IIII.J. Heat Maw RintedinGmt
Transfer. Vol.29,No.2.99. 169482. 1986
00179310/86$3.00+0.00
Britain
PergamonPrW Ltd.
The prediction
of turbulent
swirling jet flow
H. NAJI Laboratoire de Mbaniquede
Lille, U.E.R. de Math6matiques Pureset Appliquees, Universitede Lille I 59655 Villeneuve D’Asq Cedex, France (Received 11 February and infinalform 8 My
1985)
AhatractA space marching integration procedure is used to solve the Reynolds equations governing the axisymmetric incompressible turbulent swirling jet flow. Turbulence is modelled by the kt model with an isotropic turbulent viscosity. Resides mean velocity field, turbulent propertiessuch as Reynolds stresses, turbulent kinetic energy and dissipation rateare obtained and the results are compared with experimental data. Agreement is quite encouraging and shows that the assumption of isotropic turbulent viscosity seems plausible.
1. INTRODUCTION FREE AND swirling jets are of practical
importance
in
connection with verticaltakeoff aircraft and are also used in many industrial applications to effect spraying, drying, heating, coaling and leaching of liquids and solid particles. These practical cases could be managed more efficiently with the aid of swirl. Much work has been done to predict turbulent flows numerically. Various turbulence models have been proposed to close the timeaveraged governing equation system. Unlike wall boundary layers and free shear flows such as jets and wakes, only few studies have been devoted to rotating turbulent flows [l, 21. Ifthere is no reverse flow present, the boundarylayer approximation is valid and the radial axis is taken as the marching direction. The governing equations are parabolic, i.e. convection phenomena are important
along this direction and diffusion is effective normal to it. This leads to a particular numerical technique [36] which enables the socalled parabolic form of the NavierStokes equations to be solved. The calculation always proceeds in the downstream direction. Thus the whole flow field can be rapidly covered.
2. DEFINING THE PROBLEM This paper is devoted to the prediction of the swirling radial free jet issuing from the gap between two parallel discs, one of them rotating at a constant rate and the other one being at rest (Fig. 1). This problem has been studied experimentally by Muhe [7,8]. 2.1. The governing equations The flow is axisymmetric, so the cylindricalpolar
coordinates are used.
I
I
FIG. 1. Flow geometry. 169
170
H. NAJI
NOMENCLATURE
total diffusion coefficient 4 defined in equation (11) cm2 s ‘1 D mean rate of strain tensor F function defined by F = Wq  L. U h gap width [m] k turbulent kinetic energy (17+7+~7)/2 [mm2 s~] L(r) length scale used in the numerical procedure [m] P mean pressure m m  2] PS rate of shear production of k, gr?id U @ 2D Pe P&let number, W  L *Aq/C, r, 0, z radial, angular and axial coordinates Cm, rad, ml R disc radius [m] Re rotating Reynolds number, Q  R2/v turbulent Reynolds number, k2/v  E Re, S swirl parameter, Q  R/o source term of variable 4 S, S;, S$ linearized source terms defined in Table 1 u, u, w radial, tangential and axial fluctuating velocities [m s  ‘1 U, K W radial, tangential and axial mean velocity components [m sl] if discharge exit velocity (volume flow rate/2nRh) [m s ‘1 tensorial product. @
Greek symbols 6 half width of swirling jet defined from U = iJJ2 location [m] Ar size of the forward step, rd  r” [m] & turbulence energy dissipation rate [m2 sA3] &* dimensionless ration, h/R dimensionless coordinate, z/L(r) crossstream size dimension of the :, control volume, q,+ 1vi_ 1 dimensionless coordinate, z/6 ‘1* kinematic viscosity and density of the v, P fluid (air) [m2 s‘, kg m7 kinematic turbulent viscosity defined in VI equation (6) Cm2 s ‘1 a general dependent variable 4 turbulent Prandtl number for 4 %0 angular velocity of the rotating disc [s ‘1. n
c,
Superscripts d downstream station U upstream station mean quantities. Subscripts corresponding to the quantity 4 4 point at r~+ + point at q0 point at free stream m maximum.
The parabolic equations governing a steady (a/at = 0), axisymmetric (a/a0 = 0), isothermal (T = cte) turbulent flow, without body forces are [9] : u~+w?.p&$*f
+d
(,au>_!!E
aZ
u;
[email protected]$~ a(rU)+a(rW)=O. Br aZ
aZ
aZ
(1)
(2)
(3)
In the simplified form (I), (2) of the NavierStokes equations, only the rdiffusion terms are neglected. 2.2. The twoequation turbulence model As (l)(3) do not constitute a closed set of equations, it is therefore necessary to specify the quantities produced by timeaveraging the nonlinear convection terms: ui, UT. These terms are the Reynolds shear stresses.
However, the derivation ofexact transport equations for these stresses leads to new partial differential equations containing higherorder turbulence unknown correlations, such as utlw, etc. [lo, 111. This difficulty is generally avoided by expressing the turbulent stresses in terms of known quantities in order to obtain a closed set of equations. Turbulence models of this kind have been introduced by many authors for application to turbulent boundarylayer flows [12,13]. Most of these models are based on the concept of turbulent or eddy viscosity v,. For the radial swirling jet, the only significant Reynolds stresses are ui and 177 connected to the turbulent viscosity by :
m
=v,.(!.E+?.K) umJ=v,~
av aZ
(> 
.
The turbulent viscosity is defined by : v, = C,  k’/&.
(6)
171
The prediction of turbulent swirling jet flow
uak
For thejet flow, the quantity C, is constant due to the absence of a solid wall proximity. k and E are obtained from the following transport equations [9, 14, 18, 193 :
According to Oliver [14] the expression of E in cylindrical coordinates for an axisymmetric flow is :
ar
=
V,‘PS,&,
o
The subscript o specifies outer conditions. The first condition (9a) implies that U at z = z,, can be different to zero even though this is not reported in Fig. 5. Moreover, Ud = r”* U”/rd with the outer velocity at r” = R is one hundredth of the core flow velocity 0. Equations (SC) and (9d) are the reduced forms of equations (7) and (8) by setting the transverse gradients to be zero [3,6]. 3. NUMERICAL
E=Y
au,% a+x, 1
g+u + r2 3
where repeated indices hold for summation over 1 < i, j < 3, and ui is the velocity fluctuation in the direction i. In equation (8) fi is a function which takes into account the low turbulent Reynolds number effects at the vicinity of the jet exit : fi = l.O0.3exp(_ef). The different equations used here contain the quantities C,, C,r and C,, which in the absence of definite information, have been assumed constant for high Reynolds numbers. Their values have been taken from literature [16, 173 : C, = 0.09, C,i = 1.45, CE2= 1.95. 2.3. Boundary conditions At the freestream edge of the jet, the following conditions are employed : p WI,
= 0
VI,= 0
(W
PROCEDURE
Equations (l)(3), (7) and (8) together with the boundary conditions (9) form a closed set of equations. These equations may be written in a unified form :
where 4 = (U, V,k, E). S, is the source rate of the averaged quantity 4 and C, stands for the diffusion coefficient which can be expressed by : c,=v+$.
(11)
The values assigned to c,,+ are [ 151: u,,+ = 1 for I$ = U, K k and cl.4 = 1.3 for 4 = 8. 3.1. Transformed coordinate system Since the domain of the jet flow grows with the radial distance and since the transverse flow velocity is generally very small, it is inconvenient to discretize the original differential equation (10). As a consequence, we introduce a length scale L(r) and we transform the physical plane r, z (Fig. 2a) into the r, q plane, where
,Ar
I
(4
04 FIG.2. Physical and calculation domain.
I
‘u
I ‘cl
H. NAJI
172
?Jis the dimensionless coordinate defined by : 9 = z/L(r).
(12)
A linear variation has been prescribed for
[email protected] according to experimental data. The transformed domain is of rectangular geometry (Fig. 2b).
those formulated by Patankar and Spalding [3]. Figure 3 shows part of a finitedifference grid where the values of Q are assumed known. So we get : (
[email protected]  r” Vy&‘)Au
3.2. Transformed diflerential equations Using the variables r, t], equations (3) and (10) are now formulated as :
au
i
W) r__?+_‘_=O ar L atl 1 a(rWfj)
a(rLJ4)
L ‘all+
x1ar
t
r
aw
L
atl
a(rUcj) aq
=j$*t
+rS,
C+$ (
(14)
1
where J!. = dL,ldr. In order to overcome the nonlinearity express it as [4] :
of S,, we
s, = s;+s;4.
(15)
The definition of q and S!$are given in Table 1. By an orderofmagnitude analysis we can show that the quantity C,, v,  Ps  C,,  f2  Eis less than or equal to zero except possibly in the neighbourhood of S. Therefore, the source term Ss is not positive. The details of procedure for linearizing the source terms can be found in ref. [43. Before starting discretization of the above equations, they can recast in a different form by introducing the function F = Wq*L* V:
(16)
whereAq+ = ~j+l~,andA~= qjqj_l. The details of the discretization are given in ref. [9]. In the first term of equation (18) U* is unknown and must be estimated from the continuity equation in order to linearize the convection terms [S]. When using the hybrid scheme [4], the terms of diffusion in equation (18) are multiplied by a function G of the P&let number Pe which is defined by : G(Pe) = max (0.0, 1  0.5 IPet).
The P&let number accounts for the convection and diffusion fluxes through the boundaries of the control volume. 3.4. The continuity equation The continuity equation (16) is discretized at node q, in order to compute W at the downstream location. The result is : W+ = W_  &*Aq(rdU,dr”Uj) + tdtl,(v;+ I u; d/2.
(17) 3.3. Discretization The basic assumptions which are required for integration over the control volume are identical to
Table 1. Linearized source terms
+
q
u
V2 i ap ___.P
T
ar
UV
V

k
[email protected] 0
E
t
sp *
4
0
i
0
r
0
l/k(C,,v, *Ps  fi*C,, *8)
(19)
rd FIG.3. Control volume.
(20)
The prediction of turbulent swirling jet
3.5. Solution procedure The resulting discretized equations (18) are solved by using a classical substitution technique of Thomas for inversion of tridiagonal matrices [20221. The calculation domain is covered by a rectangular mesh with a nonuniform cell size such that the grid is very fine near the discs in the z and F directions. Figure 4 shows the grid which has been used to perform the calculations. 3.6. Conditions at the exit Starting profiles for velocity and turbulent quantities are taken from results due to a computation of the flow field between the discs [9]. These profiles are plotted on Fig. 5 vs the axial dimensionless variable I* for different values of S and for r/h = 60.
4. PREDICTION
AND DISCUSSION
The calculated values of the various dependent variables are presented together with experimental data coming from refs. [7] and [8]. In order to make a comparison with the experimental data, the obtained predictions have been reduced to represent the following characteristics : dimensionless velocity profiles U/V, and V/V,, radial and tangential
flow
173
decay of maximum velocity, dimensionless shear stresses ui#, and viG/Vf.
turbulent
4.1. Dimensionless velocity profiles
The dimensionless velocity profiles V/V, are compared for different values of S, and for two radial positions r/h = 80 and r/h = 104 (Figs. 6a and b). It can be seen that the calculation is in good agreement with the experimental data except for Jq*l > 1.6 because in this zone, the measurement by hotwire anemometers are so difficult and this explains the absence of the experimental results for Iv*1> 1.6. The tangential mean velocity is plotted in Figs. 7a and b. The agreement with experimental results is quite good for Iv*16 0.4, while for lq*l > 0.4 the standard ke model overestimates the calculated profiles with respect to the experimental ones. The discrepancy could stem from either the measured values of V by hotwire anemometers at low velocities [23] or from the eequation [24,25]. 4.2. Characteristic scales In Figs. 8 and 9 the variation of the predicted and measured radial and tangential maximum mean velocity are compared. The agreement is very satisfactory. The comparison between the measured and
~iiiiii
ii i
FIG. 4. Calculation grid.
I

174
H.
NAJI
l 0.4 A l 0.2 l
(4
I
.I%_“”
1.6
rlt1.67
.
2.90
A
54.94
3.33
0
76.50
4.16
X
1.2
0.6
0.4
0.0
. 0.4
0.6
1.2
1.6
0.6
1.2
1.6
‘I*
39.27
76.50
PX
0.6
a
0.6
(b) 2.0
1.6
1.2
0.6
0.4
0.0
0.4
2.0
‘I
175
The prediction of turbulent swirling jet flow
(1u”m)
.lO'
k
18
X
16
X 14 X 12
0
X
0
10
A
X
0
A 8
A0
X
0
A
8
A A0
. .
A 4. . . .
2.
. b
.
a
(cl 2.0
8
1.2
1.8
1 kE 1 “m 1
0.4
0.8
27.76
2.08
v
22.06
2.90
A
21.60
0.8
rfu
1.2
( )
6.8/U:, .lO’
30
A
tIll .
1.67
0.4
0.0
25
V
A
.
2c
A V IE
A .
1c
v A
(4 Rc. 5. Initial profiles of (a) U, (b) V,(c) k and (d) Eat r/h = 60.
8 1.6
1
2.0
q*
H. Nlut
176
, 0.0
0
*
1.67
.
.
2.06
*
I
2.33
+
v
2.78
x
2.09
*
+ 8
3.33
D
.
r/h=80. .0167
(4 2.0
1.6 1.2 08
0.L
0.0
0.L
0.8
1.2
1.6
2.09*
(b) FIG. 6. Axial distribution of radial mean velocity U.
calculated value of the local degree of swirl, i.e. the ratio V,,/U,,plottedinFig. 10,showsalso that theagreement is quite good except for the lowest values of S and r/h. Figure 11 compares the calculated and measured jet spreading rates. The agreement is not very good. Indeed, experiments show that the jet spreads linearly with r, whereas the calculations predict effectively the linearity of the growth but with slightly different slopes. A survey of this figure shows that the numerical prediction enables us to obtain a virtual origin of the jet independent on S and located between r/h = 50 and r/h = 60, while experiments show that for high values of S the virtual origins is located between r/h = 20 and rJh = 40. 4.3. Turbulence characteristics The curves plotted in Fig. 12a, b and c give the turbulent shear stress iiZGscaled by Vi. Results are
presented for three values of r/h and different values of S. Continuous and broken lines are present predictions and symbols measurements [S]. The prediction is correct, except in theintermittent region ofthejet where the kE model leads to an overestimation of the Reynolds shear stress iii. The turbulent shear stress 177is presented in the same manner in Figs. 13a, b and c. The ke model provides similar profiles for all values of S, while experiments obtain this result only for high values of S. We will notice that for high values of S the prediction is correct and that for q* > 0 (respectively t)* < 0) 17% is overestimated (respectively underestimated) by the model. The discrepancy between the numerical and experimental results may be due to the model which connects the shear stress to the mean velocity gradient via the eddy viscosity concept. Profiles of k and E are not included for discussion
The prediction of turbulent swirling jet flow
(4
2.0
1.6
1.2 0.8
0.4
0.0
0.L
0.8
1.2
1.6
2.Oq
2.0
1.6
1.2 0.8
0.~
0.0
0.~
0.8
1.2
1.6
2:O q*
(b) FIG.7.Axial distribution of tangential mean velocity K
I 50.
60.
70
80.
90.
100. 110. 120. r/h
FIG.8.Radial decay of the radial maximum mean velocity U,.
178
H. NAJI
;
/
e
50
60.
70.
80.
90.
100. HO.
120.
r/h
FIG. 9. Radial decay of the tangential maximum mean velocity V,.
vm/um .6
0.5
0.4
0.3
0.2
0.1
1.0
1.5
2.0
2.5
3.5
3.0
L.0
L.5”
FIG. 10. Variation of the local degree of swirl with swirl parameters S.
a.
6.
2.
50.
60.
70.
80.
90.
100.
110.
120. r/h
FIG. 11. Jet spreading with r/h.
The prediction of turbulent swirling jet flow
2.0
1.6
1.2
0.8
179
0.4
FIG. 12. Axial distribution of iii profiles. (a) r/h = 80, (b) r/h = 92, (c) r/h
=
104.
180
H. NAJI
3.0 I
(a)
.
A I
(b)
30
Re
=7.80.10'
r/h
= 92.
E’”
= 0.0167
3s
= c_) .lO’
“m
S 2s 3.33
i4.16
l.C 2.0
1.6 1.2 0.8 0.~ 0.4
1.2
1.6
2.0
3.0
Cc) FIG. 13.Evolution
0.8
axial distribution
of 07 profiles. (a) r/h = 80, (b) r/h = 80, (c) r/h = 92.
9'
The prediction of turboulent swirling jet flow since, in the absence of relevant experimental data, no comparisons were possible. They can be found in ref.
PI.
5. CONCLUSIONS The study reported herein has shown that axisymmetric swirling flows such jets can be numerically investigated by the numerical method developed in ref. [3]. For large radial distance, experiments show that the maximum radial and tangential mean velocity vary asymptotically as l/r and l/r2 and computational predictions corroborate this result. The jet thickness is found to be a linear function of the downstream distance both experimentally and numerically, but the calculated spreading rate is smaller than the experimental one. The discrepancy probably comes from the sequation which is not entirely adequate for rotating flows [24261. Nevertheless, the overall observation of predictions implies that the performance of a simple kc model seems to be encouraging. Concerning future developments, there are several areas in which further research is necessary. The first is to modify the sequation for swirling flows by making C,, a function ofthe gradient Richardson number [25]. The second is to use a spectral model like that of Hanjalic et al. [26] and Launder et al. [27]. The third is the need for additional experimental data, especially for the distributions of V and I?? which will enable refinement of the turbulence model.
AcknowledgmentsThe assistance of Drs J. Cousteix and R. Houdeville of C.E.R.T.O.N.E.R.A. for computations is greatly acknowledged. The author is grateful to Drs D. Vandromme and H. Muhe for their helpfuldiscussion. Thanks are due also to Professor A. Dyment for his encouragements.
REFERENCES
1. A. D. Gosman, F. C. Lockwood and J. N. Loughead, Prediction of recirculating, swirling, turbulent flow in rotating disc systems, J. mech. Engng Sci. 142148 (1976). 2. D. G. Lilley, Prediction of inert turbulent swirl flows, AIAA J. 11,955960 (1973). 3. S. V. Patankar and D. B. Spalding, Heat and Mass Transfm in Boundary Layer, 2nd edn. Intertext, London (1970). 4. S. V. Patankar, Numerical Heat Transjkr and Fluid Flow, Series in Computational Methods in Mechanics and Thermal Sciences, McGrawHill, New York (1980). 5. J. Cousteix, X. De Saint Victor and R. Houdeville, Marching methods to solve the NavicrStokes equations in two and threedimensional flows, Third Symposium on
181
Numerical and Physical Aspects of Aerodynamics Flows, State University, Long Beach, California (1985). 6. D. Vandromme, Contribution B la mod6lisation et g la prtiiction d’boulements turbulents g masse volumique variable. Th&se d’Etat, UniversitC de Lille, France (1983). 7. H. Muh&, Jets toumants libre et pari6tal. Thkse de Docteur Ingknieur, Universitt de Lille, France, (1982). 8. H. Muh6, The swirling radial jet, Structure of complex turbulent shear flow. In IUTAM Symposium, Marseille. SpringerVerlag, Berlin (1982). 9. H. Naji, Modklisation et calcul de l’icoulement turbulent dans un jet tournant. Thtse de Docteur de 3ime cycle, Universitt de Lille, France (1984). 10. K. Hanjalic and B. E. Launder, A Reynolds stress model of turbulence and its application to thin shear flows, J. Fluid Mech. 52,609638 (1972). 11. B. E. Launder, G. H. Reece and W. Rodi, Progress in the development of a Reynolds stress turbulence closure, J. Fluid Mech. 68.537566 (19751. 12. B. E. Launder ahd D. B. Spalding Mathematical Models of Turbulence. Academic Press, New York (1972). 13. B. E. Launder and D. B. Spalding, Numerical computation of turbulent flows, Comput. Meth. Appl. Mech. Engng 3,269289 (1974). 14. A. J. Oliver, The prediction of heat transfer and fluid flow in the entrance region of an annulus with the inner cylinder rotating. Ph.D. thesis, Central Electricity Research Laboratories, Leatherhead, Surrey, U.K. (1975). 15. A. Pollard, Flows in teejunctions. Ph.D. thesis, University of London (1978). 16. B. E. Launder, A. D. Morse, W. Rodi and D. B. Spalding, The prediction of free shear flowsa comparison of the performance of six turbulence models, Proc. Langley Free Shear Flows Conference, Vol. 1 (1972). 17. B. E. Launder, Progress in the modelling of turbulent transport, Lecture series 76, Prediction methods for turbulent flows, V. K. Institute (1975). 18. W. Rodi, Basic equations for turbulent flow in Cartesian and cylindrical coordinates, Imperial College Report, BL/TN/A/36 (1970). 19. W. Rodi, On the equation governing the rate of turbulence energy dissipation, Imperial College Report, TM/TN/A/l4 (1971). 20. P. J. Roache, Computational Fluid Dynamics. Hermosa, Albuquerque, NM (1972). 21. R. D. Ritchmeyer and K. W. Morton, Dzfirence Methods for Initial Value Problem, 2nd edn. Intertext, London (1967). 22. T. M. Shih, Numerical Heat Transfer, series in computational methods in mechanics and thermal sciences. Hemisphere, Washington, DC (1984). 23. A. Baille, Lois de refroidissement des fils chauds $ faibles viresses, Bulletin de la Direction des Etudes et Recherches, E.D.F., France No. 3 (1973). 24. B. E. Launder and A. Morse, Numerical prediction of axisymmetric free shear flows with a Reynolds stress closure. In Turbulent Shear Flows. SpringerVerlag, Berlin (1979). 25. W. Rodi, Influence of bouyancy and rotation on equations for the turbulent length scale, 2nd Symp. Turbulent Shear Flows, pp. 10.3710.42 (1979). 26. K. Hanjalic, B. E. Launder and R. Schiestel, Multipletime scale concepts in turbulent transport modelling, 2nd Symp. Turbulent Shear Flows, pp. 10.3G10.36 (1979). 27. B. E. Launder and R. Schiestel, Application d’un modele de turbulence Bbhelles multiples au calcul d’6coulements libres turbulents, C.r. Acad. Sci. Paris 288,127130(1979).
182
H. N~ur PREDETERMINATION
DUN ECOULEMENT
DE JET TOURNANT
TURBULENT
R&nrmCUne procedure de calcul pas a pas a et6 prise comme base de resolution numtrique des equations de Reynolds gouvemant l’ecoulement turbulent dans unjet tournant. Le caractere turbulent a et6 pris en compte par une modblisation simple bas&esur le concept dune viscosite turbulente dont la determination a et&rtalisee a l’aide du modele kE. Le calcul a permis de determiner, en plus des profils de vitesses moyennes, les tensions de Reynolds, l’inergie cinitique de turbulence et son taux de dissipation. L’accord avec les rtsultats experimentaux est relativement satisfaisant et montre que l’utilisation dune viscositd turbulente isotropique semble correcte.
DIE BERECHNUNG
DER STRBMUNG
EINES TURBULENTEN
ROTIERENDEN
STRAHLS
ZusammenfassungEinerlumlichfortschreitendeIntegrationsmethodewurdeverwendet,umdieReynolds’schen Gleichungen zu l&en, welche die achsensymmetrische, inkompressible, turbulente Strijmung eines rotierenden Strahls beschreiben. Als Turbulenzmodell wurde das ksMode11 mit isotroper turbulenter Viskositlt gewlhlt. A&r dem mittleren Geschwindigkeitsfeld wurden die turbulenten Eigenschaften, wie z. B. Reynolds’sche Schubspannung, kinetische Turbulenzenergie sowie die Dissipationsrate, berechnet. Die Ergebnisse wurden mit experimentellen Daten verglichen. Die Ubereinstimmung ist relativ gut und zeigt, dag die Annahme einer isotropen turbulenten Viskositat gerechtfertigt erscheint.
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