the resulting thermal stresses in pipes, two solids namely; steel and cooper and
... analysis. The numerical scheme employing control volume approach is ...
Thermal Stresses in Pipes
By Iy ad A l-Z ah arn ah , BSc. & MSc. In Mechanical Engineering
This thesis is subm itted to D ublin C ity U niversity as the fulfillm ent o f the requirem ent for the aw ard o f degree o f
Doctor of Philosophy
Supervisors
P rofessor M .J. H ashm i P rofessor B.S. Y ilbas
School of M echanical & M an u factu rin g E ngineering D ublin C ity U niversity
April 2002
DECLARATION
I hereby certify that this material, which I now submit for assessment on the programe o f study leading to the award o f Doctor o f Philosophy is my own work and has not been taken from the work o f others save and to the extent that such work has been cited and acknowledged within the text o f my work.
I.D No.: 9897021
D ate: ! 3 - 0 S ^ Z 0 o 2
'REF£RENCE
I dedicate this thesis to my beloved parents, brother and sister
ACKNOWLEDGMENT
First and foremost, all praise to Almighty, Allah Who gave me the courage and patience to carry out this work and I Ask to accept my little effort. May He, Subhanahu-ta-Aala, guide the humanity and me to the right path.
My deep appreciation is to my Ph.D., thesis advisors Professor M.S.J. Hashmi (Dublin City University, Ireland) and Professor B.S. Yilbas (King Fahd University of Petroleum and Minerals, Saudi Arabia) for their continuous support and matchless patience throughout this work. Their suggestions were always valuable and working with them was always indeed a wonderful and learning experience. Continuously, they were supportive and kind to me.
I would also like to thank both Dublin City University in Ireland and King Fahd University o f Petroleum and Minerals in Saudi Arabia for providing everything necessary to make this work possible.
Thanks are due to my parents, brother and sister for their prayers and support throughout my academic life. I dedicate this work to them.
Appreciations are due to Mr. Abdallah Al-Gahtani for his kind support before the viva.
Title of thesis:
Thermal Stresses in Pipes
N am e of student:
Iyad Al-Zahamah
S tudent No: 9897021
ABSTRACT T his study presents results about therm al stresses in externally heated pipes th a t are subjected to d ifferen t flow types: lam inar flow , tu rb u len t flow, and pulsating flow . T he effect o f flow R eynolds nu m b er o n therm al stresses in the pipe is studied. To investigate the influence o f fluid and solid properties on the resulting therm al stresses in pipes, tw o solids nam ely; steel and cooper and three fluids nam ely; w ater, coolanol-25, and m ercury are u sed in the study. Pipes w ith d ifferen t diam eters, length to diam eter ratios, and thickness to diam eter ratios are covered in the study to exam ine th e effects on therm al stresses. D ifferen t param eters for p ressu re difference and oscillating frequency are used in the case o f pulsatin g flow to find their in flu en ce on th e resulting therm al stresses in the pipe. T he am ount o f h eat flux at th e outer w all o f the pipe is also included in the study.
In order to account for the turbulence, the k-s model is introduced in the analysis. The numerical scheme employing control volume approach is introduced to discretize the governing equations o f flow and heat transfer. The grid independent tests are carried out to ensure grid independent solutions. To validate the present predictions, data presented in the open literature are accommodated. iv
Table of Contents
Declaration
i
Dedication
ii
Acknowledgment
iii
Abstract
iv
Table o f Contents
V
List o f Tables
viii
List o f Figures
ix
Nomenclature
xiii
CHAPTER 1 Introduction and Scope of the Work 1.1
Introduction
1
1.2
Scope of the present study
5
CHAPTER 2 Literature Review
6
Laminar flow
6
Turbulent flow
13
Pulsating flow
17
Thermal stresses in pipes
25
V
CHAPTER 3 Mathematical Modeling, Numerical Solution and Results Validation 3.1
Introduction
34
3.2
Mathematical Modeling
34
3.2.1
Boundary Conditions
35
3.2.2 Governing Thermal Stress Formulae
37
3.2.3
38
Fully developed Laminar Flow
3.2.4 Turbulent Flow
39
3.2.5 P u lsatin g F lo w
42
3.3
N u m erical S olution and R esu lts v alid atio n
43
3.3.1
Fully Developed Laminar Flow
50
3.3.2 Turbulent Flow
51
3.3.3 Pulsating Flow
53
CHAPTER 4 Results and Discussion 4.1
Introduction
55
4.2
Fully Developed Laminar Flow
55
4.2.1 The Effects o f Diameter, Thickness and Length Size Effects on Thermal Stresses
56
4.2.2 The Material Properties and the Thermal Conductivity Effects on Thermal Stresses
77
4.3
Turbulent Flow
82
4.4
Pulsating Flow
95
4.4.1
The Effects o f Diameter Size and Thickness to Diameter Ratio on Thermal Stresses
95
4.4.2
The Effects o f Length Size on Thermal Stresses
104
4.4.3
The Effects o f Reynolds Number on Thermal Stresses
109
4.4.4
The Effects o f Fluid Properties (Prandtl Number) on vi
Thermal Stresses 4.4.5
114
The Effects o f pressure Difference Oscillating Frequency on Thermal Stresses
4.4.6
119
The Effect o f Heating Load Magnitude on Thermal Stresses
124
CHAPTER 5 Conclusions and Future Work 5.1
Conclusions
129
5.1.1
Laminar Flow
129
5.1.2
Turbulent Flow
131
5.1.3
Pulsating Flow
133
5.2
Future Work
135
References
136
Papers in Conference and Journals
147
vii
LIST OF TABLES
Table 3.3.1
The turbulent Prandtl numbers and the resulting Nusselt numbers for the validation and the present study results
Table 4.1.1
Properties of the pipe material and fluids used in the study
Table 4.2.1
Diameters, thicknesses, lengths and grid sizes of
the pipes used in the parametric study for
laminar flow
Table 4.4.1
The pipe diameters and thicknesses at Reynolds
number =500 Table 4.4.2
The pipe lengths at Reynolds number = 500 and
LIST OF FIGURES
Figure 3.1.1
Schematic diagram o f the pipe and coordinates
34
Figure 3.2.1
The turbulent Prandtl numbers for various Reynolds numbers at
41
Different Laminar Prandtl numbers Figure 3.3.1
A finite control volume
44
Figure 3.3.2
Meshes used in the study
49
Figure 3.3.3
Axial distribution o f the dimensionless temperature distribution
50
Figure 3.3.4
The Nusselt numbers for various Reynolds and Prandtl numbers
52
from the present and previous studies Figure 3.3.5
The oscillating pressure difference input and the resulting output
54
Axial velocity Figure 4.2.1
Dimensionless temperature contours for the conditions: D = 0.08
58
m, t = O.lxD, L = 5xD (case 1 in Table 4.2.1) Figure 4.2.2
Dimensionless temperature contours for the conditions: D = 0.08
58
m, t = O.lxD, L = 25xD (case 3 in Table 4.2.1) Figure 4.2.3
Dimensionless temperature contours for the conditions: D = 0.08
59
m, t = 0.5xD, L = 5xD (case 7 in Table 4.2.1) Figure 4.2.4
Dimensionless temperature contours for the conditions: D = 0.08
59
m, t = 0.5xD, L = 25xD (case 9 in Table 4.2.1) Figure 4.2.5
Thermal stresses for cases 1, 2 and 3 in Table 4.2.1
61
Figure 4.2.6
Thermal stresses for cases 4, 5 and 6 in Table 4.2.1
62
Figure 4.2.7
Thermal stresses for cases 7, 8 and 9 in Table 4.2.1
63
Figure 4.2.8
Thermal stresses for cases 10, 11 and 12 in Table 4.2.1
64
Figure 4.2.9
Thermal stresses for cases 13, 14 and 15 in Table 4.2.1
65
Figure 4.2.10 Thermal stresses for cases 16, 17 and 18 in Table 4.2.1
66
Figure 4.2.11
Thermal stresses for cases 19, 20 and 21 in Table 4.2.1
67
Figure 4.2.12 Thermal stresses for cases 22, 23 and 24 in Table 4.2.1
68
Figure 4.2.13 Thermal stresses for cases 25, 26 and 27 in Table 4.2.1
69
Figure 4.2.14 Dimensionless temperature (T*) contours for the cases o f
71
a) steel and mercury and b) copper and mercury
ix
Figure 4.2.15
Dimensionless temperature (T*) contours for the cases
of
73
of
74
a) steel and water and b) copper and water Figure 4.2.16 Dimensionless temperature (T*) contours for the cases a) steel and coolanol-25 and b) copper and coolanol-25 Figure 4.2.17
The dimensionless outer wall temperature vs. the
76
dimensionless Pipe length for various Prandtl numbers and thermal conductivity ratios Figure 4.2.18
The effective stress distribution vs. the dimensionless pipe
76
radius at the inlet-plane o f the pipe for various Prandtl numbers and thermal conductivity ratios Figure 4.2.19 The effective stress distribution vs. the dimensionless pipe
78
radius at the mid-plane o f the pipe for various Prandtl numbers and thermal conductivity ratios Figure 4.2.20 The effective stress distribution vs. the dimensionless pipe
78
radius at the outlet-plane o f the pipe for various Prandtl numbers and thermal conductivity ratios Figure 4.2.21
The dimensionless temperature ratio vs. the dimensionless
79
distance along the pipe for various Prandtl numbers and thermal conductivity ratios Figure 4.2.22 Location o f the minimum effective stress at the inlet, mid
81
and outlet planes o f the pie for various Prandtl numbers and thermal conductivity ratios Figure 4.3.1
Variation o f the local Nusselt number with the dimensionless
83
length o f the pipe for two fluids at different Reynolds numbers for the cases o f a) steel pipe and b) copper pipe Figure 4.3.2
Dimensionless temperature (T*) contours for the cases o f copper
85
pipe with water and coolanol-25 at Reynolds number = 10000 Figure 4.3.3
Dimensionless temperature (T*) contours for the cases o f steel
86
pipe with water and coolanol-25 at Reynolds number = 10000 Figure 4.3.4
Dimensionless temperature (T*) contours for the cases o f copper pipe with water and coolanol-25 at Reynolds number = 30000
x
88
Figure 4.3.5
Dimensionless temperature (T*) contours for the cases o f copper
89
pipe with water and coolanol-25 at Reynolds number = 50000 Figure 4.3.6
Dimensionless temperature (T*) contours for the cases o f steel
91
pipe with water and coolanol-25 at Reynolds number = 30000 Figure 4.3.7
Dimensionless temperature (T*) contours for the cases o f steel
92
pipe with water and coolanol-25 at Reynolds number = 50000 Figure 4.3.8
Mid-plane effective stresses for combinations o f two solids and
94
two fluids at three Reynolds numbers (10000, 30000 and 50000) Figure 4.4.1
Inner and outer wall temperature at the inlet and outlet planes
97
for the cases o f D = 0.04 m and D = 0.08 m and t = 0.125xD Figure 4.4.2
Thermal stresses at inlet and outlet planes for the case o f
98
D = 0.04 m and t = 0.125xD = 0.005 m Figure 4.4.3
Thermal stresses at inlet and outlet planes for the case o f
99
D = 0.08 m and t - 0.125xD = 0.01 m Figure 4.4.4
Inner and outer wall temperatures at the inlet and outlet planes
101
for the cases o f D = 0.04 m and D = 0.08 m and t = 0.5xD Figure 4.4.5
Thermal stresses at inlet and outlet planes for the case o f
102
D = 0.04 m and t = 0.5xD = 0.02 m Figure 4.4.6
Thermal stresses at inlet and outlet planes for the case o f
103
D = 0.08 m and t = 0.5xD = 0.04 m Figure 4.4.7
Inner and outer wall temperatures at the inlet and outlet planes
106
for the cases o f L =12.5xD and L =17.5xD Figure 4.4.8
Thermal stresses at inlet and outlet planes for
107
the case o f L = 12.5xD Figure 4.4.9
Thermal stresses at inlet and outlet planes for
108
the case o f L = 17.5xD Figure 4.4.10 Inner and outer wall temperatures at the inlet and outlet planes
111
for the cases o f Reynolds number = 1000 and Reynolds number = 1500
Figure 4.4.11 Thermal stresses at inlet and outlet planes for the case o f Reynolds number = 1000
xi
112
Figure 4.4.12 Thermal stresses at inlet and outlet planes for the case o f
113
Reynolds number = 1500 Figure 4.4.13
Inner and outer wall temperatures at the inlet and outlet planes
116
for the cases o f coolanol-25 and mercury Figure 4.4.14 Thermal stresses at inlet and outlet planes for the case o f
117
Coolanol-25 Figure 4.4.15 Thermal stresses at inlet and outlet planes for the case o f
118
Mercury Figure 4.4.16 Inner and outer wall temperatures at the inlet and outlet planes
121
for the cases o f 0.2 Hz and 1 Hz Figure 4.4.17 Thermal stresses at inlet and outlet planes for the case o f 0.2 Hz
122
Figure 4.4.18 Thermal stresses at inlet and outlet planes for the case o f 1.0 Hz
123
Figure 4.4.19 Inner and outer wall temperatures at the inlet and outlet planes
125
for the cases o f 2000 W /m2 and 10000 W/m2 Figure 4.4.20 Thermal stresses at inlet and outlet planes for the case o f
126
2000 W/m2 Figure 4.4.21
Thermal stresses at inlet and outlet planes for the case o f 10000 W/m2
xii
127
Nomenclature A
velocity amplitude
(m/s)
Cp
specific heat o f fluid (J/kgxk)
CpSoiid specific heat o f solid (J/kgxk) D
inside diameter o f the pipe
(m)
E
modulus o f elasticity o f the pipe material
e
constant in law o f wall
h
heat transfer coefficient
J
total flux across a face o f the finite control volume (J/m )
k
turbulent kinetic energy generation variable
(Pa)
(W/m xk) •5
(m /s }
kf
thermal conductivity o f the fluid
(W/mxk)
ks
thermal conductivity o f the solid
(W/mxk)
kfiuid
thermal conductivity o f the fluid
(W/mxk)
ksoiid
thermal conductivity o f the solid
(W/mxk)
L
length of the pipe
n
oscillating frequency o f a pulsating flow
p
pressure
Pr
laminar Prantle number
Prt
turbulent Prantl number
q
heat flux
(m) (Hz)
(Pa)
(W/m2)
Re
laminar Reynolds number
Ret
turbulent Reynolds number
r
radial coordinate
r*
dimensionless radius o f a grid point = (r-r,)/(r0-r[)
r0
pipe outer radius
(m)
ri
pipe inner radius
(m)
S,),
source or sink of variable (j)
t
thickness o f the pipe (m)
T
temperature at a grid point
(m)
(K)
xiii
Tavs
average temperature in the solid
T*
dimensionless temperature at a grid point
T inlet
pipe inlet temperature
Tmean
mean temperature of all grid points (K)
Tsolid
solid-side temperature
Tsw
temperature at the first radial grid point in solid at a certain axial plane
Tfiuid
fluid-side temperature
Tftv
temperature at the last radial grid point in fluid at a certain axial plane
Tinlet
pipe inlet temperature
(K)
ToW
outer-wall temperature
(K)
Tiw
inner-wall temperature
(K)
U
fluid axial velocity
(K)
(m/s)
fluid radial velocity
Vo
resultant radial velocity
X
axial coordinate
(m/s)
(m/s) (m/s)
(m)
Greek Symbols s
turbulent dissipation variable
£u
tangential strain
Sr
radial strain
£x
axial strain
CTV
effective stress
(Pa)
CTU
tangential stress
(Pa)
Or
radial stress
(Pa)
Ox
axial stress
(Pa)
V
gradient/divergence operator
r*
exchange coefficient for