
4.1.1 Speed of sound
When considering the propagation of an acoustic signal along the length of a pipe, it
is important to understand the speed that this signal travels, i.e. the speed of sound
73
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 74
in the medium. The speed of sound c will vary depending on the conditions in the
pipe [86]. Speed of sound is defined by the equation [95]
c =
√K
ρ, (4.1)
where K is the coefficient stiffness and ρ is the density.
For the ideal gas, K is given by
K = γp, (4.2)
where p is the presure and γ is the ratio of specific heats
γ =√Cp/Cv. (4.3)
In (4.3), Cp is the specific heat at a constant pressure and Cv is the specific heat at a
constant volume.
In this way, (4.1) can be written as
c =
√γp
ρ. (4.4)
Under ideal gas law,
p = nRT/V. (4.5)
The speed of sound can be expressed in
cideal =
√γp
ρ=
√γRT
M, (4.6)
where
• R (approximately 8.314,5 J·mol−1· K−1) is the molar gas constant [96];
• T is the absolute temperature, K;
• M is the molar mass of the gas. The mean molar mass for dry air is about
0.028, 964, 5 kg/mol.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 75
This equation applies only when the it is ideal gas inside of the pipe. Calculated values
for speed of sound of air cair have been found to vary slightly from experimentally
determined values [97].
For air, a simplified symbol is used
R∗ =R
Mair
. (4.7)
Define ϑ = T − 273.15 when T is in degrees Celsius (◦C). Then
cideal =√γ ·R∗ · T =
√γ ·R∗ · (ϑ+ 273.15) =
√γ ·R∗ · 273.15
√1 +
ϑ
273.15. (4.8)
Following numerical substitutions, R = 8.314, 510 J/(mol ·K),Mair = 0.028, 964, 5 kg/mol
and γ = 1.4000, cair can be written as
cair = 331.3
√1 +
ϑ
273.15m/s. (4.9)
In laboratory measurement and simulation, the medium inside of the pipe is air and
the pressure is atmospheric. (4.9) can be used to calculate the speed of sound when
air travels inside of pipeline. For on-site experiments, because of complex environment
and different gas pressure and density, and the inside medium is not air or the inside
pressure is not atmospheric, speed of sound generated by AGA 10: 2003 is used. There
is an online tool for this to get the speed of sound directly under different temperature
and pressure.
4.1.2 Boundary of plane wave
A plane wave is defined as follows: each acoustic wave has a constant amplitude and
phase on any plane perpendicular to the direction of propagation.
Figure 4.1 shows different modes for values of m and n of up to 3 where m is the
angular mode order (line in the figure) and n is the radial mode order (circle in the
figure). kz is the wave number in z direction. In Table 4.1, it is shown the extrema
value of Jm under each mode [84].
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 76
m=0 m=1 m=2 m=3
n=0
n=1
n=2
n=3
Figure 4.1: Acoustic Modes in a Cylindrical Pipe (Agarwal and Bull [98])
Table 4.1: Extrema: Bessel Functions of the First Kind
n=1 n=2 n=3 n=4 n=5m=0 0 3.83 7.02 10.17 13.32m=1 1.84 5.33 8.54 11.71 14.86m=2 3.05 6.71 9.97 13.17 16.35m=3 4.20 8.02 11.35 14.59 17.79m=4 5.32 9.28 12.68 15.96 19.20m=5 6.41 10.52 13.99 17.31 20.58
When in mode (0, 0) the acoustic signal travels as a plane wave mode at the velocity of
sound in the particular medium it is travelling through. Kichhoff’s attenuation theory
is only applicable when the signal travels in this mode.
According to Kinsler [84], Bessel functions of the first kind (Jm) are introduced to
solve the boundary conditions, which offers the condition when the signal is travelling
as a plane wave. kmn is the wave number
kmn =j′mna
(4.10)
kz =
[(ωc
)2− k2mn
]1/2(4.11)
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 77
a diameter of the pipe, ω angular frequency of the transmitting acoustic wave
j′mn is the extrema of Jm whose values have been tabulated for convenience, where the
m suffix represents a circumferential wave mode and the n suffix a radial mode. Based
on different values of m and n, the wave can be transmitted in different modes (m, n)
within the pipe.
If the wave form is in a higher mode and kz has an imaginary part then the wave will
be evanescent in z direction.
Hence for each higher mode, there is a cut off frequency when
ω
c=j′mna
(4.12)
For the first mode beyond the plane wave, the value of j′mn is 1.84 [84]. Therefore,
provided that the angular frequency is lower than 1.84c/a, only the plane wave will
propagate within the rigid wall of the pipe. For example, when the temperature is
20◦C and according to (4.9) the speed of sound is 343.42 m/s and the ID of the pipe
is 50 mm, then the cut off frequency is
f =ω
2π= 4.02× 103Hz (4.13)
In the work presented in this thesis the test pipelines varied in size from 2.7 mm (0.5
inch) to 254.0 mm (10 inches), with the tested length up to 12 km. In Table 4.2, the
cut-off frequency for each pipe size are listed for reference. Equation (4.12) and (4.13)
define the highest frequency when only plane wave travels along the pipeline, which for
the pipeline considered above means that if the frequency is below 4.02 kHz, then the
signal can be considered to be a plane wave. In the experimental work reported in this
thesis the frequency content of the acoustic signals was primarily below 200 Hz, which
was considerably below cut-off frequency and hence plane wave mode was assumed.
Blackstock [99] placed a restriction on the pipe diameter for which the attenuation
equation could be used. This is defined in (4.14).
δν << R <<c2
ω2δν(4.14)
and
δν =
√2µ
ρω(4.15)
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 78
Table 4.2: Pipe Size vs Cut-frequency
Size (mm) Cut-off frequency (kHz)12.7 15.8425.4 7.9250.8 3.9676.2 2.64101.6 1.98127.0 1.58152.4 1.32177.8 1.13203.2 0.99228.6 0.88254.0 0.79
δν is the viscous acoustic boundary layer measured in meters.√2µ
ρω� R� c20
ω
(1 +
T
273
)√ ρ
2µω(4.16)
The range of the diameter, when the Kirchhoff’s equation can be applied, is defined
based on the frequency of the signal and temperature of the environment. Assuming
the temperature is 0 ◦C, then the ranges of diameters for the frequency range 10 to
2000 Hz is shown in Figure 4.2. This figure provides the range of diameters when the
application of Kirchhoff’s equation is valid. Based on the boundary results of the pipe,
for an industrial pipe, the larger the pipe is, the more suitable Kichhoff’s equation will
be applied.
A further assumption that is made when applying Kirchoff’s attenuation theory is that
the pipe is infinitely long. In reality, this is not possible. However, the addition of a
’dissipation pipe’ to the end of pipe systems used in this work simulates the idealised
infinite condition.
4.1.3 Window function comparison
In a practical situation it is not possible to inject acoustic signals with unlimited
lengths and therefore it is necessary to use a signal of finite length. After cutting
or shortening the length of a signal, the frequency spectrum will be affected. This is
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 79
0 500 1000 1500 20000
0.5
1
1.5
Frequency (Hz)
Dia
mete
r (m
m)
Lower boundary
0 500 1000 1500 20000
2
4
6
8x 10
7
X: 2000
Y: 2.815e+04
Frequency (Hz)
Dia
mete
r (m
m)
Upper boundary
Figure 4.2: Kichhoff Attenuation Restrictions
known as spectral leakage. A window function can be used to control certain properties
of the wave and help to reduce the frequency leakage. If the side lobes of the window
function are close to 0, then the main energy stays within the main lobe, which can keep
the cut wave close to the original spectrum. There are several window functions that
are typically used for this including rectangular window, triangular window, Hamming
window and Hanning window. In Table 4.3, a comparison of the different windows is
provided. The frequency response of each windowing technique is shown in Figure 4.3
to Figure 4.6.
If the primary frequency in the signal is particularly important, then it is better to
choose a window function with a narrow main lobe, which will result in less leakage.
Theoretically either Hanning window or Hamming window works in this situation
as they both have narrow windows. In the presented analysis the Hanning window
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 80
Table 4.3: Comparison Among Different Window Functions
Window Name Advantage Disadvantage
Rectangular window(Figure 4.3)
The main lobe is focused.
Side lobes are high withnegative side lobes as well.High frequency interferenceand leakage, Even withminus frequency spectrum
Bartlett window(Figure 4.4)
Side lobes are smallercompared to rectangularwindow, with nonegative side lobes.
The main lobe is twice widerthan the rectangular window.
Hamming window(Figure 4.5)
Decreases high frequencyinterference and leakage
There are more ringsthan in Hanningwindow.
Hanning window(Figure 4.6)
Decreases high frequencyinterference and leakage
The main lobe is widercompared to rectangularwindow.
was used. The Hamming window showed no improvement in the results when it was
applied.
0 5 10 15 20 25 30 35 40 45 500
0.5
1
Samples
Am
plit
ude
-150 -100 -50 0 50 100 1500
20
40
60
Bins
Am
plit
ude
Figure 4.3: Rectangular Window
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 81
Samples
Bins
Am
plitu
de
Am
plitu
de
Figure 4.4: Bartlett Window
Samples
Bins
Am
pli
tud
eA
mp
litu
de
Figure 4.5: Hamming Window
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 82
Samples
Bins
Am
plitu
de
Am
plitu
de
Figure 4.6: Hanning Window
4.2 Experiments validation
Previous results published in other research studies highlighted errors between theoret-
ical and measured attenuation to be in the range of 1.5% to 15%, with the majority of
experiments performed on pipelines with lengths of less than 33 m. Furthermore, the
lower frequencies, which are particularly important in the present work, had received
very little attention in these previous studies. To fully understand the suitability of us-
ing the attenuation theory detailed above for experiments in long lengths of industrial
pipeline, a series of validation experiments were conducted.
4.2.1 Previous research results
Several studies have investigated the validity of Kirchhoff’s equation. These studies
are summarised below.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 83
Tijdeman [80] and Davies Rodarte [100] showed that the average error was 11.6% as
summarised in [101].
In work conducted by Mason [102], pipe diameters of 14.98 mm, 11.7 mm, 8.46 mm
and 5.36 mm, with corresponding lengths of 6.22 m, 4.89 m, 4.26 m and 7.63 m were
used, with a frequency range between 200 Hz and 4000 Hz. The maximum error
between the theoretical result and the experimental result was 5.56%. The average
temperature used in the experiment was 23.5◦C.
In Lawleys research [103], five tubes were tested with diameters ranging between 0.3
mm and 2.34 mm. The measurements focused on the frequencies of 60 kHz, 80 kHz,
100 kHz, 120 kHz. Although error metrics weren’t provided a statement of their
[Kirchoff’s equation] accuracy was not high. The temperature used in the experiment
was 27◦C.
Weston [87] compared the theoretical result to the experiment result from Lawley,
using a frequency of 120 kHz in a tube with a diameter of 1.5 mm, containing oxygen.
It was shown that the attenuation error was 10.4%. The temperature used in the
experiment was 27◦C.
Fay [104] used 15 mm diameter pipe, with a length of up to 1 m at temperatures of
26◦C and 27◦C. The value of the attenuation coefficient was approximately 5 % in error
based on the magnitude of the received signal in ranges from 1.5% to 15% compared
to the Kirchhoff theory.
Angona [105] used the frequency range from 2 kHz to 10 kHz. The size of the tested
tube was 16.82 mm with 0.5 m long for attenuation test. The test made on dry air
and nitrogen demonstrated that the attenuation from Kirchhoff was underestimated
by 4.5%.
4.2.2 Experimental apparatus
As discussed earlier, the experiments previously reported in the literature have fo-
cused on measuring attenuation in short lengths of small-bore pipes at relatively high
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 84
Table 4.4: Details of the Test Pipes
GroupNumber
ID(mm) OD(mm) Length(m)
1 39.8 50
5075100125150175200
2 25 32
5075100125150175200
3 15.17 20
5075100125150175200
frequencies. The experiments described in this Chapter attempt to validate Kirshoff’s
theory at low frequencies over relatively long lengths of pipe.
The pipes used in the laboratory tests were made of polyethylene, and were new and
clean. The three sets of pipes that were used are listed in Table 4.4. The sizes of
the tested pipes were 15.17 mm (0.6 inch), 25 mm (0.98 inch) and 39.8 mm (1.57
inch). Each size of pipe was tested using different lengths, ranging from 50 m to 200
m, which is the target range for the gas distribution work. The length measurements
were provided by the manufacturers and were considered to be only approximate.
More accurate lengths were determined using acoustic time of flight measurements.
Table 4.4, provides full details of the pipes used in the experiments, where ID and OD
represent inner diameter and outer diameter of the pipeline.
The test equipment is listed below, with a diagram of the set up shown in Figure 4.7.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 85
• A/D NI 9234: 24-bit resolution 51.2 kS/s per channel maximum sampling rate
±5V input
• D/A NI 9263: 16-bit resolution 100 kS/s simultaneous analogue output module
• Amplifier: YAMAHA Natural Sound Integrated Amplifier A-S3000
• Microphones: DeltaTron Pressure-field Microphone Type 4944A
• Loudspeaker: SEAS H1208-08 L22RN4X/P
• USB cable
• BNC cables
MIC1
LOUDSPEAKER TEST TUBE
AMPLIFIER
COMPUTER
A/DD/A
MIC2
DISSIPATION TUBE
Figure 4.7: The Set up of the Experiment in the Lab
A photograph of one test is shown in Figure 4.8. It shows the coiled pipe fitted with two
microphones, a speaker at one end, with the other end open to the environment. The
open end meant that the temperature remained consistent with the temperature in
the laboratory. Microphone 1 was positioned close to the loudspeaker with a distance
of around 0.5 m to avoid any ringing from the loudspeaker. A fitting was designed
to connect the loudspeaker to the tested pipe. The fitting was made of a poly acrylic
sheet with four screws to fit the loudspeaker and one central hole to fit the tested
pipe. An amplifier was used to amplify the signal sent out from D/A NI 9263. The
two microphones could receive the acoustic waves along the pipeline with a time delay
between them. After receiving all of the test data, post processing was performed.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 86
Figure 4.8: Coiled Pipes for the Experiments
25 m and 50 m pipes were used to dissipate the signal beyond the end of the pipes. The
pipes used in the experiment had lengths of either 25 m or 50 m. Therefore, to achieve
the longer lengths they were connected via compression polypropylene coupling.
Figure 4.9 shows the flow of data in the experiments.
Cable
ComputerDAQ
board
Conditioner
Loudspeaker
Microphones
Cable Cable
Cable
Figure 4.9: Data Transmission Order of the Test System
During the entire test, the temperature of the environment was considered to be con-
stant while the test was running.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 87
4.2.3 Analysis
During all the tests reported in this Chapter, the amplitude of recorded data refers
to the pressure of the sound wave that is injected and transmitted inside the coiled
pipes.
To begin, tests were conducted using pipelines of the same diameters, but with fre-
quencies ranging from 50 Hz to 2000 Hz. Taking one set of tests as an example (ID
of 39.8 mm, measured using venire callipers). This test was performed on pipes from
50 m to 200 m in increments of 25 m (i.e. seven sets of data were collected). For
each pipe set up, acoustic signals at each frequency was injected and the measure-
ments taken. This was repeated five times and the results averaged to reduce any
unexpected disturbances in the environment.
Acoustic signals ranging in frequency from 20 Hz to 2000 Hz, in increments of 10 Hz,
were transmitted to the loudspeaker and the signals recorded by two microphones were
collected. The signal sent into the system was a short burst sinusoidal wave with a
single frequency. The sinusoidal signal was the wave that produced the minimum dis-
turbance in the electrical circuits and was the only wave that remained unchanged after
signal processing (using filters or following differentiation). Experimental attenuation
values were calculated using
αp = −8.686× ln(p2p1
)/l12 (4.17)
αp experimental attenuation, dB/m
p1, p2 pressure signals recorded by the two microphones
l12 the length between the two microphones.
The constant, 8.686, was used to change the attenuation unit from Neppers/m to
dB/m, i.e. 1Np = 20 log10 e = 8.686 dB.
To analyse the acoustic measurements taken from the experiments, three methods
were used to evaluate the attenuation of the signals: the root mean square (RMS)
value, the peak amplitude value and the root of the FFT spectrum of the signal.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 88
Using these techniques, the acoustic measurements were analysed in both the time and
frequency domains, which allowed different interpretations of the signals. In related
work, Mason [102] used the power ratio to obtain their attenuation measurements
whilst. Fay [104] used the maximum and minimum values to determine the ratio of
pressure.
In the time domain, the RMS and peak amplitude values were used to evaluate the
attenuation. When using the RMS value, p1 and p2 refer to the RMS values of the
two signals recorded by the two microphones. For the peak evaluation, p1 and p2
refer to the peak values of the two signals recorded by the two microphones. The
measurements collected from the microphones were processed in the following way.
1. The beginning and end sections of the signals were ignored as these parts of the
signal were not stable.
2. Full cycles of the signal data were saved. Incomplete periods were discarded as
these would affect the RMS value.
3. A band-width filter was used to reduce secondary frequency content. This was
necessary because the aim was to focus on specific frequencies.
4. Following the signal processing, two signals were available; one from each mi-
crophone. They are the original signals from each microphone after being filtered.
Equation (4.18) was used to determine the RMS measurement and peak values of
the signals were determined directly from the processed measurements. As the signal
could be affected by background noise, the peak value was read from different periods
and averaged. This resulted in more consistent results. The RMS value of a signal is
defined by
xrms =
√1
n
(x21 + x22 + · · ·+ x2n
)(4.18)
where n is the number of points for the target signal and x1, x2, x3, . . . , xn are the
corresponding values at each point along the entire recorded signal length.
Figure 4.10 illustrates the difference between the RMS and Peak values.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 89
Samples
Am
pli
tude
Figure 4.10: RMS Value and Peak Value
To analyse the attenuation in the frequency domain, FFT was applied to the measure-
ments. p1 and p2 refer to the two signals recorded by the microphones after FFT has
been applied. The FFT measurements were processed as follows:
1. A band-width filter was used to remove the unwanted frequencies of the raw data;
i.e. the frequencies that were not the focus.
2. A Hanning window was applied to decrease the edge affects of the signals from the
two microphones. As the same Hanning window was applied to both of the signals,
the attenuation results were not influenced as the operation involves division.
The Hanning window is defined as
w(n) = 0.5(
1− cos( 2πn
N − 1
))(4.19)
where N is the number of Hanning window.
Finally, FFT was applied to the resulting data to determine the frequency content.
To improve the consistency of the results all the tests were completed five times and
the results averaged.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 90
The error between the theoretical value and the experimental values was determined
using the following equation:
Error =(αp − α
α
)× 100% (4.20)
α theoretical attenuation
αp experimental attenuation
The theoretical attenuation α (dB/m) has already been introduced in section 3.2.3
when Kirchhoff’s attenuation was described.
α = 8.686× ω
cR
(√ µ
2ρω+ (γ − 1)
√K
2ρωCp
)(4.21)
If the result is negative, this means that the experimental result is less than the theo-
retical prediction. In contrast, when the result is positive, it means the experimental
result is larger than the theoretical attenuation. In the following subsections of this
chapter, all the errors were calculated using (4.20).
4.3 Experimental results
4.3.1 Different length tests
Taking the 50 m length as an example, the distance between the two microphones
was 50 m, the diameter of the pipe was 39.8 mm and the ambient temperature was
20 ◦C. Figure 4.11 illustrates the attenuation results by utilising the three different
analysis approaches described earlier, compared with the theoretical results, obtained
using (4.21). This figure shows that there is a high degree of consistency in the results.
Figure 4.12 shows the error that was measured for each of the three analysis techniques.
In Figures 4.14 and 4.16, the attenuation results and errors are presented for the
experiments conducted with pipelines with ID of 25 mm and 15.17 mm respectively.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 91
0 200 400 600 800 1000 1200 1400 1600 1800 20000
0.1
0.2
0.3
0.4
0.5
0.6
0.7
Frequency (Hz)
Att
en
uati
on
(d
B/m
)
Attenuation Results
Theoretical Attenuation
RMS attenuation
Peak to Peak attenuation
FFT attenuation
Figure 4.11: 50 m Pipe Attenuation Results When D = 39.8 mm
0 200 400 600 800 1000 1200 1400 1600 1800 2000-20
-15
-10
-5
0
5
10
Frequency (Hz)
Err
or
(%)
Error Analysis(%)
RMS
Peak to peak
FFT
Figure 4.12: Error Results When D = 39.8 mm
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 92
200 400 600 800 1000 1200 1400 1600 1800 2000-2
-1
0
1
2
3
4
5
Frequency (Hz)
Err
or
(%)
Error Analysis(%)
Figure 4.13: Error Results of RMS Value
0 200 400 600 800 1000 1200 1400 1600 1800 20000.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
Frequency (Hz)
Att
enuation (
dB
/m)
Attenuation Resuts
Theoretical Attenuation
RMS attenuation
Peak to Peak attenuation
FFT attenuation
Figure 4.14: Attenuation Results When D = 25 mm
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 93
200 400 600 800 1000 1200 1400 1600 1800 2000-8
-6
-4
-2
0
2
4
6
8
Frequency (Hz)
Err
or
(%)
Error Analysis(%)
RMS
Peak to peak
FFT
Figure 4.15: Error When D = 25 mm
0 500 1000 1500 20000.2
0.4
0.6
0.8
1
1.2
1.4
1.6
Frequency (Hz)
Att
nu
ati
on
(d
B/m
)
Theoretical Attenuation
RMS attenuation
Peak to Peak attenuation
FFT attenuation
Figure 4.16: Attenuation Results When D = 15.17 mm
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 94
0 200 400 600 800 1000 1200 1400 1600 1800 2000-25
-20
-15
-10
-5
0
5
Frequency (Hz)
Err
or(
%)
RMS
Peak to peak
FFT
Figure 4.17: Error When D = 15.17 mm
0 200 400 600 800 1000 1200 1400 1600 1800 20000
0.1
0.2
0.3
0.4
0.5
0.6
0.7
Frequency (Hz)
Att
enuation (
dB
/m)
2D plot for Attenuation
Theory
50m
75m
100m
125m
150m
175m
200m
Figure 4.18: Attenuation Results When D = 39.8 mm
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 95
0 200 400 600 800 1000 1200 1400 1600 1800 20000.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
Frequency (Hz)
Att
enuation (
dB
/m)
Theory
50m
75m
100m
125m
150m
175m
200m
Figure 4.19: Attenuation Results When D = 25 mm
0 200 400 600 800 1000 1200 1400 1600 1800 20000.2
0.4
0.6
0.8
1
1.2
1.4
1.6
Frequency (Hz)
Att
enuation (
dB
/m)
Theory
50m
75m
100m
125m
150m
175m
200m
Figure 4.20: Attenuation Results When D = 15.17 mm
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 96
Similar attenuation tests were performed for the other lengths and the results are
shown in Figures 4.18- 4.20.
An initial analysis of the results presented in Figures 4.18 to 4.20.
• The results were consistent with each other and similar to the theoretical results.
The exception to this is Figure 4.18 to 4.20 which shows that the attenuation
is significantly lower than anticipated at higher frequencies in small diameter
pipes. This is discussed further in the following discussion in this section.
• The error tended to be slightly larger at frequencies above 200 Hz than below this
frequency. However, the errors were within 5%, with the minimum error being
approximately 0.5%. As the focus for this work was to validate the suitability of
applying Kirchoff’s theory to approximate the attenuation in industrial piping,
which is likely to contain debris and corrosion then a 5% error was considered
to be acceptable at this stage of the research.
• The RMS value had the lowest error when compared with the other metrics.
However, all errors were below 5% (Figure 4.13).
• All of the results had a positive error, except for three frequencies (190 Hz, 210
Hz, 500 Hz). This means that for these tests, Equation (4.21) tended to under
estimated the attenuation.
Figures 4.18 to 4.20 clearly show that at the higher frequencies the measured attenua-
tion is significantly lower than that calculated using Kirchoff’s theory. The reason for
this was because of experimental limitations. Attenuation in the pipes is quite signifi-
cant, particularly at higher frequencies and small diameter pipes. As the attenuation
increases then the signals can get lost in the background noise and when frequency
analysis is applied errors are introduced. If the results for the 175 m (39.8 mm ID)
pipe are now considered. Figures 4.21 and 4.22 show some of the signals recorded in
this test. The upper plots in each figure compare the injected signal (red, using the
Y label in the left) with the reflected signal (green, using the Y label in the right),
while the lower plots show the FFT analysis of the two signals. When the frequency is
relatively low, for example when f = 500 Hz, the reflected signal can still be identified
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 97
clearly as a sinusoidal wave. However, when the frequency is increased to f = 1500 Hz,
then the reflected signal is difficult to be identified and as can be seen in the lower plot
of Figure 4.22, other frequencies are introduced in to the analysis which complicates
the analysis. Although the errors encountered in this study are relatively large, these
errors are only significant (above 5%) at frequencies that are above approximately 200
Hz and in relatively small diameter pipes. The focus of this work is in using APR
over long lengths of large diameter pipes. Since long distances are required then the
important frequencies are those that are below 200 Hz.
0.054 0.056 0.058 0.06 0.062 0.064 0.066 0.068-0.04
-0.02
0
0.02
Time (s)
Pre
ssu
re (
V)
0.054 0.056 0.058 0.06 0.062 0.064 0.066 0.068-10
-5
0
5
x 10-5
0 50 100 150 200 250 300 350 400 450 500 5500
0.5
1x 10
-4
Frequency (Hz)
Am
pli
tud
e (V
)
0 50 100 150 200 250 300 350 400 450 500 5500
0.5
1x 10
-9
Reflection signal
Input Signal
Input Signal
Reflection Signal
Figure 4.21: 175 m Pipe Recordings When D = 39.8 mm and f = 500 Hz
0.045 0.05 0.055 0.06 0.065 0.07 0.075-0.02
0
0.02
Time (s)
Pre
ssu
re (
V)
0.045 0.05 0.055 0.06 0.065 0.07 0.075-1
0
1x 10
-4
0 500 1000 15000
0.5
1x 10
-4
Frequency (Hz)
Am
pli
tud
e (V
)
0 500 1000 15000
1
2x 10
Input Signal
Reflection Signal
Reflection Signal
Input Signal
-13
Figure 4.22: 175 m Pipe Recordings When D = 39.8 mm and f = 1500 Hz
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 98
4.3.2 Different diameters tests
The laboratory experiments considered a number of tests with varying pipe diameters.
Considering the experiment using the 50 m length of pipe as an example, Figure 4.23
shows the attenuation results when pipes with three different diameters, 39.8 mm, 25
mm and 15.17 mm, were used, at temperatures of 20◦C, 23◦C and 22◦C, respectively.
In this figure ’TD’ represents the theoretical measurements and ’D’ refers to the actual
measurements. The results show that for most of the results, and particularly those at
the lower frequencies, the experimental and theoretical results are very consistent. It
can be seen that at the higher frequencies and smaller diameter there is a significant
difference in the experimental and theoretical results. As before this was because of
the high attenuation rates and the reflected signal being affected by background noise.
0 200 400 600 800 1000 1200 1400 1600 1800 20000
0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
Frequency (Hz)
Att
enuat
ion (
dB
/m)
Attenuation for different diameters
TD=39.80mm
TD=25mm
TD=15.17mm
D=15.17mm
D=25mm
D=39.80mm
Figure 4.23: Attenuation Results for Different Size of Pipes
4.3.3 Different temperature tests
As mentioned earlier in this Chapter, temperature has a significant impact on the
transmission of acoustic signals in pipelines. Figure 4.24 illustrates how the attenuation
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 99
changes as a result of variation in temperature. The attenuation in this figure was
calculated using Kirchoff’s theory (3.16).
0 100 200 300 400 500 600 700 800 900 10000.05
0.1
0.15
0.2
0.25
0.3
0.35
0.4
0.45
Frequency (Hz)
Att
enu
atio
n (d
B/m
)
0°C
5°C
10°C
15°C
20°C
25°C
30°C
Figure 4.24: Attenuation Changes When the Temperature Changes
When determining the attenuation α inside a long length of pipeline, which contains
variations in temperature, the attenuation αn in equally spaced subsections (of length
l) of the pipeline, within which the temperature is constant, can be considered.
α = 8.686× ln(pn+1
p1
)/L (4.22)
where L is the length of the full pipeline. The full pipeline is described in Figure 4.25.
...
Ll
p1 p2 p3 p4 p5 pn pn+1
temp1 temp2 temp4temp3 tempn
Figure 4.25: Temperature Gradient Model
The attenuation αn in each subsection of pipe can be calculated using the following
equations.
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 100
α1 = 8.686× ln(p2p1
)/l
α2 = 8.686× ln(p3p2
)/l
αn = 8.686× ln(pn+1
pn
)/l
(4.23)
with
ln(p2p1
)= ln p2 − ln p1
ln(p3p1
)= ln p3 − ln p2
ln(pn+1
pn
)= ln pn+1 − ln pn
ln(pn+1
p1
)= ln pn+1 − ln p1
(4.24)
Then (4.22) can be described by
α =1
n(α1 + α2 + ...+ αn). (4.25)
This means the attenuation for the whole pipeline is equal to the average attenuation
across each of the subsections. The temperature gradient can be considered by intro-
ducing temperature in to the simulator model, which will be explained in Chapter 6.
4.4 Summary
This Chapter has described how three metrics have been applied and compared for
measuring acoustic attenuation in pipes. These three techniques compared and anal-
ysed the RMS, peak value and FFT power of the acoustic signals to provide a measure
of attenuation. A series of experimental tests were used to validate the acoustic at-
tenuation which is predicted using theory developed by Kirchhoff. The results from
these experiments showed that Kirchhoff’s theory was accurate to within approxi-
mately 5% when compared with the experimental attenuation. Errors were measured
for experiments that were conducted at higher frequencies and on pipes with relatively
small diameters. For these tests the attenuation of the acoustic signal was high and
background noise was found to have a significant impact on the results. This is not
a problem for the work described in this thesis as the purpose of this study was to
CHAPTER 4. ATTENUATION OF THE ACOUSTIC WAVE 101
validate Kirchoff’s theory for relatively large diameter pipes (50 mm and above) over
large distances (hundreds of meters or even kilometers). over the longer distances the
higher frequencies will attenuate and it is the lower frequency signals that are impor-
tant. It can therefore be concluded from the results presented in this Chapter that for
the application area that is of interest in this study, Kirchoff’s equation provides an
acceptable approximation of acoustic attenuation.
Chapter 5
Feature/Defects Characterisation
This chapter will discuss how different sizes of features/defects (e.g. erosion, leakage,
etc), as mentioned in Chapter 2, are determined. Different features were added to the
existing pipes for experimental purpose. Limited research has been conducted on this
topic. Among these studies, Morgan’s theory was consistent with the experimental
results. Based on the equations provided by Morgan [10], different features were
characterised. Attenuation was added to the feature characterisation equations to
improve the accuracy of the size approximation.
5.1 Method for the detection of the defects
The basic idea for sizing the defects used the equations presented by Morgan [10]
in 1978. APR-based equipment was used to record the signal. Morgan pointed out
that by using the Acoustic Ranger, the defects inside a tube can be identified quickly.
However, the information from the directly recorded data was not sufficient to obtain
detailed information about the defects themselves. From experience, it was assumed
that the larger the leakage hole was, the smaller the amplitude of the received signal
amplitude would be. The functional scheme of the Acoustic Ranger was explained
in Chapter 3. It has been widely used to identify defects in heat exchangers, power
plants and conventional boilers, to name a few.
102
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 103
The APR based technique was used to detect the defects inside the feed heater tube
in the present study. The initial pulse was sent to the tube and any reflection caused
by defects/features could be recorded by the sensor at the beginning of the pipe.
Different defects are described in Figure 5.1. This figure shows how different defects
are modelled in the sizing procedure. Figure 5.1 (a) shows the clean pipeline without
any defects. Figure 5.1 (b) shows a pipe with a hole in one side of the pipe, the radius of
the hole is a. In Figure 5.1 (c), it is shown that a pipe with erosion, which is equivalent
to partially increase of the ID (2a) and a length of l. Similarly in Figure 5.1 (d), a
pipe with blockage can be equivalent to partially decrease of the ID (2a) and a length
of l.
Inner wall
Outer wall
Hole
Clean pipe
Pipe with
a hole
Erosion
Pipe with
erosion
l
a
ar
Blockage
Pipe with
blockagel
ai
( a )
( b )
( c )
( d )
Figure 5.1: (a) Clean Pipe (b) A Hole Defect in the Pipe (c) An Erosion Defect in thePipe (d) A Blockage Defect in the Pipe
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 104
5.1.1 Holes
The amplitude p of the received signal from a hole in the pipe wall is [10]
p = p0
{1 +
(πD2(W + 1.7a)
a2λ
)2} 12
(5.1)
Where p0 = the amplitude of reflected sound pulse from the end of the pipe when the
tube is without a leak
D = ID of the tested pipe (mm)
a = radius of the hole (mm)
λ = the wavelength of the input sound pulse (mm) @ probe central frequency
W = pipe wall thickness (mm)
The pressure is assumed to be at atmospheric.
λ =1000c
fc(5.2)
fc = centre frequency from the input signal (Hz)
c = speed of sound (m/s), as shown in Chapter 3.
Based on the equation from experimental attenuation, attenuation α can be written
as follows
α = −8.686× ln(p
p1)/L (5.3)
α = −8.686× ln(p0p1
)/L0 (5.4)
L = distance between the leak and the beginning of the pipe (m)
L0 = distance between the end of the pipe and the beginning of the pipe (m)
p1 = the amplitude of the input signal
p = the amplitude of the reflection signal from the leak
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 105
p0 = the amplitude of the reflection signal from end of the pipe
Deviate -8.686 on both sides
− α
8.686= ln(
p
p1)/L (5.5)
− α
8.686= ln(
p0p1
)/L0 (5.6)
Multiply by L and L0 respectively
− αL
8.686= ln(
p
p1) (5.7)
− αL0
8.686= ln(
p0p1
) (5.8)
It follows by
e−αL
8.686 =p
p1(5.9)
e−αL08.686 =
p0p1
(5.10)
Divide the above two equations
ξ =p
p0= e
α(L0−L)8.686 (5.11)
where the attenuation α can also be achieved using Kirchhoff’s attenuation equation.
ξ =
√(1 +
((πD2(W + 1.7a)
a2λ
)2(5.12)
ξ2 = 1 +((πD2(W + 1.7a)
a2λ
)2(5.13)
ξ2 − 1 =((πD2(W + 1.7a)
a2λ
)2(5.14)
Take square root √ξ2 − 1 =
(πD2(W + 1.7a)
a2λ(5.15)√
ξ2 − 1 =πD2W
a2λ+πD21.7
aλ(5.16)
Multiply by a2 and λ
a2λ√ξ2 − 1 = πD2W + πD21.7a (5.17)
Subtract πD21.7a
a2λ√ξ2 − 1− πD21.7a = πD2W (5.18)
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 106
Subtract πD2W
a2λ√ξ2 − 1− πD21.7a− πD2W = 0 (5.19)
Solve this equation as the quadratic equation
Aa2 +Ba+ C = 0, (5.20)
where
A = λ√ξ2 − 1 (5.21)
B = −πD21.7 (5.22)
C = −πD2W (5.23)
Because a can only be positive as it is the diameter of the pipe, (the negative a has
already been neglected)
a =−B +
√B2 − 4AC
2A(5.24)
For the size of the hole, the error might be introduced because of the error of Kirchhoff
attenuation theory, the speed of sound and the centre frequency.
5.1.2 Blockage and erosion
Some defects such as erosion and blockage can be modeled to the decrease or increase
of the pipe inlet wall as shown in Figure 5(c) and (d).
According to Morgan, when the alteration in an area is longer than the length of 100
mm, the change, the amplitude from the reflected signal of the feature can be written
as [10]
p = p0
( A
2− A
)(5.25)
A is the cross section change at the defect
p and p0 have the same definitions as in the last section
ξ =A
2− A(5.26)
Multiply by (2− A)
2ξ − ξA = A (5.27)
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 107
Add ξA
2ξ = A+ ξA (5.28)
Divide by (1 + ξ)
A = 2ξ/(1 + ξ) (5.29)
By definition
A = π(D
2+ ∆)2 − π(
D
2)2 (5.30)
∆ is the change of the radius. Add πD2
π(D
2+ ∆)2 = A+ π(
D
2)2 (5.31)
Divide by π
(D
2+ ∆)2 =
A+ π(D2
)2)
π(5.32)
Square root
D
2+ ∆ =
√A+ π(D
2)2)
π(5.33)
Minus D/2
∆ =
√A+ π(D
2)2)
π− D
2(5.34)
∆ =
√(4A+ πD2)
4π− D
2(5.35)
If ∆ > 0, the new internal diameter increases. In this way, it is an expansion of the
internal diameter, which can sometimes be the defect of erosion.
If ∆ < 0, the new internal diameter decreases. In this way, it is a contraction of the
internal diameter, which can sometimes be the defect of blockage.
This equation applies to both expansion and contraction conditions in the pipe. Nor-
mally it is the case when the reflections from the start and end do not interfere with
each other.
When the length l is less than 100 mm and the start and rear signals interfere with
each other. The ratio ξ between p and p0 can be written as [10]
ξ = (1− eFl) A
2− A, (5.36)
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 108
where l = length of the defect F is a function of shape factor and wavelength of
sound. When the defect is rod or bar, F = 36 and when the defect is a sphere,
F = 25. Multiply by (2− A)
ξ(2− A) = (1− e−Fl)A (5.37)
2ξ − ξA = (1− e−Fl)A (5.38)
Add ξA
2ξ = (1− e−Fl)A+ ξA (5.39)
2ξ = (1− e−Fl + ξ)A (5.40)
Divide (1− e−Fl + ξ) on both sides
A =2ξ
1− e−Fl + ξ(5.41)
5.2 Experimental apparatus
To locate and determine the size of the defects along the pipes, an experiment was
performed to identify specific defects. These pipes were made of aluminum and dif-
ferent kinds of defects, i.e. holes of varying diameters were machined into the pipe
manually .
The test rig shown in Figure 5.2 was built for the experimental test with manually
induced defects along the pipeline at the designated location. Six seamless tubes
(labeled 5, 7, 9, 10, 11 and 12) of 5 m long, 18.6 mm ID, 25.4 mm OD and with a wall
thickness of at least 3.4 mm, were used for the test with some specific features and
only one tube (labeled 15) was kept in a clean state and use as a comparison standard.
The other tubes in the picture were not used for the characterisation test.The details
of the pipes used in the experiment are listed in Table 5.1. The test rig as shown
in Figure 5.2 was AR 6000 with the gas gun. It included a microphone (Sennheiser
ke-4-211-2), a compression driver (Faital HF104) and a DAQ board (NI 4431).
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 109
Table 5.1: Details of the Features in the Test
Number Feature Size(mm)Distance fromthe end(mm)
Total length(mm)
5 hole 0.25 400 50007 hole 0.5 400 5000
9 blockage50 long,
0.2 � reduction1172 5000
10 blockage50 long,
0.4 � reduction1420 5000
11 erosion300 long,
0.2 � reduction940 5000
12 erosion300 long,
0.4 � reduction627 5000
15 clean 5000A hole 2.5 1500 3750B hole 2.5 2500 3750C hole 2.5 700 3750D hole 2.5 3300 3750
5.2.1 Holes detection
Firstly, to obtain the signal caused by the feature, the original signal recorded by
the loudspeaker was filtered and the background noise was removed from the original
signal. Figure 5.3 illustrates the signal after filtering and the zoomed in part is the
signal caused by a hole along the pipe.
Secondly, to determine the centre frequency of the feature signal, which would be used
in the estimation equation, a low-pass filter was applied to both the defect signal and
the reflection from the end of the tube. After that, the centre frequency was defined
as the frequency with the highest energy in the frequency domain.
Thirdly, Short Fourier Transform (SFT) was adopted to the feature signal and com-
pensated the loss due to the attenuation of the pipe in the frequency domain. The
same procedure was applied to the echo from the end of the tube.
Finally, IFFT was applied to the frequency signal. The signal could be recovered
without any attenuation. After the previous processing, the signal could be regarded
as transmitted without any energy loss.
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 110
Figure 5.2: Test Rig
For sizing the holes, Equation (5.21) to (5.24) were used to calculate the size of the
defect (radius measured in mm). The input signal for the first test was a signal with
the amplitude that did not exceed the range of the loudspeaker. Similarly to the first
test, the second test used a signal that was twice larger than the first input signal.
Table 5.2 shows the results from the pipes mentioned in Table 5.1. Table 5.3 illustrates
four pipes with a hole in different positions. The hole sizes, i.e. the radius of the hole,
was 2.5 mm. The error e was obtained by using Equation (5.42).
e =rp − rεrp
× 100% (5.42)
rp actual size machined in the metal pipe (mm)
rε estimated size (mm)
Based on the results in Table 5.2 and Table 5.3, theoretically the error was as high as 6
%. This error could be caused by the error from the speed of sound, the measurement
of the center frequency and the attenuation. Practically there was little difference
if a hole was predicted to measure 0.47 mm but in fact measured 0.5 mm. Potential
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 111
Time (s)
0 0.005 0.01 0.015 0.02 0.025 0.03
Imp
uls
e re
spo
nse
-2
-1
0
1
2
3
-4
10
Figure 5.3: A Reflection Signal Caused by a Hole in the Pipeline
Table 5.2: Hole Size Estimation Results
Test 1Estimatedsize (mm)
Practicalsize (mm)
Distancefrom the end(mm)
Error(%)
Tube 5 0.24 0.25 400 4Tube 7 0.48 0.5 400 4Test 2 Doubled amplitudeTube 5 0.24 0.25 400 4Tube 7 0.47 0.5 400 6
methods yo decrease the error are the calibration of the temperature of the room, which
affects both the speed of sound and attenuation, and detecting the centre frequency
correctly.
5.2.2 Erosion and blockage detection
For long erosion, the reflection signals of the defects could be separated (Figure 5.4);
Equations (5.29) and (5.35) were used to determine the equivalent size of the defect.
Similar to the test for hole sizing, the second set of tests used a signal that was twice as
large as the first signal. The estimated size means the equivalent decrease or increase of
the diameter. Test results are listed in Table 5.4. From the observation of the results,
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 112
Table 5.3: Hole Size Estimation Results (Short Pipes)
Test 1Estimatedsize (mm)
Practicalsize (mm)
Distancefrom the end(mm)
Error(%)
Tube A 2.39 2.5 1500 4.4Tube B 2.36 2.5 2500 5.6Tube C 2.35 2.5 700 6Tube D 2.51 2.5 3300 0.4
improving the amplitude of the input signal, it did not improve the performance of
the equipment. Theoretically the error was up to 5 %. The main error came from ξ
was dependent on the ratio between reflection signal amplitude and the end reflection
amplitude. By improving the accuracy of measuring the two amplitudes, the accuracy
of the prediction can be increased. Practically, it did not make a huge difference when
the prediction was 0.21 mm and the measurement was 0.2 mm in the actual pipe.
Time (s)
0 0.005 0.01 0.015 0.02 0.025 0.03
Imp
uls
e re
spo
nse
-1
-0.8
-0.6
-0.4
-0.2
0
0.2
0.4
0.6
0.8
1
-3
10
Figure 5.4: A Reflection Caused by a 300 mm Erosion in the Pipeline
For partial blockages with a length the reflection signals of the defects could not
be separated (Figure 5.5). Equations (5.35) and (5.41) were used to calculate the
size of the defect. The test results are shown in Table 5.5. The error in the un-
separated condition was up to 5 %, which was mainly caused by the shape factor and
the measurement of the length. The accuracy of the shape factor can be calibrated by
the pipe with a known feature so that it can be calibrated by the known parameters
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 113
Table 5.4: Erosion Size Estimation
Test 1Estimatedsize (mm)
Practicalsize (mm)
Distancefrom the end(mm)
Error(%)
Tube 11 0.21 0.2 increase 1172 5.0Tube 12 0.41 0.4 increase 1420 2.5Test 2 Doubled amplitude
Tube 11 0.22 0.2 increase 1172 10.0Tube 12 0.3728 0.4 increase 1420 7.5
as shown in the equation below. However, the effect of measuring the amplitude still
exists and is unavoidable. Practically it was also acceptable with a difference between
0.38 mm and 0.4 mm.
F = −ln(
1− ξ 2−AA
)l
(5.43)
Time (s)
0 0.005 0.01 0.015 0.02 0.025 0.03
Imp
uls
e re
spo
nse
-2
-1
0
1
2
3
4
5
-3
10
Figure 5.5: 50 mm Blockage
5.3 Application to the real-world
This chapter aims to complete a series of validation tests for the new version of Acoustic
Ranger AR 6000. A series of tests were performed to validate Morgan’s equations to
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 114
Table 5.5: Blockage Size Estimation
Test 1Estimatedsize (mm)
Practicalsize (mm)
Distancefrom the end(mm)
Error(%)
Tube 9 0.20 0.2 increase 1172 0Tube 10 0.38 0.4 increase 1420 5.0Test 2 Doubled amplitudeTube 9 0.21 0.2 increase 1172 5.0Tube 10 0.38 0.4 increase 1420 5.0
characterise a series of features (e.g. holes, blockages and erosion) in the pipeline. All
the tubes in the experiments were machined to match the requirements of the testing,
which can give a thorough picture how the AR 6000 performs.
Based on Equation (5.9) and (5.10), acoustic pressure p at location L and p0 at location
L0 in Figure 5.6 can be expressed as
p = p1e− αL
8.686 (5.44)
p0 = p1e− αL0
8.686 (5.45)
Define M as the minimum parameter (determined by the user) compared to the
L
L0
p1 p p0
Figure 5.6: Illustrated Pipeline with a Feature
background noise of the recorded signal pnoise. As both p and p0 are the key parameters
to locate the size of defects, this means both p and p0 should meet the following
requirements.
p ≥M · pnoise (5.46)
p0 ≥M · pnoise (5.47)
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 115
As p > p0, if (5.47) is met, both p and p0 meet the requirement.
α > 8.686 ln(Mpnoisep1
)/L0 (5.48)
Apply (4.21) to (5.48),
ω
cR
(√ µ
2ρω+ (γ − 1)
√K
2ρωCp
)> ln(
Mpnoisep1
)/L0 (5.49)
All the parameters can be referred to glossary for Chapter 3.
As long as the signal frequency ω, length of the pipe L0 match (5.49), the defect can be
identified based on the different types in Section 5.1.1 and 5.1.2 and the corresponding
size can be calculated by (5.24) or (5.35).
Short length test result is a way to verify the feature equations. Long length with
feature location and size characterisation is similar to the short ones. The short
length verification tests provided a systematic way of testing and verification. The
narrow error offered a promising future research area by applying the equation to
longer length in the later of the thesis regarding simulator when a defect was detected.
This technique can help to provide more details.
According to the theory, as long as the reflection can be identified the size can be cal-
culated based on the reflection amplitude and frequency spectrum. As a validation for
AR 6000, this chapter is mainly as a reference for further research. In the next chapter,
pipeline simulators will be introduced. The defects interpreted by the simulator can
be analysed using the results listed in this chapter. The only barrier is sometimes,
the clean pipe response is not available, which is the majority situations in the actual
situation. This means p0 is not available anymore. Other sizing methodologies should
be explored. The rest of the analysis is out of the focus in this thesis.
5.4 Summary
By using Morgan’s method, a normal hole in the pipe wall could be detected and even
the small one (0.25 mm) could also be sized. The expansion of the pipe diameter can
also be detected. The error of sizing was up to 6% under the normal test.
CHAPTER 5. FEATURE/DEFECTS CHARACTERISATION 116
The revised equations were presented for the blockage and erosion detection. Even
though the equivalent diameter change of the pipe was not totally proper, it was
useful for the start of the research at the beginning part as a simple equivalence.
By changing the amplitude of the input signal, the results show that the normal input
signal was enough to detect the defect and there was no need of to increase the input
signals energy. The error for estimating the size of the defects was within 8% if the
input signal amplitude was not boosted.
Chapter 6
Pipe Simulators and Experimental
Validation
As explained in Chapter 1, features in a simple pipeline system may cause numerous
reflections in the impulse response. However, for APR to be of value then it is essential
that these complex signals can be interpreted. To help with the interpretation of the
results recorded in a pipeline system by the APR equipment, a single pipe simulator
and a pipeline network simulator were designed and validated.
6.1 Background
The data obtained by APR from the real pipeline system is difficult to interpret because
of background noise and overlapped reflection and re-reflection signals caused by cross
section changes in pipes, e.g. T-piece or branches. For example, one pipe main had
three pipeline branches as shown in Figure 6.1 and the recorded impulse response was
plotted in blue in Figure 6.2.
An acoustic signal is split into three at each branch location, which makes it more
difficult to directly identify the signal features associated with defects, even for a
simple pipe setup. In Papadopoulou’s research [1], the idea of comparing the signals
before and after the defects was presented. However, in a number of situations, the
117
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 118
1
30
0.0254
36
0.04
14
0.77
50 25 50 100
MIC
Figure 6.1: Layout of a Pipe Network
Distance from microphone (m)
Imp
uls
e re
spo
nse
0 50 100 150 200
-6
-4
-2
0
2
4
6
8
10
10-6
Figure 6.2: The Response of the Pipe Network
signal before the defects may not be recorded. This is one of the reasons to use the
simulator. To help interpret the results obtained using APR, research into an industrial
simulator has been conducted. The simulator generated the expected response of the
tested system. By comparing the signals from a field test with those generated by
the simulator, any defects will be identified in a more effective and efficient way. In
the example, it is difficult to identify whether there was a defect in the system in
Figures 6.1, as there were many reflections and re-reflections from the joints.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 119
6.2 The single pipeline simulator
The single pipeline simulator was designed to help interpret the response of a single
pipeline system. The single pipeline system is defined as a pipe system without any
branches or T-pieces.
6.2.1 Reflection and transmission coefficients
When a plane wave propagates inside an air-filled cylinder, changes in the cross section
area cause partial reflections. The changes in acoustic pressure as the wave propagates
down the pipe are illustrated using a basic pipeline in Figure 6.3 [84].
The acoustic pressure of the wave before and after the cross section are represented
as p1 and p2 respectively. The particle velocities before and after the cross section
are represented as U1 and U2 respectively. As previously defined, + indicates that
the direction is the same as the propagation direction and − indicates the opposite
direction. According to the continuity of pressure and flow
p+1 + p−1 = p+2 (6.1)
and
U+1 + U−1 = U+
2 (6.2)
p1-
p1+
p2+
Figure 6.3: Pressure Transmission in a Pipeline Unit
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 120
Divide (6.1) by (6.2)p+1 + p−1U+1 + U−1
=p+2U+2
(6.3)
Given the acoustic impedance Z, then according to Kinsler [84]
± Z =p
U±, (6.4)
(6.3) can be rearranged:
p+1 + p−1p+1Z1
+p−1−Z1
= Z1. (6.5)
It therefore follows that
Z1(p+2 + p−1 ) = Z2(p
+2 − p−1 ) (6.6)
Z1p+2 + Z1p
−1 = Z2p
+2 − Z2p
−1 (6.7)
Z1p+2 − Z2p
+2 = −Z2p
−1 − Z1p
−1 (6.8)
Then the reflection coefficient r1,2
r1,2 =p−1p+1
=Z2 − Z1
Z2 + Z1
. (6.9)
As the impedance Z is defined as
Zi =ρicisi
with i = 1, 2 (6.10)
with respect to the density of air ρi and the speed of sound ci in the ith section of the
pipe, and in the same environment, there is no difference between the air density and
the speed of sound, i.e. ρ1 = ρ2 and c1 = c2, we have
r1,2 =Z2 − Z1
Z2 + Z1
=
ρ2c2S2− ρ1c1
S1
ρ2c2S2
+ ρ1c1S1
=1S2− 1
S1
1S2
+ 1S1
=S1 − S2
S1 + S2
. (6.11)
Similarly, a series of reflection and transmission coefficients between two adjacent
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 121
segments of pipe are given in [84]:
r1,2 =S1 − S2
S1 + S2
(6.12)
r2,1 =S2 − S1
S1 + S2
= −r1,2 (6.13)
t1,2 =2× s1S1 + S2
= 1 + r1,2 (6.14)
t2,1 =2× s2S1 + S2
= 1− r1,2 (6.15)
where S1 and S2 are the cross section areas of segments 1 and 2 respectively; r1,2 is the
reflection coefficient from segment 1 to 2 and t1,2 is the transmission coefficient from
segment 1 to 2; similarly r2,1 is the reflection coefficient from segment 2 to 1 while t2,1
is the transmission coefficient from segment 2 to 1.
6.2.2 Digital waveguides
Digital waveguides [106] are digital filter designs that model the acoustic wave propa-
gation inside of the pipe in a lossless way throughout the whole length; with the losses
and dispersion described using filters. They offer filter-like structures to simulate the
modified physical systems [94,107]. Digital waveguides were widely used in the musical
field for musical sound synthesis and computational models [108–110].
A simplified digital waveguide structure is shown in Figure 6.4.
Figure 6.4: Waveguide Filter Structure
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 122
The excitation signal U corresponds to the energy supplied to the whole system at the
beginning of the system. The output Y represents the travelling wave component at
the end of the selected point. D0 is the minimum digital time delay in the system over
a round-trip distance. F is the filter that describes the remaining losses in the system
over the round-trip.
The method of using digital waveguides will not be discussed in depth in this thesis.
However, there is a comprehensive review of this topic in the literature [111]. It offers
a basic model for the simulator models. In Section 6.2.2 and Section 6.3.2 of this
chapter, more detail for the modelling is provided.
6.2.3 The cylindrical model to build pipeline
A tubular object, i.e. pipe, whose cross-sectional area varies with axial distance can
be modelled by a series of i discontinuously joined cylindrical segments. The length
of each segment is l and it has a corresponding one-way travel time T , that is defined
as:
T =l
c(6.16)
where c is the speed of sound. Figure 6.5 shows the division of one section of a pipeline
into several segments, each with different cross section areas.
With reference to Figure 6.6, the generalised scattering equation is presented to process
how the signal propagates and is reflected when the signal hits the barrier between
two adjacent segments [61]:p+i+1,i(nT )
p−i+1,i(nT )
=1
(1− ri,i+1)
1 −ri,i+1
−ri,i+1 1
p+i,o(nT )
p−i,o(nT )
(6.17)
with i = 1, 2, ...,M and n = 1, 2, ..., N , where M is the number of all the segments
and N is the number of samples recorded.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 123
SOURCE TUBE
TEST OBJECT
Segment 1 2 3 4 5 … i-7 i-6 i-5 i-4 i-3 i-2 i-1 i
l
Figure 6.5: Discretizing a Pipeline
p+1,i p+
1,o
p+2,i
...
p+i,op+
i,i
p-1,i
p-2,i
p-1,o
p-i,i p-
i,o
Segment 1 Segment i
Figure 6.6: Signal Propagating Along the Pipe
A space-time diagram is displayed in Figure 6.7. The arrows indicate the direction of
the signal propagation (forwards and backwards) at different times in each segment.
The pressures at the left and right sides of each segment are also displayed. For
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 124
example, when signal p+1,o[T ] hits the barrier between segment 1 and segment 2 at
time T, signal p+2,i[T ] and signal p−1,o[T ] are generated according to the transmission
and reflection coefficients. There is an assumption that no backward travelling wave
is present in a segment before a forward travelling wave has reached that segment.
0 1 2 3 4 5
0
T
2T
3T
4T
5T
6T
p+0,i[0T]
p-0,o[0T]
Segment i
Time t
p-1,o[T] p+
2,i[T]
p+2,o[2T]
p+3,i[2T]
p+3,o[3T]
p+4,i[3T]
p+4,o[4T]
p+5,i[4T]
p+5,o[5T]
p+1,i[0T]
p+1,o[T]
p+1,i[2T]
p+1,o[3T]
p+2,i[3T]
p+2,o[4T]
p+3,i[4T]
p+3,o[5T]
p+4,i[5T]
p+4,o[6T]
p+1,i[4T]
p+1,o[5T]
p+2,i[5T]
p+2,o[6T]
p+5,i[6T]p+
3,i[6T]p+1,i[6T]
p-1,i[2T]
p-2,o[2T]
p-2,i[3T]
p-3,o[3T]
p-3,i[4T]
p-4,o[4T]
p-4,i[5T]
p-5,i[6T]
p-1,o[3T]
p-1,i[4T]
p-2,o[4T]
p-2,i[5T]
p-3,o[5T]
p-3,i[6T]
p-4,o[6T]p-
2,o[6T]
p-1,o[5T]
p-1,i[6T]
p-0,o[2T]
p-0,o[4T]
p-0,o[6T]
Figure 6.7: Space-time Diagram [61,112]
To include attenuation losses along the pipeline, discrete time filters are applied as the
acoustic signal is passed through each segment [61]:
p+i,o(nT ) = p+i,i((n− 1)T ) ∗ xi(nT ) (6.18)
p−i,i(nT ) = p−i,o((n− 1)T ) ∗ xi(nT ) (6.19)
where ∗ represents convolution. Sequence xi(nT ) is the loss filter x(nT ) inside the ith
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 125
segment, as described in Section 6.2.4.
6.2.4 Attenuation filter
To produce an algorithm capable of simulating the behaviour of an acoustic pres-
sure wave travelling in a cylindrical void requires a suitable means of accounting for
attenuation. The initial Keefe’s model was introduced in 3.2.4.
As validated in Chapter 4, Kirchhoff’s attenuation equation matched the experimental
attenuation with an error of less than 5 %. The comparison between Kirchhoff’s
equation and Keefe’s equation is shown in Figure 6.8. It is clearly illustrated that
both of the attenuation equations match each other closely after 20 Hz. The main
frequency of the wave for testing industrial pipe was between 20 Hz and 100 Hz. The
absorption value mainly relies on the temperature and the sampling frequency.
100
101
102
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
Frequency (Hz)
Att
enu
atio
n (
dB
/m)
Kefee
Kirchhoff
Figure 6.8: Attenuation Comparison Between Kirchhoff’s And Keefe’s Equation
The proposed simulator is a causal time-stepping solver; therefore, (3.35) must be
transformed into discrete time. To perform this transform, (3.35) is discretized and
inverted using the inverse Fast Fourier algorithm as per Amir [6] and Sharp [51]. The
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 126
resulting discrete time filter x(nT )is typically beset by ripple due to phase disconti-
nuities in the frequency domain filter. To remove the ripple, the rotating phase [113]
was applied to the filter X(ejω). To diminish the time delay caused by the rotating
phase model, an all pole model [6] was used by performing a M pole transfer function
on filter x′(nT ). M is normally adjusted according to the length of the attenuation
filter.
1. To remove the discontinuity, the rotating phase method works by forcing the
phase to be zero at f = 12F (applied to equation (3.35)).
X ′(jω) = e−γ(ω)lejωl
ϑp(2π12F ) (6.20)
After discretizing X ′(jω) and applying IFFT to equation (6.20), a new discrete
time domain filter x′(nT ) is achieved.
2. The autocorrelation of filter x′(nT ) was calculated, where m = 0, 1, ..., N − 1.
R(m) =N−1−m∑n=0
x′(nT )x′((n+m)T ) (6.21)
3. The predictor coefficients ak for the all-pole model were calculated using Durbins
recursive method [6], where k = 1, 2, ...,M . The gain G was calculated using ak
and R(m).
G =
√√√√R(0) +M∑k=1
akR(k) (6.22)
4. The frequency domain filter X ′(ejω) is evaluated on the unit circle, where f =
0, 1N, 2N, ..., N−1
N.
X ′(ejω) =G
1 +40∑k=1
ake−jωk(6.23)
5. A ripple-free filter approximation x′′(nT ) was calculated by applying IFFT to
X ′(ejω).
The combined model is a minimum phase model, which means that the delay caused
by the tube is missing. The missing delay could be expressed explicitly by adding a
delay to the forward signals and subtracting it from the backward signals.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 127
6.3 The pipeline network simulator
To expand the current study for single pipes, research into pipe networks was con-
ducted. Pipe network systems are used widely in natural gas transportation, particu-
larly in domestic gas distribution systems. A pipe network simulator provides a way to
help the interpretation of the measurements obtained when APR is applied to pipeline
networks. The pipe network simulator was based on the single pipe simulator, how-
ever, special processing was introduced for the branch joints. To speed up the single
pipe simulator, a non-equal segment model based on the feature location was used to
build the pipe network simulator.
The division of one pipeline with different acoustic impedance changes is shown in
Figure 6.9.
The model presented here is a discrete time model, which discretizes the tubular
pipeline by concatenating cylindrical segments. Different from the previous work
in [114], which divided a tube into segments of the same length, the pipe is divided
into a set of segments with different lengths separated by known features of the pipe,
which improved simulation speed. The length of the ith segment is
li = Ni ×c
fs(6.24)
Ni = [lpic/fs
] (6.25)
where the speed of sound and the sampling frequency are represented by c and fs
respectively; lpi is the practical length of the ith segment and [a] means the nearest
integer to a.
6.3.1 Reflection and transmission coefficients at joints
A generic Y-piece is shown in Figure 6.10. The junction is modelled as a point in a
lossless scenario and does not include any losses. A forward transmitting signal in +x
direction is considered to split into three parts at the junction. The resulting signals
are reflected signal in -x direction and transmitted signals in +y and +z directions.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 128
Segment SX1 SX2 SX3 SX4
SOURCE TUBE MAIN PIPE
BRANCH 1
BRANCH 2
SOURCE TUBE MAIN PIPE
BRANCH 1
BRANCH 2
Segment SZ
1
Seg
men
t S
Y1
Figure 6.9: Pipeline with Branches Discretization
0
x
y
z
Figure 6.10: A Generic Y-piece-branch
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 129
Given x, y, z as the unit distance in each direction as shown in Figure 6.10, in the main
pipe shown on the left in the x direction. pi is the acoustic pressure inside of the pipe
and Ui is the volume velocity.
p0 = Aej(ωt−kx) +Bej(ωt+kx),
U0 = Aej(ωt−kx)+Bej(ωt+kx)
ρ0c0S0.
(6.26)
where A is the amplitude of the input signal and B is the amplitude of the reflection
signal at the reflection point. In the first branch in the y direction, A1 is the amplitude
of the signal transmitting in the +y direction.p1 = A1ej(ωt−ky),
U1 = A1ej(ωt−ky)
ρ1c1S1.
(6.27)
Similarly, in the second branch in the z direction, A2 is the amplitude of the signal
transmitting in the +z direction.p2 = A2ej(ωt−kz),
U2 = A2ej(ωt−kz)
ρ2c2S2.
(6.28)
At the location x = y = z = 0, the diameter of the pipe is far smaller than the
wave length. Because of the continuity of pressure and volume velocity, there exist
continuity conditions on acoustic pressure and the flow [84], such that:
p0 = p1 = p2 (6.29)
U0 = U1 + U2 (6.30)
Dividing (6.30) by (6.29) gives:
U0
p0=U1
p1+U2
p2(6.31)
Evaluating this and (6.4)1
Z0
=1
Z1
+1
Z2
(6.32)
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 130
S0
ρ0c0(A−B) =
S1
ρ1c1A1 +
S2
ρ2c2A2 (6.33)
Given
Yi =Siρici
(6.34)
with i = 0, 1, 2,
Y0A−BA+B
= Y1 + Y2 (6.35)
and thenA
B=
1− Y1+Y2Y0
1 + Y1+Y2Y0
=Y0 − (Y1 + Y2)
Y0 + (Y1 + Y2). (6.36)
Again, in the same environment, there is no difference between the air density and the
speed of sound, i.e. ρ0 = ρ1 = ρ2 and c0 = c1 = c2, we have
r+0 =A
B=Y0 − (Y1 + Y2)
Y0 + (Y1 + Y2)=S0 − (S1 + S2)
S0 + (S1 + S2). (6.37)
Similarly, all the reflection coefficient ri for different pipes at the joint are
r+0 =S0 − (S1 + S2)
S0 + (S1 + S2)(6.38)
r+1 =S1 − (S0 + S2)
S1 + (S0 + S2)(6.39)
r+2 =S2 − (S0 + S2)
S2 + (S0 + S2)(6.40)
according to [84], where the same gas propagates in all pipe branches in this study, S0,
S1 and S2 are the cross section areas of segments in the x, y, z direction respectively;
The subscript ’+’ means a signal is transmitting in the x+ direction.
The transmission coefficient ti = 1 + ri is still applicable to the branch pipelines.
6.3.2 The network model
A generic pipeline network is shown in Figure 6.11. Each branch in this network can
be modelled by a series of n cylindrical segments, similar to the way the single pipe
simulator was modelled in Section 6.2. For the joints between the branches, such as
joint A, B, C and D in Figure 6.11, the following approach was used.
Each junction causes three major changes in acoustic propagation, shown in Fig-
ure 6.12. If a subscript ′+′ is used to designate a wave travelling in the forward
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 131
B
CA D
Figure 6.11: A Generic Pipeline Network
direction and a subscript ′−′ for a wave travelling in the backward direction, then in
reference to Figure 6.12
p−0 (nT ) = p+0 (nT ) · r+0 + p−1 (nT ) · t−1 + p−2 (nT ) · t−2 (6.41)
p+1 (nT ) = p+0 (nT ) · t+0 + p−1 (nT ) · r−1 + p−2 (nT ) · r−2 (6.42)
p+2 (nT ) = p+0 (nT ) · t+0 + p−1 (nT ) · t−1 + p−2 (nT ) · r−2 (6.43)
p0+ p2
+
p1+
p0-
p1-
p2+ p0
-
p1+
p2-
(a) (b) (c)
Figure 6.12: Signals Change at the Junction
To deal with the branch joints, a dimension is added to label different branches in the
pipe network in the network model with one dimension for time and one for segments.
The way to deal with the branch dimension is to set designated connection locations at
the beginning of the simulator. Every branch can be considered as a window with their
own time-space diagrams, which is the same as Figure 6.7. In each window, the signal
propagates in the same way as a single pipe simulator except for the junctions between
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 132
branches. The connections between the windows contribute to the third dimension,
which is the branch dimension. The pressure values at the connections are updated
every cycle during the simulation.
6.3.3 Summary of the pipe simulators
Both the single pipe simulator and pipe network simulator use the time domain signals
to describe the acoustic signal transmitting inside the pipeline. When a layout of the
pipeline system is known, the impulse response can be generated by the simulator.
The pipeline system can be numerically modelled using the step-by-step method. Any
signal at each segment is available by initiating the output in the simulator. This helps
to interpret signals which are recorded at any accessible points of the pipeline system.
The network simulator uses a nodal model to discretise the pipeline. Compared to
the equally discretized model, this saves computing time for convolution inside each
segment. For a certain length of the pipe without any significant features, the output
signal can be calculated immediately by the convolution of input signal of this segment
and the attenuation filter when it is modelled in the nodal mode. This improves the
calculation efficiency compared the the equal step model.
The minimum step of calculation l is determined by the sampling frequency fs and
speed of sound c. This has been discussed earlier in this chapter to define the step of
discretisation. In the actual test, sampling frequency of 1 kHz is used very often. For
a long pipeline with hundreds of kilometers, the minimum step effect is less compared
to the whole length of the pipe. However, if the pipe is short within a few meters,
the minimum step has to be defined small enough and this requires high sampling
frequency. Otherwise, some key features will be interpreted in the wrong location.
In summary, the simulator developed in this chapter is efficient and applicable to the
long pipes, especially the nodal model in network simulator. Mentioning hundreds of
kilometers, low sampling frequency device can also provide a way to record the signals
which reflect the features/defects of the pipeline.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 133
6.4 Laboratory validation of the single pipeline sim-
ulator
6.4.1 Experimental setup for single pipeline simulator
To validate the accuracy of the simulator, a series of experimental tests were carried
out. The apparatus used in these tests is shown schematically in Figure 6.13. The pipes
used in the lab tests were new polyethylene pipes with an outer diameter of 50 mm and
internal diameter of 39.8 mm. A Fostex FF105WK loudspeaker was connected to the
beginning of the test tube via a plastic adaptor, which had the same diameter as the
test tube. Two 1/4-inch Bruel and Kjaer DeltaTron pressure-field microphones were
inserted in the test pipe via two 7 mm holes so that the diaphragm of the microphones
was flush inside the pipe wall at the either end of the test tube. Signal output and
acquisition were handled by NI-9263 and NI-9234 modules; sampling was performed
simultaneously across all channels at 51.2 kHz.
MIC1
LOUDSPEAKER TEST TUBE
AMPLIFIER
COMPUTER
A/DD/A
MIC2
DISSIPATION TUBE
COMPACT DAQ
BOARD
Figure 6.13: Experimental Setup
The distance between the loudspeaker and MIC1 was 0.2 m. The tube length between
the two microphones was 100 m while the second part of the pipe (dissipation pipe) was
50 m. As the excitation signal used in the test was ≈ 0.25 s (that is 0.25×340 = 85 m),
both the test pipe and the dissipation pipe were long enough to make sure that the
transmitted signal and the reflected signal from the end of the pipe did not interfere
with each other in the microphone recordings.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 134
6.4.2 Results and analysis
A series of digitally generated short burst sinusoidal waves with different frequencies
were used as input signals. The frequencies of the input signals ran from 50 Hz to
1000 Hz in 10 Hz increments. For each test, the signals recorded by both microphones
were time windowed so that only the section of either signal containing the sine burst
was present. The RMS value of the time windowed data was then calculated. Testing
was repeated 5 times at each frequency and results were averaged to reduce the effects
of any environmental noise. Attenuation between the two microphones was calculated
as per [2]:
αp = −8.686× ln(p2p1
)/l (6.44)
where l is the length between the two microphones, p1 and p2 are the RMS values of
time windowed pressure signals recorded by the two microphones and αp is experimen-
tal attenuation in dB/m (1Np = 20 log10 e = 8.686 dB).
The simulator was configured so that the pipe dimensions, such as diameter and length,
and gas properties, such as pressure and temperature, matched the experimental set-
up. The same series of input signals were sent through the simulator to generate the
simulated response. In Figure 6.14 the attenuation, according to (6.44), attenuation is
plotted against frequency for both the experimental and the simulated response. The
error between the two data sets is presented in Figure 6.15. The simulated response
was also compared to the direct use of (6.44) and found to give very similar results;
slight deviation is to be expected due to numerical errors. Figures 6.14 and 6.15 show
that the experimental results are very similar to those gained via simulation, thus
validating the pipe simulation algorithm.
In the results from the tests, the maximum error between the simulation and exper-
imental results was 3.02%. It was observed that higher errors were recorded at the
higher frequencies. This was most likely caused by the lower signal to noise ratio(SNR)
achieved at high frequency due to the greater attenuation. It was noticeable that for
frequencies between 460 Hz to 860 Hz, the experimental attenuation was consistently
lower when compared with simulation results. The reason for this was unclear, but
may have been caused by background noise during the test.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 135
0 200 400 600 800 1000 0.05
0.1
0.15
0.2
0.25
0.3
0.35
0.4
0.45
Frequency (Hz)
Att
enu
atio
n (
dB
/m)
Simulation Attenuation
RMS attenuation
Figure 6.14: Attenuation Results for Pipe with ID = 39.8 mm
0 200 400 600 800 1000 -4
-3
-2
-1
0
1
2
X: 910
Y: -3.023
Frequency (Hz)
Err
or
(%)
Figure 6.15: Error Between the Simulation And Experiment Results
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 136
6.4.3 Further demonstration of experimental tests
To further test the capabilities of APR for surveying pipeline networks, prototype
hardware consisting of a speaker-microphone system that could be connected to a gas
main, using a 1” BSP threaded connection was developed. A schematic showing the
hardware layout is presented in Figure 6.16. The microphone is inserted 200-500 mm
into the gas main while the speaker is located outside the main but is in direct contact
with air in the main. The hardware is connected to a laptop via a ’Peli’ case that
contains all the necessary amplification and data acquisition equipment. Figure 6.17
is a photograph of the system including the Peli case.
Figure 6.16: Layout of the Prototype Hardware
To evaluate the prototype system and the mathematical model a series of tests were
first performed in the laboratory using 50 mm MPDE pipe, Figure 6.18 shows the
layout used for testing. Table 6.1 lists the features present in the pipe and their
location for each of the six tests. For each test two measurements were taken, first
with the microphone installed in the pipe to the right of the prototype hardware
facing L4 (as shown in Figure 6.18) and second with the microphone installed in the
pipe to the left of the prototype hardware, facing L1. Taking readings at two different
microphone locations gives directionality, allowing us to determine if a given feature is
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 137
in the pipe section to the left of the prototype hardware or in the section to the right.
Plastic box
Wiring
Speaker
Gas main Guide tubeConnection tube
Microphone
Figure 6.17: Diagram of the Prototype System Used for Testing Air Filled Pipes
Prototype
hardware
Microphone
Ball valveL1
L2L3 L4 L5
48.896.2
122.9 98.750.1
0.2
Figure 6.18: Layout of the 50 mm Pipework Used in Laboratory Testing; L1, L2 and
L4 Represent Pipe Feature Locations While L3 And L5 Are Open Ends, All Lengths
Are in meters
Table 6.1: Test Rig Feature Table
Pipe feature LocationTest 1 Clear pipe n/aTest 2 Partially closed ball valve L1Test 3 Fully closed ball valve L1Test 4 300 ml water pool L2Test 5 25 � 200 mm long solid cylinder inside pipe L4Test 6 32 � 200 mm long solid cylinder inside pipe L2
Figure 6.19 shows the simulated and measured responses of the pipe system shown in
Figure 6.18 when it was free from features, as per test 1 in Table 6.1. Figures 6.20-6.24
present the results from Tests 2-6 (Table 6.1) where additional features are present in
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 138
the pipe. In Tests 2-6 the results were analysed in a way that mimics the proposed
analysis method of real pipe systems. The top plot in Figures 6.20-6.24 shows a
simulation of the clear pipe that was generated using knowledge of the pipe layout.
The second plot is the measured response. By comparing the expected response with
the actual response it is possible to identify and locate any unexpected signal features
and provide information on the geometry of what is causing these signal features.
The bottom plot in Figures 6.20-6.24. shows a simulation of the pipe that includes
the physical item(s) that are suspected to be causing the unexpected signal features.
This simulation can be used to confirm the presence of expected and unexpected pipe
features (water pools, misbehaving valves, unknown services), and provide details of
their location and size.
In Figure 6.19, the top plot shows the expected response from a clear pipe while the
bottom plot shows the measured response. The two plots are similar and there are no
unexpected features in the measured response. It is evident in the measured response
that the signal feature at ≈ 100 m results from a feature that lies to the right of the
prototype hardware at L5 because the signal recorded with the microphone in the
right position (in red) arrives before the signal recorded with the microphone in the
left position (blue) and as such the feature is clearly associated with the open end at
L5, vice versa is true of the signal feature at ≈ 125 m and therefore this feature is
clearly associated with the open end at L3.
Simulation of clear pipe
Distance from microphone (m)
Imp
uls
e re
spo
nse
Imp
uls
e re
spo
nse
Microphone left
Microphone right
Measured response of clear pipe
Distance from microphone (m)
Figure 6.19: Comparison Results Between Simulation Results And Experimental Re-
sults in Test 1
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 139
Simulation of clear pipe
Distance from microphone (m)
Distance from microphone (m)
Distance from microphone (m)
Imp
uls
e re
spon
seIm
pu
lse
resp
on
seIm
pu
lse
resp
on
se
Microphone left
Microphone right
Measured response of pipe with partially closed ball valve
Simulation of pipe with partially closed ball valve
Figure 6.20: Comparison Results Between Simulation Results And Experimental Re-
sults in Test 2
In Figure 6.20, comparing the simulation of a clean pipe with the measured response
(top and middle plots) gives a clear indication of a partial blockage at L1 (Figure 6.18).
The shape of the measured signal at ≈ 50 m indicates a blockage (rise followed by fall),
because the signal features from both open ends of the pipe are present it is apparent
that the blockage is only partial and from the order of arrivals of the microphone left
and microphone right signals it is ascertained that the partial blockage is to the left
of the prototype Hardware. The simulation result in the bottom plot confirms that a
partial blockage L1 is congruent with the results obtained in the measured response
(middle plot).
In Figure 6.21, comparing the simulation of a clean pipe with the measured response
(top and middle plots) indicates a full blockage at L2 (Figure 6.18). The shape of the
measured signal at ≈ 50 m is indicative of a blockage (rise followed by fall), because
the signal features from the open end at L3 (Figure 6.18) is not present it is inferred
that there is a complete blockage. The order of arrivals of the microphone left and
microphone right signals suggest that the blockage is to the left of the prototype
hardware. The simulation result in the bottom plot closely resembles the measured
response and so confirms the diagnosis.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 140
Imp
uls
e re
spon
seIm
pu
lse
resp
on
seIm
pu
lse
resp
on
se
Microphone left
Microphone right
Distance from microphone (m)
Distance from microphone (m)
Distance from microphone (m)
Simulation of clear pipe
Measured response of pipe with fully closed ball valve
Simulation of pipe with fully closed ball valve
Figure 6.21: Comparison Results between Simulation Results And Experimental Re-
sults in Test 3
Imp
uls
e re
spon
seIm
pu
lse
resp
on
seIm
pu
lse
resp
on
se
Microphone left
Microphone right
Distance from microphone (m)
Distance from microphone (m)
Distance from microphone (m)
Simulation of clear pipe
Measured response of pipe with 300 ml water pool at L2
Simulation of pipe with 300 ml water pool at L2
Figure 6.22: Comparison Results Between Simulation Results And Experimental Re-
sults in Test 4
In Figure 6.22, comparing the simulation of a clean pipe with the measured response
(top and middle plots) indicates a partial blockage at L2 (Figure 6.18). Although the
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 141
signal feature at ≈ 97 m overlaps with the signal feature from the open end at L5 it is
possible to ascertain from the order of arrival of the microphone left and microphone
right signals that the small signal feature at ≈ 97 m comes from the left section of the
pipe while the bigger feature caused by the open end at L5 comes from the right section.
The simulation result in the bottom plot confirms the location and characteristics of
the unexpected feature and is used to provide further sizing information.
In Figure 6.23, comparing the simulation of a clean pipe with the measured response
(top and middle plots) gives a clear indication of a partial blockage at L4 (Figure 6.18).
The shape of the measured signal at ≈ 52 m is indicative of a blockage (rise followed
by fall), because the signal features from both open ends of the pipe are present it
is apparent that the blockage is only partial and from the order of arrivals of the
microphone left and microphone right signals it is ascertained that the blockage is to
the right of the prototype hardware. The simulation result in the bottom plot confirms
that a partial blockage at L4 is congruent with the measured results and can be used
to improve locational accuracy and give sizing information.
Imp
uls
e re
spon
seIm
pu
lse
resp
on
seIm
pu
lse
resp
on
se
Microphone left
Microphone right
Distance from microphone (m)
Distance from microphone (m)
Distance from microphone (m)
Simulation of clear pipe
Measured response of pipe with cylindrical blockage at L4
Simulation of pipe with cylindrical blockage at L4
Figure 6.23: Comparison Results Between Simulation Results And Experimental Re-
sults in Test 5
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 142
In Figure 6.24, comparing the simulation of a clean pipe with the measured response
(top and middle plots) indicates a partial blockages at both L2 and L4 (Figure 6.18).
The shape of the unexpected features suggest they are caused by blockages and as the
signal from both open ends of the pipe are present, this suggests that both blockages
are only partial and from the order of arrivals of the microphone left and microphone
right signals the direction of each blockage relative to the prototype hardware can be
ascertained. The simulation result in the bottom plot confirms that partial blockages
at L2 and L4 match the measured results. The simulation result also reveals that
the partial blockage at L2 causes a greater restriction than the partial blockage at L4
despite the signal feature at ≈ 50 m being larger than the signal feature at ≈ 97 m.
This anomaly is caused by losses in acoustic energy as sound travels along the pipe.
Imp
uls
e re
spon
seIm
pu
lse
resp
on
seIm
pu
lse
resp
on
se
Microphone left
Microphone right
Distance from microphone (m)
Distance from microphone (m)
Distance from microphone (m)
Simulation of clear pipe
Measured response of pipe with cylindrical blockage at L4 and L2
Simulation of pipe with cylindrical blockage at L4 and L2
Figure 6.24: Comparison Results Between Simulation Results And Experimental Re-
sults in Test 6
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 143
6.5 Laboratory validation of the network pipeline
simulator
To validate the proposed network pipeline simulator, a series of tests were conducted
in the laboratory.
6.5.1 Experimental setup for the network pipeline simulator
The pipes used in these tests were new polyethylene pipes (MDPE pipe). Details of
the test equipment are listed in Table 6.2. Sampling was performed simultaneously
across all channels at 96 kHz, the highest rate for the analogue output channel, to
minimize the discretization error.
Table 6.2: Equipment Used in the Tests
Equipment Model
Amplifier YAMAHA A-S300
Loudspeaker SEAS H1208-08 L22RN4X/P
Microphone Bruel & Kjaer DeltaTron 1/4-inch 4944-A
Data Acquisition Board National Instruments USB-4431
6.5.2 Reflection and transmission coefficients validation tests
Two different layouts of the pipes, shown in Figure 6.25 and 6.26, were used to validate
the model used within the simulator. All the pipes used in this test had an internal
diameter (ID) of 39.8 mm and an outer diameter (OD) of 50 mm. The capped ends
are marked as E1 and E2. The main test points, where the microphone was attached,
were the locations marked L1, L2 and L3. The distance between L1 and J1 was 24 m
while L1 was 25 m from the loudspeaker. The length between J1 and L2 was 50 m and
it was 50 m from J1 and L3. To ensure the accuracy of the test, the same microphone
was inserted into the pipe where it was flush inside the pipe during each test.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 144
The excitation signal was a logarithmic sine sweep with 221 samples ranging from
20 Hz to 1 kHz and was played five times back to back so that a complete cyclic signal
could be achieved in the middle of the data sequence. The resulting pressure signal
was recorded by the microphone inserted in the pipe.
The averaged periodic response signal of the second to the fourth sequences was de-
convolved with the periodic input signal to determine the impulse response of the
pipe. This impulse response included the acoustic response of the pipe, the acous-
tic response of the speaker system and enclosure and the electrical response of the
laptop/DAQ/amplifier.
MIC
LOUDSPEAKER MAIN PIPE
AMPLIFIER
COMPUTER
A/DD/A
BRANCH
DAQ BOARD
J1 E2
E1
L3
L2L1
Figure 6.25: Pipe Layout A
6.5.3 Results and analytics
The equivalent pipeline network was simulated using parameters to match those used
in the experiment. The comparison results are shown in Table 6.3. As the attenuation
for a tubular pipe has already been validated in previous work [114,115], the reflection
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 145
MIC
LOUDSPEAKER MAIN PIPE
AMPLIFIER
COMPUTER
A/DD/A
BRANCH 1
DAQ BOARD
J1
BRANCH 2
E1
E2
L3
L1
L2
Figure 6.26: Pipe Layout B
and transmission coefficients were calculated as
r1,23 =p
psim(6.45)
and
t1,2 = t1,3 =p
psim(6.46)
where p is the peak value of the reflected or transmitted wave in the experiment; psim
is the peak value of idealised signals when there is no T-piece branch. From Table 6.4,
it is clear that the maximum error for the reflection and transmission coefficients that
was measured in this experiment was 5.697%.
Table 6.3: Peak Values at Each Location
L1 (×10−5) L2 (×10−5) L3 (×10−5)
Layout ASimulation(without branch) psim 7.227 4.703 4.695
Experiment p -2.393 2.956 2.978
Layout BSimulation(without branch) psim 10.683 7.206 7.192
Experiment p -3.530 4.622 4.597
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 146
Table 6.4: Errors Between the Simulation And Experiment Results
r t1,2 t1,3
Layout ASimulation -0.333 0.667 0.667Experiment -0.331 0.629 0.634
Error(%) 0.601 5.697 4.948
Layout BSimulation -0.333 0.667 0.667Experiment -0.330 0.641 0.639
Error(%) 0.901 3.898 4.198
6.5.4 Network Pipeline simulator validation tests
Pipeline tests for setups with different numbers of branches
0.9
50
.95
0.9
5
7
3
LOUDSPEAKER
MIC
14
7550
1 2
100
J1E1 E2
E3
(a)
4
125
1
50
E1 E2
36
E4
50
5
(b)
7
4
14
7550
1 2
50
J1E1 E2
E3
(c)
36
E4
50
6
MIC
MIC
0.3
0.3
0.3
6
6
5
J3
J3
LOUDSPEAKER
LOUDSPEAKER
Figure 6.27: Layouts of the Pipe Network Setup
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 147
Figure 6.27, shows the layout of the experimental setups for pipeline networks with
two and three branches separately. In this figure all distances are labeled in meters.
All the ends of the pipes were capped to simulate a closed system. The ID of the
main pipe was 39.8 mm while the ID of the 14 m branch pipe was 25.4 mm. The
pipe system was excited by a loudspeaker using a logarithmic sine sweep as with the
previous tests.
All the simulator parameters were specified to match the experimental setup in Fig-
ure 6.27. The pipe used in the main section had a ID of 39.8 mm and the branches had
IDs of 25 mm. If not specified otherwise, all the experimental set-ups had the same
pipe diameters in this section. In the simulation, the input signal was set to be a clean
short burst of an impulse. However, the input signal in actual situation, will not be the
idealised burst, which caused the slight differences between the simulated signal and
experimental signal at each feature. The simulation results are plotted and compared
with the experimental results in Figure 6.28 - Figure 6.30. This figure shows that a
number of features can be identified in the trends and that each feature is associated
with reflections that result from a change in cross sectional area. For example, the
first feature F1 in Figure 6.28 is caused by the reflection from J1 in Figure 6.27 (a).
The locations that caused the relative reflections are listed in Table 6.5.
The differences in amplitudes between the simulated and experimental results were
caused by small errors in the calculation of the attenuation of the acoustic signal
along the pipe and from errors associated with the T-piece reflection and transmission
coefficients, which are not known precisely. However, given that in an industrial set-
ting, there will be debris and other features in the pipelines, the results show that the
network simulator can simulate a pipeline network and generate an acoustic response
that is similar to that obtained from the real system, and it can therefore be used to
help identify and locate unexpected defects in a pipeline system.
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 148
Distance from microphone (m)
Imp
uls
e re
spo
nse
SimulationExperiment
0 20 40 60 80 100 120 140 160-1
0
1
210
-4
Figure 6.28: Comparison Between Simulation And Experiment Results for Layout (a)
Distance from microphone (m)0 20 40 60 80 100 120 140 160-1
Imp
uls
e re
spon
se
0
1
210
-4
SimulationExperiment
Figure 6.29: Comparison Between Simulation And Experiment Results for Layout (b)
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 149
Distance from the microphone (m)
Imp
uls
e re
spo
nse
0
-10 20 40 60 80 100 120 140 160
1
2 10-4
SimulationExperiment
Figure 6.30: Comparison Between Simulation And Experiment Results for Layout (c)
Referring back to a previous example in Section 6.1, that used the same layout, a hole
was inserted in the pipe. Assuming that the precise location of the hole was unknown,
the acoustic response of the pipe was determined and analysed. By comparing the
experimental result with the simulation results in Figure 6.31, the location of the
7 mm hole was identified as the point in the expanded section of the plot where
the experimental and simulated results begin to differ. This location was manually
confirmed to be the correct location of the hole.
All the features in different layouts are summarised and lised in Table 6.5. For example,
in Layout (a), feature F1 represents the feature of J1, F2 is the reflection from E3
and features F3 and F4 represents E2 and E1, respectively as labeled in Figure 6.27.
Feature 5 is the combination from both E3 and E1. Similarly, the rest of features in
Layout (b) and (b) can be explained by the features in the table.
Table 6.5: Locations That Caused Each Feature in Different Layouts
Layouts F1 F2 F3 F4 F5(a) J1 E3 E2 E1 E3+E1(b) J3 E4 E2 E1 E4+E2(c) J3 J1 E3+E4 E2 E1
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 150
Figure 6.31: Comparison Between the Simulation And Experiment Results for a Three-
branches Pipeline
A pipeline test with a loop and branch
The pipe layout when a loop was located in the network is shown in Figure 6.32. This
network was also simulated in the simulator. It was noted that because of the limited
space in the laboratory, all the pipes that were used in the experiment were coiled up.
This explains how a 14 m loop was able to connect two pipe sections that were 25 m
apart in the pipe main.
MIC
1005050 25
30
14
Figure 6.32: Layout of a Pipe Main Containing a Loop And a Branch
The experimental and simulated acoustic response of the pipe is shown in Figure 6.33.
This figure shows that the simulator was able to generate an acoustic response for the
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 151
pipe network containing a loop with a high degree of accuracy, once again confirming
the suitability of the simulator for estimating pipeline behaviour.
Figure 6.33: Comparison Between the Simulation And Experiment Results for the
Layout in Figure 6.32
A pipeline test for detecting a defect in a branch
A further pipeline layout was set up as shown in Figure 6.34. The pipe main for
this set up contained with four branches of varying length. A cylindrical object with
dimensions 155 mm × 8.15 mm was inserted in the pipe as a partial blockage. APR
testing revealed that there was something located approximate 86 m from the end
of the pipe. By conducting a APR second test from the branch as shown in Figure
6.36 and triangulating the results, it was clear that the partial blockage was correctly
located along branch 1 where it is marked with a circle in Figure 6.34. This result
confirmed that the simulator could be used to help identify partial blockages in pipe
networks. However, with pipeline networks it may be necessary to determine the APR
from multiple locations in the network. Separate tests were conducted to determine
the exact location of the blockage, from pipe main and pipe branch. By a single result
recorded from pipe main as shown in Figure 6.35, it is difficult to identify the location
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 152
of the blockage. However, with another set of result from pipe branch as shown in
Figure 6.36, it is confirmed that the blockage is located in the pipe branch.
MIC50505050 25
Defect 20
30
14
36
MIC
Figure 6.34: Layout of a Pipe Main with 4 Branches
Figure 6.35: Comparison Between the Simulation and Experiment Results for the Pipe
Main with the Layout Depicted in Figure 6.34
CHAPTER 6. PIPE SIMULATORS AND EXPERIMENTAL VALIDATION 153
Figure 6.36: Comparison Between the Simulation and Experiment Results When a
Partial Blockage Was Located in a Pipeline Branch, as per the Layout in Figure 6.34
6.6 Summary
A series of validation tests demonstrated that the experimental attenuation is consis-
tent with those that were estimated using the simulator; the maximum experimental
error was found to be 3.02% in the pipeline containing no branches. A pipe network
simulator has been designed to model the propagation of acoustic waves in a pipe
network containing branches and loops. To model the signal propagation at branch
joints, reflection and transmission coefficients were considered and the resulting simu-
lator validated using a number of experimental scenarios. Comparison of the simulated
and experimental results were very consistent and believed to be suitable to help in the
interpretation of APR data collected from real gas pipelines. The following Chapter
shows results that were obtained when the APR equipment and simulator was applied
to industrial gas pipelines.
Chapter 7
Industrial Case Studies
7.1 A case study for an industrial pipeline - Case 1
This section describes how the single pipeline simulator was used to support the sur-
veying of a live industrial pipeline. In the experiment, approximate details of the
pipeline, such as changes in cross section and valve locations were known. Using the
simulator it was possible to compare the acoustic response of the pipe with the sim-
ulated response and identify any inconsistencies. The overall aim of this study was
to identify and locate a pig that had become stuck in the pipe. The pipeline was
approximately 12 km long and was pressurised to approximately 5 MPa.
7.1.1 Description of the test
To generate an excitation signal with sufficient energy and the appropriate frequency
content to travel the required distance, a pulse of pressurised gas was injected into the
pipeline using the Echometer Remote Fire Gas Gun.
The resulting reflection sequence was recorded by a pressure transducer housed in the
same assembly used to inject the pressure pulse. The pressure of the gas in the pipeline
was 6.1 MPa and the temperature was approximately 8.9◦C. The pressure pulse was
injected in to the pipeline 10 times and the acoustic response recorded for each test
154
CHAPTER 7. INDUSTRIAL CASE STUDIES 155
was averaged to increase the SNR. The composition of the compressed gas used in the
industrial test, which affects the speed of sound in the gas, is listed in Table 7.1.
Table 7.1: Gas Composition
Gas Component Formula Gas Composition (% Mole)
Methane CH4 81.35
Nitrogen N2 6.59
Carbon Dioxide CO2 0.04
Ethane C2H6 6.64
Propane C3H8 3.56
I-Butane C4H10 0.56
N-Butane C4H10 0.95
I-Pentane C5H12 0.14
N-Pentane C5H12 0.01
Helium He 0.16
Figure 7.1 shows the recorded reflections as the excitation pulse propagated along
the test pipeline. The excitation pulse was introduced at time 0 s, but unfortunately
it was not possible determine the precise pulse that was injected as the microphone
located within the equipment saturated. Without the precise input signal it is not
possible to use the simulator and therefore a method was developed to obtain an
estimate of the injected signal. This method involved analysing the signal produced
by a known feature in the pipeline, in this case a change in internal diameter from 186
mm to 216 mm. Deconvolution with an appropriate time domain propagation filer, as
presented in Section 6.2.4, of the reflected signal from this feature was then used to
determine the approximate signal that was injected into the pipe.
The injected signal was relatively complex because the single pulse that was injected
into the pipe was reflected from various pipe fittings that were within approximately
20 m of the injection point. The method of recovering the actual input signal was the
inverse of how the attenuation filter was used to implement wave propagation. The
excitation signal was achieved by applying (7.1) - (7.3). The feature lying between
CHAPTER 7. INDUSTRIAL CASE STUDIES 156
9.97 s and 10.4 s (zoomed section of Figure 7.1) was used as p−i,o, the output backward
signal at ith segment. xi(nT ) was the time domain attenuation filter obtained if
the segment length was taken to be equivalent to the spacing between the pressure
transducer and where the reference signal p−i,o was reflected. The recovered input signal
at the first segment p+1,i, that was used as the input signal for the simulator, is shown
in Figure 7.2.
p−i,o(nT ) = p−i,i(nT ) ∗−1 xi(nT ) (7.1)
p+i,o(nT ) = p−i,o(nT )/ri,i+1 (7.2)
p+i,i(nT ) = p+i,o(nT ) ∗−1 xi(nT ) (7.3)
0 10 20 30 40 50 60 70 80
-0.01
-0.005
0
0.005
0.01
0.015
Time (s)
Imp
uls
e R
esp
on
se
10 10.2 10.4-5
0
5x 10
-3
Figure 7.1: Raw Data with the First Distinguished Feature
7.1.2 Results of the industrial testing
By comparing the simulated signal with the recorded experimental signal, any un-
expected features in the pipeline can be revealed. There were altogether 12 major
reflections that were identified in Figure 7.3. The first reflection occurred after 9.97 s,
CHAPTER 7. INDUSTRIAL CASE STUDIES 157
which corresponded to a known bore reduction (the pipe bore changed whenever the
pipe went under a road). It was followed by several reflections corresponding to the
location and size of other known features. Each of these features corresponded to
changes in internal pipe diameter of approximately 10 mm, corresponding to a change
in cross sectional area of 10%, (2002 − (200 − 10)2)/2002 = 9.75% . The only obvi-
ous difference between the expected and measured signals lay at 18.53 s, as shown in
Figure 7.4. Using the simulator, the feature was investigated and interpreted to be a
short unexpected blockage of approximately 50%. The pipe was later inspected using
a radiographic camera which located the blockage to within 3 m of that estimated
using APR. The blockage was confirmed to be a cleaning pig that had become stuck
in the pipe.
Figure 7.2: Recovered Input Excitation Signal
The reflection at 65.8 s resulted from the end of the pipe as shown in Figure 7.5. The
results from this test and relevant validation tests by the simulator, together with
knowledge of SNR, suggest that the APR technique, utilising the Echometer Remote
Fire Gas gun to deliver the acoustic signal, could detect a full blockage at up to 32 km
under similar conditions as with this test. In generating this distance it is assumed
that a feature is only detectable when the amplitude of the feature signal is at least
CHAPTER 7. INDUSTRIAL CASE STUDIES 158
twice that of the noise. This detection length could be extended if the gas inside the
pipeline was at higher pressure or the input impulse amplitude was increased.
Impuls
e R
esponse
Time (s)
Simulation
Experiment
Figure 7.3: Reflection Signals from the Pipeline
0 20 40 60 80 100 120
-0.01
-0.005
0
0.005
0.01
Time (s)
Impuls
e R
esponse
Simulation
Experiment
18.5 19 19.5-0.01
0
0.01
Figure 7.4: A 50% Blockage Interpreted by the Simulator
The maximum distances for different blockage percentages detected by the present
APR equipment for this particular pipeline condition (eg. pressure and temperature,
CHAPTER 7. INDUSTRIAL CASE STUDIES 159
etc.) are listed for a variety of pipelines in Table 7.2. For example, if a 1 m pipe is
to be surveyed under the same conditions, then it should be possible to detect a full
blockage at 17.1 km and a 50% blockage at 13 km, etc. As many sub-sea pipelines
operate at approximately 100 bar and have diameters of approximately 1 m, the table
provides an indication of the maximum length that the current APR technique could
be applied to.
0 10 20 30 40 50 60 70
-4
-2
0
2
4
x 10-3
Time (s)
Impuls
e R
esponse
Simulation
Experiment
65.5 66 66.5-5
0
5x 10
-3
Figure 7.5: Reflection From the End of the Pipe
Table 7.2: Maximum Detected Distances When Pressure = 6.1 MPa And Temperature= 8.9◦C, with the Distances Measured in Meter
Percentage
Distances D(mm)
20 50 100 200 500 1000
10% 1200 3100 6000 12500 31000 6000020% 1700 4300 8500 17500 43500 8500030% 2050 5100 10000 20500 52000 10000040% 2300 5700 11500 23000 59000 11500050% 2550 6300 12500 26000 64000 13000060% 2800 6900 14000 28000 69500 13500070% 3050 7500 14500 29500 78500 14500080% 3150 7500 15000 31000 80500 15000090% 3250 8100 15500 32000 81500 170000100% 3300 8150 15700 32400 82000 171000
CHAPTER 7. INDUSTRIAL CASE STUDIES 160
7.2 A case study for an industrial pipeline - Case 2
In a further test APR, using the Echometer Gas gun was used to detect a subsea
valve opening and closing. The layout of the field test was shown in Figure 7.6.
Unfortunately the composition of gas was unknown to us. Topsides pressure during the
tests was 25 Mpa, and ambient (surface) temperature was 16 ◦C. Sea bed temperature
would have been significantly lower and estimated to be 6 ◦C. Sampling frequency was
1 kHz for all the tests; this was limited by equipment. In total, 10 acoustic tests were
performed and the average response determined to improve the SNR. The speed of
sound was estimated to be 366 m/s for this on-site test after calibration, which was
calculated based on the known feature reflection location l and the time it took to
travel t, c = l/t .
The acoustic pulse was injected after 1.5 s and as with an earlier test which caused
the first 1.5 s empty in the signal, it was not possible to correctly ascertain the precise
pulse that was injected because the microphone saturated. A similar method to that
applied in Section 7.1 was applied to estimate the input signal.
A comparison of the experimental and simulator results are shown in Figure 7.7.
A reflection was identified at the location of ’Spool Item 14’ in the layout diagram
(Figure 7.6). Through consultation with plant operators, this reflection was believed
to be from the bottom of the riser or a 90◦ bend. The simulator helped to simulate
the response of Figure 7.6 and the feature was identified based on the difference at the
zoom in area n Figure 7.7. A 70 % closed (cross section percentage) at Valve 16 was
also simulated to offer the difference when the opening size of the valve changed. The
difference was shown between the red (fully closed) and green color (70% closed) in
Figure 7.7.
CHAPTER 7. INDUSTRIAL CASE STUDIES 161
Figure 7.6: Layout of the Testing at Alba
1.5 2 2.5 3 3.5 4 4.5 5 5.5 6-0.1
-0.05
0
0.05
0.1
Time (s)
Impuls
e re
sponse
Original closed record
70% closed simulation
Fully closed simulation
2.7 2.8 2.9 3
-0.01
0
0.01
0.02
Figure 7.7: Comparison Between the Simulation And Experiment Results
7.3 A case study for an industrial pipeline - Case 3
As part of the on going commercialisation of the Acoustek R© APR technique at the
University of Manchester, several live trials were performed on live gas distribution
pipeline networks. The results of these trials are analysed in this Section to further
validate the developed simulator. Among the various trials that were conducted, the
trial at ”Haylie Gardens” could be used to test the single pipeline simulator. Further
trials will be introduced in Case 4 to Case 6 to validate the network simulator. In
CHAPTER 7. INDUSTRIAL CASE STUDIES 162
each of the trials the experimental equipment that was used is imaged in Figure 7.8.
The aluminum ’box’ contains a 150 mm loudspeaker which was connected to the pipe.
The small yellow cable houses two microphones, which were inserted into the pipe.
Figure 7.8: Test Equipment
The pipe main was 76.2 mm spun iron with the condition clean and free of debris.
Live trial Haylie Gardens demonstrated that the system was capable of detecting and
locating features over a range of 100 m. Figure 7.9 gives the site layout. The distances
of each part are shown in the figure.
Figure 7.10 shows plots from the Acoustek R© software (top plot) and the simulator
(bottom plot) and Table 7.3 presents the table of features detected by the Acoustek R©
equipment. The simulation results used the same set up as the layout shown in Fig-
ure 7.9. The reflections at direction Dir 2 was considered in the simulation. However,
compared to the recorded signal, feature 25F1 was not obvious in the recording from
on-site staff. if observed at distance 10.8 m, the reflected signal from 25F1 is shown
in the simulation while because of the original input signal with long ringing, the first
reflection was difficult to identify in the original signal. The simulator generated the
response of the pipeline when it is under the idealised situation with clean and smooth
inside of the pipeline. It is also shown that, the amplitude of the reflections are higher
CHAPTER 7. INDUSTRIAL CASE STUDIES 163
in the simulation than those in the recording. One reason might be that the inside
surface of the pipe was not idealised clean and the coarse surface caused energy loss
inside of the pipe.
Speaker location
and mic direction
Gas main
Excavation
Ex1
Ex2
Dir 1
Dir 2 25F1
25F2
25F3
76.2
Cast
Stand pipe
62.4
103.1
Hayli
e G
ard
ens
Figure 7.9: Layout of Trial Haylie Gardens
CHAPTER 7. INDUSTRIAL CASE STUDIES 164
Table 7.3: Features in Layout of Trial Haylie Gardens
Feature code Features detected Direction Distance Confirmed
25F1 Blockage/reduction Dir 2 10.8m No
25F2 branch/expansion Dir 1 63.1m Stand pipe at 62.4 m
25F3 Large blockage/reduction or cap Dir 1 103.2m Capped end visible at 103.1m
Distance from microphone (m)
Distance from microphone (m)
Simulation results
Field test results
Imp
uls
e re
spon
seIm
pu
lse
resp
on
se
Figure 7.10: Impulse Response of Trial Haylie Gardens
7.4 A case study for an industrial pipeline - Case 4
In addition to the Haylie Gardens trial, there were a number of trials conducted on
pipeline networks. For each trial, the simulator was used to estimate the response of
the network, with parameters set to correspond to the layouts provided and measured
by the on-site staff.
In case 4, the investigated test was conducted at Newmains Rd, Renfrew. The pipe
main was 152.4 mm ductile iron with extremely dirty condition filled with gravel like
substances. The main contained two abandoned sections (the two branches at the
top of Figure 7.11. These abandoned mains were capped. This trial result has been
included to show the performance of the system in conditions when the pipe is not
CHAPTER 7. INDUSTRIAL CASE STUDIES 165
clean.
Speaker location
and mic direction
Gas main
Excavation
New
Main
Road
Ex1
Abandoned
Abandoned
20F1
N
Du
ctil
e Ir
on
Dir 1
61
63
Figure 7.11: Layout of Trial Newmains Rd
The standard approach for inspecting gas distribution pipeline is to insert small cam-
eras on long tethers (up to 50 m). However, for this study the pipe was so dirty that a
camera could not be inserted and attempts were being made to pump the main clear
of debris prior to replacement. The debris in the main caused a high noise level on the
signal obtained from the Acoustek R© equipment but still some information could be
obtained: at the suspected location of the two abandoned mains, there is a clear fea-
ture in the signal resulting from the capped ends. Figure 7.11 gives the site layout and
CHAPTER 7. INDUSTRIAL CASE STUDIES 166
Table 7.4: Features in Layout of Trial Newmains Rd, Renfrew
Feature code Features detected Direction Distance Confirmed
20F1 Raise in signal level Dir 1 61.1 Abandoned mains on maps at 61m and 63m
Figure 7.12 shows plots from the Acoustek R© software and the pipe network simulator
and presents the table of features in Table 7.4 detected by the Acoustek R© equipment.
This plot shows the response of the simulator when it modeled the pipeline using the
same layout as in Figure 7.11. From the observation, at distance 60-70 m the second
abandoned main is estimated to be further than 63 m based on the difference in the
plots.
Distance from microphone (m)
Distance from microphone (m)
Simulation results
Field test results
Imp
uls
e re
spon
seIm
pu
lse
resp
on
se
Figure 7.12: Impulse Response of Trial Newmains Rd
7.5 A case study for an industrial pipeline - Case 5
The pipe main was 101.6 mm spun iron with clean condition and free of debris. Live
trial Crocus Grove was performed at Location Ex1. Figure 7.13 gives the site layout
while Figures 7.14 shows the plots from the Acoustek R© software and the pipe network
simulator and presents the table of features detected by the Acoustek R© equipment.
CHAPTER 7. INDUSTRIAL CASE STUDIES 167
Speaker location
and mic direction
Gas main
Excavation
Cro
cus
Gro
ve
63 mm PE
Ex3
Ex2
Ex1
11
9.8
95.2
72.1 11.3
90 mm PE
Siphon
49.6
N
23F1
23F2
23F3
23F5
22.2
Figure 7.13: Layout of Trial Crocus Grove
Prior to the arrival most of the site had been inspected using a camera, however,
the siphon (23F3) was unknown and was not present on any maps. The APR test
revealed a significant and unexpected feature at 93.8 m; due to an equal tee this signal
feature could relate to one of two sections in the 101.6 mm main. To confirm which
stretch of pipe the feature was in, another trial was performed at Excavation Ex3. This
second test confirmed that the feature was directly in front of the test location and
that the feature was large enough to stop any signal passing it. Following discussion
with operators and a subsequent camera inspection, a siphon was later confirmed as
the cause of this reflection. As well as finding the unexpected siphon the Acoustek R©
CHAPTER 7. INDUSTRIAL CASE STUDIES 168
Distance from microphone (m)
Distance from microphone (m)
Simulation results
Field test results
Imp
uls
e re
spon
seIm
pu
lse
resp
on
se
Figure 7.14: Impulse Response of Trial Crocus Grove
system correctly located all other large features present in the network. The size
of siphon was also evaluated by the simulator and the simulated results are shown
in Figure 7.14. A siphon refers to a tube in an inverted ’U’ shape, which causes a
liquid to flow upward without help of pump. In the simulator, a 30% expansion was
modeled at the location 23F3 in Figure 7.13 as an equivalent feature of a siphon. The
reflection at location 95.2 m in the plot underneath was from the simulated siphon,
which matched the recorded signal.
7.6 A case study for an industrial pipeline - Case 6
This trial was conducted at Harburn Ave, Livingston. The pipe main was 200 mm
ductile iron with clean condition. Operatives requested the use of the Acoustek R©
system to test an area for blockages following a water ingress problem. From a single
location the Acoustek R© system was able to confirm that approximately 500 m of gas
main was clear of obstructions. Figure 7.15 gives the site layout and Figure 7.16 shows
plots from the Acoustek R© software and the pipe network simulator and presents the
CHAPTER 7. INDUSTRIAL CASE STUDIES 169
table of features detected by the Acoustek R© equipment. The Acoustek R© system
detected a pipe feature (31F3 in Figures 7.15 and 7.16) at 354.2 m. Unfortunately this
feature could not be fully confirmed: gas maps show a branch nearby but the distance
estimated from the map is ≈390 m. The detected features are shown in Table 7.5.
The simulator was built based on the layout in Figure 7.15. Because of the complexity
of the pipe layout, not all the features can be reflected in the recorded signal of the
actual equipment because of the low signal to noise ratio. The simulator can quickly
generate the response of the system based on the drawing from the test site. For
example, at distance around 140 m, there is no obvious reflections from the original
recording. However, based on the simulation results, the reflection should be shown
in the plot. The reason might be, in reality, there was no cross section change instead
of what is described in the drawing or the reflection was too weak to be identified. In
general, the simulator offered an accurate view to get the response of a known layout
of the tested object.
Table 7.5: Features in Layout of Trial Harburn Ave
Feature code Features detected Direction Distance Confirmed
31F1 tee/expansion Dir 2 47.2m Found with camera at 46.8m
31F2 blockage/reduction Dir 1 98.4m Reduction from 200mm to 6” present on maps
31F3 tee/expansion/siphon Dir 1 354.2m reduction to 125mm and tee nearby on maps
Speaker location
and mic direction
Gas main
Excavation
NDir 1
Dir 2Ex1
152.4
D
I
180 PE 125
PE
125 PE
200 DI200 DI
200 PE
250 DI
125 PE
150 D
I
Approx 390
31F1
Ap
pro
x 9
0
46.8
Approx 100
Figure 7.15: Layout of Trial 31
CHAPTER 7. INDUSTRIAL CASE STUDIES 170
Distance from microphone (m)
Distance from microphone (m)
Simulation results
Field test results
Imp
uls
e re
spo
nse
Imp
uls
e re
spon
se
Figure 7.16: Impulse Response of Trial 31
7.7 Summary
A number of field tests were described in this chapter. The results from these field
tests were used to validate both the single pipeline and network pipeline simulators.
The capabilities and accuracy of the simulator was demonstrated by applying it to
results obtained from an active industrial pipeline, approximately 10 km in length. In
this case, the simulator accurately generated the reflections along the pipeline and
revealed all of the known pipe features. Using the simulator it was possible to detect
and characterise cross-sectional changes of 10% in the pipeline. In the first case study,
Case 1, a blockage was successfully identified in a pipeline with length of more than
12 km. In Case 2, a suspicious defect was identified and located by the simulator. In
Cases 3 to 6, simulated results matched what was obtained from field tests. From the
results of the field testing, it was ascertained that both simulators provided very useful
information that can be utilised to help identify defects along the pipeline system.
Chapter 8
Discussions, Conclusions and
Future Work
The work presented in this thesis has expanded the functional range of existing APR
simulation tools and as a consequence improved the practical application of the tech-
nology. The assumptions of previous researchers have been experimentally validated in
long range applications and new simulation methods have been introduced to improve
simulation accuracy and execution time in pipelines with the long lengths associated
with gas distribution networks. Thorough validation of the new simulation tools was
performed, both in the laboratory and in extensive field trials.
8.1 Discussions
(1) Application of APR
APR offers considerable benefits in the monitoring of industrial pipelines. The reason
for this is that the impulse response of a pipe, which is determined when applying APR
technology, contains significant information regarding features and conditions within
the pipe. APR operates by injecting an acoustic impulse into the gas within the tested
object (pipelines being the test subject of this work) and measuring the reflections
that are produced, whenever this signal encounters a change in acoustic impedance
171
CHAPTER 8. DISCUSSIONS, CONCLUSIONS AND FUTURE WORK 172
as it propagates along the length of the pipeline. There are many applications of
APR in that have been reported in the literatures, such as its application to detect
seismic layers, reconstruct medical airways, reconstruction and defect characterisation
of musical instruments and the detection of abnormal conditions within pipelines. A
review of relevant research was provided in Chapter 3.
The focus of the work described in this thesis has been the application of APR tech-
nology for the detection and location of holes, blockages and erosion in pipelines. To
illustrate the capabilities of APR in this field, an extensive set of experiments have
been performed in the laboratory at the University of Manchester. Larger sized pipes
have also been studied in field trials. The field tests were conducted in different lo-
cations across the UK to demonstrate the capabilities of APR for the inspection of
gas pipeline systems. Major defects were identified from the acoustic response of the
tested pipelines. The acoustic response of the pipes was also able to reveal the location
of the defect, through knowledge of the speed of sound in the gas and the transmission
time of the acoustic signal.
(2) Attenuation validation
Although several research studies have attempted to validate Kirchhoff’s acoustic at-
tenuation theory previously, these studies have produced variable results with errors of
up to 15% being reported, as explained in Chapter 4. To gain a better understanding
of the attenuation of acoustic signals in long lengths of pipelines, a comprehensive set
of experiments was conducted to analyse the behaviour of acoustic signals in pipes.
The results of this work was able to validate the use of Kirchoff’s theory within a
pipeline simulator that was able to estimate the acoustic response of pipelines and
pipeline networks.
The results of the experimental studies demonstrated that Kirchhoff’s equation un-
derestimated the acoustic attenuation measured in the experiments by up to 5%. 5%
is believed to be within the noise that would be measured in real environments where
the internal wall of the pipeline can contain debris and corrosion which will affect the
acoustic attenuation. This result validated the choice of using Kirchoff’s equation as
the basis for the pipeline simulators that were developed.
CHAPTER 8. DISCUSSIONS, CONCLUSIONS AND FUTURE WORK 173
Analysis of the experimental results showed that the higher frequencies had attenuated
faster than the lower frequencies and the acoustic signals attenuated faster in small
bore pipes compared with pipes with larger diameters.
(3) Feature characterisation
There are different categories of features/defects that may exist along a pipeline, such
as expansion/contraction of the inner diameter. To help develop a model that was
able to simulate the reflections produced by these features a series of experiments was
conducted to characterise 15 pipes that had a variety of features, such as holes and
blockages introduced within them.
For these pipes, the presented models were able to approximate the acoustic response
of features such as holes and blockages with very good accuracy. For example a change
in the cross sectional area within a pipeline could be estimated with an accuracy of
approximately 7 %, suggesting that if there is a 0.25 mm change in pipeline diameter
then the models would estimate the size of this reduction as 0.23 mm, which in most
practical applications of APR technology would be insignificant.
(4) Pipeline simulators building methods
In practice, even for a simple pipeline, the response can be complex and difficult to
interpret directly from the reflected signal. To help identify whether there is a defect
inside the pipe, a reference signal, indicating the expected response of the pipe if there
are no defects within it, can be highly beneficial. By comparing the actual acoustic
response of the pipe with that expected, any defects or other abnormalities can be
identified.
Theoretically, when a pipeline system is in its initial state, which means the piping is
new and only just commissioned, the reference signal is achieved by performing tests
using APR. However, in practice, it is not easy to obtain the initial response of a
pipeline. In this way, a simulator is required to generate the idealised response of a
system, which provides the reference signal from the initial state.
To develop a simulator to estimate the acoustic response of a pipe, a loss filter, based on
CHAPTER 8. DISCUSSIONS, CONCLUSIONS AND FUTURE WORK 174
Keefe’s approximation was introduced in Chapter 6. This filter defined the attenuation
and losses inside a number of segments that the pipe was divided into. Both the
transmission and reflection coefficients for changes in cross sectional area were derived
based on the continuity of pressure and particle velocity. These coefficients were
included in the scattering which helped describe how the signal propagates along the
pipeline system.
For pipeline networks, a corresponding simulator was built using a network model
that included all branches in the system. In addition to considering attenuation on
the straight lengths of pipe, transmission and reflection coefficients at the joints were
also introduced into the scattering equations.
Both the single pipeline and network simulators were validated using tests conducted
in the laboratory and through comprehensive field tests. These tests demonstrated
that the developed simulators provided an accurate estimate of the acoustic response
of the pipelines.
(5) Experimental validations in the laboratory
A series of laboratory experiments were conducted to validate the developed sim-
ulators. Different pipe layouts were used with different sizes of pipe main and pipe
branches under different lengths. Defects, such as holes and blockages, were introduced
into the pipeline. The recorded response of the experimental pipelines were compared
with the responses estimated using the simulators (single pipeline and pipeline net-
work simulators). In one experiment a water blockage, a common and difficult to
locate problem in gas distribution pipelines, was introduced into the pipe. A model
developed to simulate water pooling inside a pipe was successfully used to estimate
the real response of a water pool.
For the network simulator, transmission and reflection coefficients were validated in
the laboratory using a comprehensive set of tests. In these tests, different sizes of
branches at various locations were introduced. Thorough testing the network simulator
was found to accurately approximate the acoustic response of all the tested pipeline
networks. Furthermore, the simulator was able to locate and estimate the size of a
CHAPTER 8. DISCUSSIONS, CONCLUSIONS AND FUTURE WORK 175
partial blockage that was introduced in the network.
(6) Field tests validations
A series of field tests were conducted at a variety of locations around the UK to test
the capability and accuracy of the simulators. All these tests used live pipelines which
contained debris and many other features and were therefore provided a thorough test
of the capabilities of the ability of the simulators to aid in the interpretation of APR
data. In the tests, the pipe sizes ranged from 25 mm to 250 mm with pipe lengths of
up to 12 km. The owners of the pipelines provided details of the composition of the
gas within the pipelines (which was necessary to estimate the speed of sound) and the
layout of the pipeline networks.
The pipelines contained numerous changes in cross sectional area, particularly in the
test involving the 12 km pipeline, as discussed in Chapter 7. The measured acoustic
response of this pipeline was particularly difficult. However, the pipeline simulator
was able to aid in the interpretation of this response and using it, a cleaning pig that
had become stuck in the pipe was detected and located to within 3 m of its actual
position.
For the field test results analysed in Chapter 7, the gas composition inside of the pipe
was unavailable. However, it was still possible to estimate the speed of sound in the gas
through calibration using known obstructions in the pipeline. All the results obtained
using the pipeline simulators were consistent with the results obtained from the field
tests and in some of the trials the simulator was able to detect and locate unexpected
features in the pipelines.
8.2 Conclusions
Kirchhoff’s equation was demonstrated to be applicable to long lengths of pipelines
with large diameters. The difference between experimental and theoretical results was
consistently less than 5%.
CHAPTER 8. DISCUSSIONS, CONCLUSIONS AND FUTURE WORK 176
The simulation tools developed in this thesis were shown to provide an accurate method
for estimating the acoustic response of pipelines and pipeline networks.
Through industrial testing, it was shown that APR could detect a blockage in a pipeline
at a distance of up to 12 km, with the limitation of the technique, using the same
equipment and pipeline in this case, being approximately 35 km.
Both simulators developed in this thesis generated idealised responses of pipeline sys-
tems, which have been validated both in the laboratory and in field tests.
The developed simulators can help interpret APR measurements of complex pipelines
and pipeline networks.
8.3 Future work
The following future works are recommended.
• Setting up experimental conditions with adjustable pressures and temperatures
Currently all the tests conducted in the laboratory were within a certain range
of temperature from 20 to 27◦C and the pressure was atmospheric. In the future,
it would be recommended that greater variation in temperature and pressure be
introduced.
• Adding the estimation of the size correctly and efficiently in the simulator
It is recommended that the simulators have an auto-sizing function embedded
within them. With the information of the correct size of the defect, the operator
can decide what actions should be taken instantly. Although there has been a
considerable amount of work undertaken in this area by Kemp et al., applications
have been restricted to small and short bore tubular objects, with the main
application being musical instruments. Unlike musical instruments with clean
internal walls, industrial pipelines are usually very dirty. Furthermore, industrial
pipelines are considerably longer than musical instruments, which can introduce
scale-up problems.
CHAPTER 8. DISCUSSIONS, CONCLUSIONS AND FUTURE WORK 177
• Monitoring pipelines in real-time
The ideal situation for pipeline systems is that they can be monitored and ab-
normalities detected in real-time. Extending the research reported in this thesis
to real-time application would be highly beneficial.
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