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8/9/2019 Numerical solutions of viscous flow through a pipe orifice al low Reynolds numbers
1/8
133
NUMERICAL SOLUTIONS OF VISCOUS FLOW T H R O U G H A
PIPE ORIFICE
AT
LOW REYNOLDS NUMBERS
By R. D. Mills*
Numerical
solutions
of the Navier-Stokes equations have been obtained in the low range
of
Reynolds numbers for steady, axially symmetric, viscous, incompressible fluid flow
through
an
orifice in a circular pipe
with
a fixed orificelpipe diameter
ratio.
Streamline
patterns and vorticity contours are presented as functions of Rcynolds
number.
The
theoretically determined discharge coefficients are in good agreement with experimental
results of Johansen 2).
INTRODUCTION
THE PLATE ORIFICE
has long been used as a device for
measuring flow-rates in pipes. Various specifications of
orifice shape and positions of the pressure tappings have
been put forward as ‘standard’ (e.g. reference r)t) .
The most convenient for theoretical investigation is the
orifice with ‘corner tappings’ since this allows different
diameter orifices to be compared on the basis of Reynolds
number in any given pipe. At high Reynolds numbers with
fully developed turbulent flow the coefficient of discharge
of the pipe orifice is well-established experimentally to be
nearly constant. However, at low Reynolds numbers under
conditions of viscous flow appreciable variation in the
value of this coefficient has been observed (e.g. reference
2)). This is due to the marked dependence of the flow on
Reynolds number at low values of this parameter.
It
has therefore been the purpose of the present paper
to investigate theoretically the nature of the flow through
an orifice of simple geometrical shape at low Reynolds
numbers. Streamline patterns and contours of constant
vorticity have been obtained as functions of Reynolds
number. The calculated discharge coefficients are in good
agreement with experimental results of Johansen 2) for
an orifice having corner tappings, even with the differences
in geometry which had to be permitted to render the
problem tractable from the computational point of view.
(The orifice used by Johansen was bevelled by 45” on its
downstream face, whereas the present calculations refer
to a square-edged orifice.)
It
has thus been necessary to solve the Navier-Stokes
equations numerically in the low to intermediate range of
Reynolds numbers for axially symmetric, incompressible,
The
MS.
of this paper was received at the Institution orz 16th
October 1967undaccepted
for
publication on2 Yth hrovember
1967.
2
*
Engineering Luborutory, Cambridge University.
f
R e f m w e s are
given
in the Appendix.
J O U R N A L M E C H A N I C A L E N G I N E E R I N G
S C I E N C E
viscous flow. The foundations of this type of work were
laid nearly 40 years ago by Thom (3). Considerable
attention is currently being given to this type of problem,
including time-dependent flows. Comparatively little
work, however, has been done for axially symmetric flow
even in the time-steady case, despite the importance of
such flows in engineering applications. Th e first numerical
solution for axially symmetric flow was that for creeping
flow through a sudden expansion in a pipe, given by
Thom 4) in 1932. Later work on flow with axial sym-
metry has been reported by Jensen
( 5 )
and Lester
6).
The method of solution employed is the ‘two-field’
method of Thom: replacement of the fourth-order non-
linear partial differential equation for the stream function
by two second-order simultaneous equations for 4 and
the vorticity
7;
these equations are then replaced by their
simplest finite difference equivalents. In the case of two-
dimensional flow, this coupled pair of finite difference
equations is now well known to exhibit superior conver-
gence properties compared with finite difference forms of
the original fourth-order equation when iterative methods
are employed for their solution; moreover, the boundary
conditions are more easily treated in rhis formulation of
the problem. There is little doubt that similar conclusions
hold for flow with axial symmetry.
Notation
D
CL
curl
d
grad
H
h
Radius and diameter of pipe (Fig. l}
Coefficient of discharge
of
orifice (equa-
Vector ‘curl’.
Diameter or orifice
Fig. 1).
Vector gradient.
p+9pqz , total head.
Finite difference mesh width.
tions (19), (20)).
Vol
10No 2
I968
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134
L ,
u
P
P o
Q
q
=
u, u, w )
Re
Reo
rJ
8J
t
r =
( 8 , b 51
P
V
P
0 2
X
Superscript
k
Subscripts
i i
R. D. MILLS
Characteristic length and velocity.
Static pressure of fluid.
Upstream pressure at section AC in
Poiseuille flow (Fig. 1 and equation
(21)).
Volumetric discharge rate.
Velocity vector.
w,a/v, Reynolds number based on pipe
radius and maximum pipe speed (Fig. 1).
G0d/v, Reynolds number based on orifice
diameter and mean speed I? through
orifice (as used by Johansen 2)).
Cylindrical polar co-ordinates.
Time.
Vorticity vector.
Viscosity coefficient of fluid.
Kinematic viscosity coefficient of fluid.
Density of fluid.
Stokes stream function.
Laplacian operator.
Scalar product.
Vector product.
Number of iterations.
Refer to location of mesh points in the
usual sense of matrix notation.
N.B. Field variables, operators and the mesh width are
made dimensionless according to the scheme of
equation
3).
Primed quantities are dimensional and
unprimed quantities dimensionless.
GOVERNING
EQUATIONS
In the usual notation the equation of steady, viscous, in-
compressible fluid flow is
1)
(q’.V’)q’
=
--grad’p’+vVf2q‘
P
where
q‘
is the velocity vector,
p’
is the static pressure,
p
the density, v =
p i p
the kinematic viscosity coefficient of
the fluid, and primes signify
dimensional
quantities. If the
variables and operators are made dimensionless with
respect to a representative length
L
and velocity U , then
equation 1) becomes in
dimensionless
form
1
(q.’?)q = -ggradp+-Vq
e . .
2)
where the Reynolds number of the motion is Re =
UL/v.
Take cylindrical polar co-ordinates (r , 0,
z
with velocity
components (u, v, w ) and vorticity components t,
,
5 .
Identify L with the pipe radius a and
U
with the maximum
velocity
w ,
in Poiseuille flow (Fig.
1).
The full non-
dimensional scheme is then
] 3)
r
=
r’/a z
=
z’ia
h =
h’/a u
=
u’iw, etc.
+ = f / w , a 2 .$
=
. ’a/w, etc. p = p‘/pwm2
whereupon the Reynolds number is defined naturally as
Re
=
w,a/v;
h’ is the mesh width. Henceforth all
un-
primed quantities are dimensionless.
For motion with symmetry about the z-axis the velocity
and vorticity vectors reduce to q
=
u, 0,
w )
and
r
=
(0,
7,
0)
respectively where
au
aw
”G 5
.
.
.
’
4)
If the Stokes stream function is introduced by
Fig. 1
T O U R N A L M E C H A N I C A L E N G I N E E R I N G S C I E N C E
Vol10
No 2 1968
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NUMERICAL
SOLUTIONS OF
VISCOUS FLOW
THROUGH
A PIPE ORIFICE
AT
LOW REYNOLDS NUMBERS
135
then the equation of continuity,
L'u aw u
-+-+-=o . . . .
ar az
r
is satisfied automatically, and it can be shown (by taking
the 'curl' of both sides of equation
2)
thereby eliminating
the pressure) that the equations of motion reduce to the
pair of simultaneous equations
(7)
1 c a q la*&]
r
i.z Cr
r
8 r t k r2
Cz,
. .
(8)
Expression of equation 2) in the form
1
qxq
=
grad(p+:q2)+zcur11; . 9)
and resolution of components in the r and z directions
leads to the following two integrals relating to the total
head H = p + + q 2 :
Once the functions
I/
and
7
have been calculated equations
10) and 11) allow the pressure at any point in the flow to
be determined relative to some datum.
FINITE DIFFERENCE E QUATIONS
A
portion of the square mesh used for the finite difference
scheme is shown in Fig.
1.
Mesh points on the solid
boundaries will be referred to as boundary nodes and the
others as field nodes. By use of the simplest central-
difference formulae the stream function and vorticity
equations (7) and (8) can be written in the following
iterated forms:
*:., = ~ ~ ~ ~ ~ ~ l + ~ ~ - l * ~ + ~ ~ . ~ - l + ~ ~ ~ ~ . ,
h
2r,
:-
1 1
FF1'.J>-h t?lk
1
12)
where k is the iteration number. Apart from a difference
J O U R N A L M E C H A N I C A L E N G I N E E R I N G S C I E N C E
of notation these equations are identical with those given
by Lester
p. 5,
reference
(6) ) .
BOUNDARY CONDITIONS
To
satisfy the condition of no slip at solid walls the
normal and tangential gradients of must vanish at these
boundaries. The tangential conditions are satisfied by
setting + = constant along these boundaries. Special
boundary formulae have to be developed, however, for
the normal conditions. In view of the axi-symmetric
nature of the flow it is no longer possible to use the same
boundary formulae for both vertical and horizontal walls
as can be done for two-dimensional flow referred to a
rectangular co-ordinate system. Each direction must be
treated separately, or more generally, as Thom and Lester
have done, by considering a boundary wall at inclination.
Essentially, they expand both + and
7
in Taylor series
about their boundary values at the wall and utilize the
governing equations to provide expressions for the higher
order derivatives. I t will suffice here to quote the results;
for a full derivation the reader
is
referred to Lester's
paper ( 6 ) .
6
2
* ~ ~ I , ~ - ~ ~ , J ) - ~ 2 * l ~ ] ~ ~ l , ~
r . 1 horizontal wall 15)
1171 3
h
hZ
2F---
r, 43
(upper sign
=
outer' wall, lower sign = inner' wall)
3
r,h
72.1 = *~,~~1-***,)-~17~.~*1 vertical walls
* 14)
Equations
15)
and
(16)
are accurate to order
h3;
equation
15)
is in fact exact for Poiseuille flow, as can easily be
checked. These boundary values are determined by
iteration as the solution proceeds.
The boundary conditions are such that a parabolic
velocity distribution is prescribed at
a
section A C a short
distance upstream of the orifice and also again 'far down-
stream' a t section
BE
(Fig.
1).
In reality the downstream
reversion to Poiseuille flow at low Reynolds numbers is
achieved in an asymptotic manner (as also is the change
upstream). For these numerical computations, however,
the author adopted the following approach: take the sec-
tion at a position which seems sufficiently far downstream
physically (actually, some guide in this matter can be
obtained from a study of the photographs in reference
2));
then repeat the calculations at a section farther downstream;
if
no change in the eddy structure at the orifice is observed
then the first position is regarded as 'sufficiently far down-
stream'. This sort of downstream boundary condition of
course becomes invalidated at high Reynolds numbers
when ultimately turbulence sets in.
The sharp intruding corners at F,
G
(Fig.
1)
were
treated in the manner suggested by Thom. There are
assumed to be two values of the vorticity at the boundary
nodes F, G. These are calculated from equations 15),
16)
utilizing the values of the vorticity at
K, N
and at
V d 10
NO
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136 R. D. MILLS
My S respectively. When the 'diamond' in the iteration
process is centred on
K,
M then the first pair of values of
the vorticity is used and when centred on N,
S
the second
pair of values is used. I n this way the effects of the corners
are forced to spread into the fluid
in
both the Y and
z
directions-as must occur physically when the fluid
'passes round the corners'.
ITERATION TECHNIQUE
The iterative routine used to solve the system
of
equations
(12)
and
13)
and boundary conditions (15) and (16) was in
the main the basic technique used by Thom (p. 115, ref-
erence
7)).
Many variants are possible but the present
author has found that a single iteration of the +field, setting
the boundary valuesby equations(15)and (16), followed by
asingleiterationof the 7-field was the most satisfactory 8).
Generally, the boundary values of vorticity were given one
half their 'theoretical' movements in each iteration. To
start the solution it is necessary to have a guessed or trial
solution at each node.
This
author started simply with
all field nodal values zero and the boundary nodes given
their Poiseuille flow values. Once the solution was ob-
tained for a given Reynolds number, then this was used
as the starting solution for the next higher value of Re.
This seems a satisfactory enough procedure, though other
workers in this field have found that greater stability
(leading to a higher attainable Reynolds number) can be
obtained by taking into account the aji't terms in the equa-
tions, and stepping on from a solution at time
t
to one at
time t+ by one of the standard procedures for diffusion
problems (e.g. references
( 9 )
and
10)).
Stability and convergence
Thom and Apelt
Ir)
have studied the effect of introduc-
ing a small disturbance into a two-dimensional vorticity
field. They have shown for a square cell that the distur-
bance will not grow in magnitude provided
where
L
is the characteristic length of the problem.
Lester
12)
nd Mills 8) have generalized this work to
include a rectangular cell, Lester considering also the
effect
of
introducing a disturbance into the -field. Lester
concludes that a stability criterion based on the latter field
is less stringent than on the vorticity field. Lester also gives
procedures for obtaining 'optimum' convergence. It has
not yet proved possible to derive a similar simple criterion
for axi-symmetric flow, but it has been found that condi-
tion (17) does in practice give some indication as to when
divergence is likely to occur. It may be worth observing
here that Fromm 13) has given a stability analysis of the
full time-dependent equations, showing that simultaneous
with a condition like (17) St'lh'2
Q
1 4 v must hold.
The following two empirical criteria were utilized for
terminating the iteration process
h'/L
<
%@]Re . . . (17)
where and irirnl are the largest values of
4
and 71
occurring in the undisturbed Poiseuille flow. The fields
were given
20
iterations and then tested every subsequent
10 iterations.
VERIFICATION O F
THE
METHOD
As a check of the above methods tests were made on
Poiseuille flow in a circular pipe. Mathematically this flow
represents an exact solution of the Navier-Stokes equations
for arbitrary Reynolds number, though physically the
transition to turbulence begins at a Reynolds number
based on mean speed and pipe diameter of about 2300.
Two different starting solutions were used: in the first the
field values were set equal to zero, and in the second
starting values appropriate to a linear velocity profile were
used. A 'square' section was used for each test, that is,
equal numbers of
i
and j-steps were taken. The results
quoted refer
to
the mid-plane.
A study of Table
1
will show that there is some advantage
to be gained by starting with a closer approximation to the
ultimate solution when using the smaller mesh. As a
further investigation, it might be worth while applying the
extrapolation and empirical error tests utilized by the
author in reference 14)n connection with the boundary
layer equations.
VI SCOUS FLOW THROUGH
A
The computational method outlined above was used to
determine solutions of steady, incompressible, viscous,
axi-symmetric flow through a square-edged orifice in a
circular pipe.
A
mesh
of
width
h'
=
a116 was used, this
being sufficiently small for resolving the details of the flow
in the corners, while the orifice wall was made one mesh
width in thickness (Fig. 1). The resulting flow patterns
are depicted in
Figs
2-6 for Reynolds numbers Re,
=
0-50
and fixed diameter ratio d / D = 0.5. Also presented in these
figures are the contours of constant vorticity. (For com-
parison purposes, the Reynolds number used by Johansen,
Reo,
is
occasionally used instead of the present Reynolds
number Re. For d / D= 0.5, Re, = 2Re.)
Fig. 2 shows that even for the 'creeping' (Re
= 0)
motion two corner eddies exist upstream and downstream
of the orifice. As the equations of motion for Re = 0 are
symmetrical in
z
(equations 7),
(8))
the solution should
show symmetry about the mid-plane of the orifice. This is
confirmed in the computational solution, with its near-
perfect symmetry (Fig.
2).
It is thus immaterial whether
the flow is from left to right or vice versa
at Re
=
0.
This
condition will never actually be realized in practice though
creeping motion is possible with Re arbitrarily near to zero.
As the Reynolds number is increased (Figs 3-6) the
downstream eddy lengthens and increases in size. Simul-
taneously with this process the upstream eddy shrinks in
size and at Re, = 50
it
is very small indeed. Note also the
characteristic stretching of the vorticity contours in the
direction of motion
as
the Reynolds number increases.
SQUARE- EDGED ORI FI CE
J O U R N A L M E C H A X I C A L E K G I N E E R I N G S C I E N CE Vo110 No 2
I968
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NUMEKICAI, SOLUTIONS O F
VISCOUS
FLOW THROUGH A PIPE ORIFICE AT LOW REYNOLDS
NUMBERS
137
Table 1.
Numerical solution of Poiseuille f l o w in a circular p e
(I) Zero
field
values as
starting
solution.
11)
Field values correspondingto
a linear velocity
profile
as starting
solution.
7 . . o 0.25 050 0-75 1 oo
1 h Re
k
-values
8 10
20 0
-0.030790
-0.110 492
-0.202 992 -0.250 000
8
10 100
0 -0.030528
-0.109 747 -0.202
381
-0.250
000
16 10
50
0
-0.029560 -0.108 316
-0.202 482 -0.250 000
16 10
100 0 -0-030441
-0.109 739
-0.202 388 -0.250 000
8
20
20 0
-0'030400 -0-109 448
-0.202 254 -0.250
000
8 20
100
0
-0.030540
-0.109 776 -0.202 402
-0.250 000
16 20
50 0
-0.028097 -0.104 324
-0.199 431 -0.250 000
-0.202 141 -0.250 000
6 20 100
0
-0.030277 -0.109 342
8
8
16
16
8
8
16
16
R
8
16
16
8
8
16
16
8
8
16
16
8
8
16
16
10 20
10
50
10 50
10 100
20 20
20
50
20 50
20 100
0
-0.030 606
0
-0.030528
0 -0'031 226
0
-0.030 342
0 -0.030616
0
-0.030540
0 -0.031 036
0
-0.030 359
-0.109 935
-0.109 747
-0.1 11 609
-0.109 477
-0.109 967
-0.109 776
-0.111 160
-0.109 524
-0.202 469 -0.250 000
-0.250 000
0.202 381
.203 520 -0.250 000
-0.202 197 -0.250 000
-0.202 512 -0.250 000
-0.202 403 -0.250
000
-0'203 236 -0.250
000
-0.202 235 -0.250 000
Exact 0
-0.030273 -0.109 375 -0.202 148 -0.250 000
?-values
I0
20
0
0506 089 1.007 39 1
1.487 303 1.939 197
10 100
0
0.499 344
0.997 059
1.492 019 1.984
150
10 50
0
0,576 993 1.157 902
1.643015 1.894 199
I0 100
0
0.501 253 0.999 953 1-493330 1.985 105
20 20
0
0.501 131 1.003 136 1,503 257 1.982 480
1.982 723
0 100
0
0.500 547 0.998 756
2.084 726
0
50
0
20 100
0
0.500 113 1 000 845 1.501 477 1.997 151
1.492 660
0.499 132 1.042 35 1 1.635 715
10 20
0
10
50
0
10 50 0
10
100 0
20 20 0
20 50
0
20 50
0
20 100 0
0-496 611
0.499 345
0-499 841
0.498 926
0.500
467
0500 547
0502 419
0.500 154
0.990 094 1.482 477 1.984
138
1.492 021 1.984
148
.997 062
0.983 419 1.446 749 1.936 452
0.997 291 1.496 033 1.996 959
0.997 152 1.487 464 1.979 045
1.982 723
.998 755 1.492 660
1.950
342
,992 121 1.460 389
1.994 365
.999 246 1.496 630
Exact 0 0-500000 1 ooo 000 1
500
000 2.000 000
0
q=
1 6
0
Fig. 2.
Streamlines and vorticity contours: Re, = 0
Fig.
3.
Streamlines and vorticity contours: Re,, = 5
V d 10 h o 2 1968
O U R N A L M E C H A N I C A L E N G I N E E R I N G S C I E N C E
4
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138
R
D.
MILLS
Fig.
4.
Streamlines and vorticity contours: Re, = 10
Fig.
5. Streanzlines and vo rti city contours:
Re,
=
20
c
Fig.
6. Streamlines and vorticity comours: Re,
= 50
l O U R N A L M E C H A N I C A L E N G I N E E R I N G S C I E N C E
Vol n No 2
1968
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NUMERICAL SOLUTIONS OF
VISCOUS
FLOW THROUGH A PIPE
ORIFICE A T
LOW REYNOLDS NUMBERS
139
Pressure calculations
The usual relationship for the discharge of an incompres-
sible fluid through a pipe orifice is
where
Q’ is
the volumetric rate of flow,
C
the coefficient
of discharge and
p‘ , -p ‘ ,
is the pressure drop across the
orifice. In general the coefficient of discharge is a function
of Reynolds number, diameter ratio d / D , and orifice
geometry. The pressure drop p , -p , was calculated from
equations (10) and (11) for each Reynolds number and the
coefficient of discharge determined from
since
r =
~Ll*z 3nd p’,-p’,
=
(p1-p,)pwrn2, The
positions of the pressure points used for this calculation
and the path of integration (broken line) are shown in
Fig. 1. Integration along lines containing an even number
of mesh widths was performed with Simpson’s rule while
Gregory’s formula was used for the other lines. The pres-
sure drop was recalculated in each case using a neigh-
bouring path; this not only provided an immediate check
but also a more general one on the results as
a
whole for
the pressure changes between any
two
points
in
the field
are
independent of the path linking them. The results of
these calculations are shown quantitatively in Table
2,
and
graphically in Fig. 7 alongside the experimental results
of
Johansen 2).
So
that the creeping flow results obtain in the limit
Table
2
0 0-220
2.5
0.216
0.207
0.184
0.138
I
5.0
heory
0.5
Exper imenta l
resu l ts
f r o m reference ;2)
L
0
4 6
dRec
Fig. 7 . CoefJicient of discharge as a function of Reynolds
number
Re
0,
Re(p,
-p2)
was evaluated rather than ( p ,
p2)
in
equations (10) and (11). This means Cd12/Re is logically
evaluated in equation (20).
(For
the justification of this in
exlensu see reference IS), p. 168.) The first item in Table 2
can be expected to hold in a small neighbourhood
of
Re
=
0 . It
is seen that at low Reynolds numbers the
coefficient
of
discharge is very nearly proportional t o the
square root of the Reynolds number, a result confirmed
by Johansen’s experiments for a wide range of d / D ratios.
In Fig. 8 are shown the axial pressure distributions as
functions of Reynolds number, calculated from equation
(11). Some care is needed in evaluating 87jar and
numerically on the axis, for
7
+ 0
as r
(see reference
6) for details). Also shown
for
comparison is the linear
pressure drop
of
Poiseuille flow
Note that the pressure distribution correctly becomes
parallel to this line downstream of the orifice. Once again,
Re(p-p , ) has been evaluated rather than ( p - p , ) so that
the Stokes creeping flow results are obtained as Re
.
Fig. 8 . Axial pressure distributions as functions
of
Reynolds number
JOURNAL M E C H A N I C A L E N G I N E E R I N G S C I E N C E
Vol
I0 No 2 191
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8/9/2019 Numerical solutions of viscous flow through a pipe orifice al low Reynolds numbers
8/8
140
R. D. MILLS
The pressure minima which begin to appear just down-
stream of the orifice at about
Re
=
5
are evidently asso-
ciated with the gradual appearance, as
Re
increases, of
significant kinetic energy in the flow along the axis. The
pressure drop across the orifice, viewed as a device
incurring a ‘loss of head’, can be determined from Fig.
8.
CONCLUSIONS
Numerical solutions
of
the Navier-Stokes equations have
been obtained for axi-symmetric, viscous, incompressible
flow through a square-edged orifice in a circular pipe for
Reynolds numbers
Re
= 0-50 and fixed diameter ratio
d / D
=
0.5. It has been found that there are two eddies
symmetrically located upstream and downstream of the
orifice for Re
=
0 (creeping flow). As the Reynolds
number increases the downstream eddy lengthens while
the upstream eddy shrinks in size and become almost
imperceptible at Re
=
50.
The phenomenon of eddy-lengthening with increase
of
Reynolds number is well known for other physical situa-
tions, e.g. the flow behind spheres
( 5 )
or backward-facing
steps. It is difficult to give a simple physical explanation of
this phenomenon. However, in the present case it must
originally be connected with the shedding of vorticity
from the sharp corners of the orifice. Ultimately, a vortex
‘sheet’ arrives at the pipe wall which has insufficient con-
vective speed to enable
it
to proceed downstream against
the counterflow effect of the vorticity itself at the wall.
A
backward flow is induced at the walls and this leads in turn
to a closed recirculating region in which both diffusion and
convection of vorticity occur. As the Reynolds number
increases and convection of vorticity becomes more
important than diffusion this limiting vortex sheet is
carried farther and farther downstream and
so
the eddy
lengthens.
In all these cases, at a certain critical Reynolds number,
laminar flow breaks down into periodic eddy shedding
( K i r m h vortex street, in two dimensions) and ultimately
turbulence sets in. The critical Reynolds number in the
present case must depend on the diameter ratio d / D and
also on the detailed geometry of the orifice. Johansen’s
experimental results indicate that periodic flow does not
occur below the value
Re
= 150.
No solutions were attempted by the present methods
for Reynolds numbers
Re
in excess of
50
for the following
reasons. It is extremely difficult to disentangle the effects
of instability in the numerical procedure used to solve the
finite difference forms of the equations of motion and
boundary conditions and the hydrodynamic instability to
small disturbances of the equations of motion themselves;
and
to
ascertain to what extent these are associated with
the actual physical instability. Furthermore, it is now known
that ‘stable’ solutions obtained at high Reynolds numbers
by finite difference methods can stem from truncation
error in the finite difference representations of the con-
vective terms. The truncation error, which increases with
the mesh width, gives rise to an enhanced viscosity, i.e.
stabilizing, term. These high Reynolds number ‘solutions’
J O U R N A L M E C H A N I C A L E N G I N E E R I N G S C I E N C E
are thus open
to
question as strict solutions of the viscous
flow equations.
The discharge coefficients calculated by the present
methods show good agreement with the values obtained
experimentally by Johansen even though there was not a
complete similarity
in
regard to orifice geometry and
location of pressure tappings. Thus it seems that at low
Reynolds number these considerations are not soimportant
as the Reynolds number itself in determining the flow
characteristics.
It
might be worth while doing some further
theoretical work on different orifice geometries to confirm
this (including different
d / D
ratios), though the handling
of the boundary conditions would then present rather
greater difficulties.
ACKNOWLEDGEMENTS
The author gratefully acknowledges the receipt of the
necessary computer time for this investigation on the
Science Research Council Atlas computer, Harwell, and
on the Cambridge University Ti tan computer. H e would
like also to thank Dr L.
C.
Squire for reading the
manuscript critically. This work was made possible by the
award of
an
I.C.I. Fellowship.
APPENDIX
RE FE RE NCE S
I)B.S. 1042:
Part
1: 1964. Methods fo r the measurement of
fluid f l ow in pipes.
Part 1:
Orifice plates nozzles and
venturi tubes
1964
(British Standards Institution, London).
‘Flow through pipe orifices at low Reynolds
numbers’, Proc.
R.
SOC. 930
126
(Series A), 231.
‘The flow past circular cylinders at low speeds’,
I’roc. R. SOC. 933 141
(Series A),
651.
‘An
arithmetical solution of certain problems in
steady viscous flow’, Rep. Memo. aeronaut. Res. Comm.
1475, 1932.
‘Viscous flow round a sphere at
low
Reynolds
numbers’, Proc. R . SOC. 959 249 (Series A), 346.
‘The flow past a pitot tube a t low Reynolds
numbers’, Rep. Memo. aeronaut. Res. Comm.
3240, 1961.
Field computations n engineering
and physics 1961
(Van Nostrand).
‘Numerical solutions of the viscous
flow
equa-
tions for a class of closed flows’,J. R. aeronaut. SOC.
965
69,
714
(erratum
880).
‘Dynamics and heat
transfer in the von Kirman wake of a rectangular cylin-
der’, Phys. Fluids 1964 7, 1147.
‘A computational method for viscous flow
problems’,J.
Fluid Mech.
1965
21,
611.
‘Note on the convergence of
numerical solutions of the Navier-Stokes equations’,
Rep. Memo. aeronaut. Res. Coun. 3061, 1956.
‘Some convergence problems in numerical
solution of the Navier-Stokes equations’, Rep. Memo.
aeronaut. Res. Coun. 3239, 1961.
13) FROMM,.
E.
Article in
Methods of computational physics
1965 Vol. 3 (Academic Press).
14)
MILLS,
.D.
‘The steady laminar incompressible boundary
layer problem as an integral equation in Crocco variables:
investigations
of
the similarity flows’,
Aeronaut. Res.
Coun. 28116, 1966
(to be published in
the Rep. Memo.
series).
IS) ROSENHEAD,. Ed.) Laminar boundary layers 1963 (Oxford
University Press).
Vol I0
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JOHANSEN,
. C .
3) THOM,.
4)
THOM,
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(5) JENSEN,
.
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(6)
LESTER,
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7) THOM,. and APELT,C. J.
(8 )
MILLS,
R. D.
(9)
HARLOW,. H. and FROMM,
.
E.
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PEARSON,
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E.
11) THOM,
.
and APELT,C. J.
12)
LESTER,. . .
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