4 th European Conference on Mixing Warszawa, September THE VELOCITY FIELD IN THE DISCHARGE STREAM FROM A RUSHTON TURBINE IMPELLER Jan Talaga a, Ivan Fořt b a Cracow University of Technology, Institute of Heat and Process Engineering, -864 Kraków, Al. Jana Pawła II 7, Poland b Department of Process Engineering, Czech Technical University in Prague, Technicka 4, 667 Prague 6, Czech Republic jtalaga@pk.edu.pl Abstract. The axial profiles of the mean velocity components were investigated in the impeller discharge stream of a Rushton turbine in a pilot plant mixing vessel using the results of twocomponent Laser Doppler Anemometry (LDA). The influence of the radial distance and the blade height on the velocity profiles was processed in the form of correlation equations. The experimental results and the statistical correlations were also compared with a phenomenological model describing the velocity profiles of the radial component of the mean velocity in the impeller discharge stream. Keywords: agitated vessel, Rushton turbine, impeller discharge stream, velocity profiles, LDA.. EXPERIMENTAL INVESTIGATIONS studies were carried out in a pilot plant agitated vessel (Fig. ) with internal diameter T = 86 mm with a flat bottom and equipped with four standard radial baffles. The impeller was a Rushton turbine with diameter of D = /T and a standard geometry. The velocity of the liquid in the discharge stream from the impeller was determined on the basis of instantaneous velocity measurements made using a Laser Doppler Anemometer (LDA) []. On the basis of the results of measurements of the radial velocity B component, its distribution along the height of the impeller blade, the velocity profile can be described by the following exponential T function []: b d D h C T= 86 mm D = / T d =.66 D C = D b =.5 D h =. D B = / T Figure. Geometry of the stirred vessel equipped with a Rushton turbine. = exp( a + b z + c ) () z where is the dimensionless radial component of the mean velocity normalised with the impeller tip velocity wr = Wr / πdn and z is the dimensionless axial coordinate normalised with the half-height of the impeller blade z = z / h. Appearing in equation () the coefficients 467
a, b and c include the dependence on the distance from the tip of the turbine blades. The coefficients are a function of the dimensionless radius r = r / D of the tank, and they are defined using the following quantitative relations:, 5 a =. 6 5. 56r +. 57r. 68r (), 5 b =. 4+ 6. 7r 7. 4r +. r () c = (.. r ) (4) z = z / h.5 -.5 r =.84 C/D = r =.6 r =.4 r =. r = r =.5 r =.6 r =.7 r =.58 z r =.79..4.6.8 wr Figure. Axial profiles of the dimensionless radial component of the mean velocity, according to Eq.(). The graph reproduced in Fig. shows the radial component of the mean velocity distributions along the height of the impeller blade - expressed on the basis of equation () - for various distances r from the tip of the blades. The radial velocity distribution in the flow of liquid near the agitator blades is practically symmetrical along the entire height of the blade (the plane of the impeller separating disk), and the maximum speeds take place in the middle of its height, while further away from the blade this maximum is shifted toward the upper half of the blade, because of the asymmetrical position of the impeller in the vessel. During the experimental investigations the velocity profile of the tangential component was also determined and it can be described by equation of the same form as for the radial component this is: w tg = exp( a + b z + c ) (5) z where the coefficients a, b and c are defined using the following quantitative relations: a =.. 54r +. r (6) b =.. r. (ln r) (7). 5 c =. 66. 8r +. 7r (8) 468
. PHENOMENOLOGICAL MODEL OF THE VELOCITY PROFILES IN A DISCHARGE STREAM z r r/σ It is assumed [] that the impeller as a source of motion may be replaced by an axially symmetric cylindrical slot - the tangential cylindrical jet (Fig. ). The radius of the cylindrical tangential jet was calculated as the arithmetic mean of values: a = r sinα (9) α w tgr determined from the measured values of the radial and tangential mean velocities and angle alpha calculated from the relation: a D Figure. Cylindrical tangential jet. α = arctg( Wtg / Wr ) () for various radial positions given by the radial coordinate expressed in dimensionless form r = r / D. The dependence of the radial component of mean velocity W r on the axial coordinate z is expressed in dimensionless form as [4,5]: { tg h [ A ( z )]} A A =, r = const () Parameter A in Eq. () represents the maximum dimensionless radial velocity component of the liquid on a given profile along the blade height and for the given radial coordinate. This parameter is determined by the relation: A = A σ πdn r / ( r a / 4 ) () Parameter A represents the reciprocal width of the stream on a given position, σ/r (Fig. ), normalised by the half-height of the blade h/: A σ h = () 4r Parameter A in Eq. () expresses the dimensionless axial coordinate of the maximum on the velocity profile, i.e. its shift off the horizontal plane of coordinate z =. Parameters A, A, A were found by nonlinear regression and fit the experimental of the velocities profiles = f(z) for various radial coordinates r. The appointed values of A and A were used to calculate - for the known values of the parameter a (Eq. (9)) and the radial coordinate r - the quantity σ (Eq. ()) and A in dimensionless form as A/(πD n) (Eq. ()). The values of determined parameters σ and A/(πD n), and also parameter a (Eq. (9 and )), are presented in Table. The Table also presents the results of experiments and calculations made by other authors. 469
Table. Determined parameters of the velocity field in the discharge stream from a Rushton turbine. Author D/T C/T D [m] a [m] σ A/πD n This work / /.86.49 ±.49 4.88 ±.5. ±. / /.5.86. Fořt et al. [4] / /. 4.8.4 / /.5.. / /.4.49 5.. Obeid et al. [5] / /.4.5 7.9. / /. 5.5.4 Drbohlav [6] /4 /..6.9 Bertrand [7] / /.4 7.87. Möckel [8] / /.5 4.6.6 / /.5 7.5.9 The values of the parameter a in each case depends on the conditions of mixing according to the relation: a / D =.87 Re M.6 [5]. The value of parameter a is dependent on the impeller Reynolds number [5], so it depends in particular on the rotational speed of the impeller. On the basis of the results of experimental investigations and calculated results for impeller rotation speed n in the range from 4.7 to 7.5 s, the following relationship has been found between the dimensionless parameter a/d and the impeller Reynolds number: a 7 =. 8 ReM. D (4) where the impeller Reynolds number is defined as follows: n D Re M = (5) ν where ν is the kinematic viscosity of an agitated liquid. The values of parameters σ and A/(πD n) correspond fairly well to the same parameters determined by Fořt at al. [4] and Obeid et al. [5]. The exponent in Eq. (4) is slightly lower than the value published by the same authors, probably because in the cited articles the diameter of the vessel T =m, while in this study T=.86m. It follows from the results of experimental studies for the case of D/T = / and C/D =, that parameter A in Eq. () is not equal to zero, because there is an axial displacement of the velocity profile maximum relative to the horizontal plane z =. The value of this displacement is a function of the radial coordinate r in accordance with the found relationship: 4. 95 r =. 69 D A (6) The quantities a, σ, A/(πD n) and on this basis the calculated parameters A, A, A were used to calculate the axial profiles (along the impeller blade height) of the dimensionless radial component of the mean velocity for various radial coordinates, i.e. various positions in 47
z = z / h.5 -.5 r =.84 r =.4 r = C/D = r =.5 r =.6 r =.7 r =.58 r =.79 r =.6 r =. z..4.6.8 Figure 4. Axial profiles of the dimensionless radial component of the mean velocity, according to Eq. (). the discharge stream from the Rushton turbine. The results of these calculations are presented in Figure 4. The results for the radial component of the mean velocity obtained on the basis of the phenomenological model (Eq. ()) were compared with the results from the statistical model described by Eq. (). A comparison of the radial velocity profiles in the discharge stream of stirrer set on the basis of equations () and (), and the corresponding experimental results are presented in Figures 5 for the cases of four different distances r from the tip of impeller blades. Eq. ().5 Eq. ().5 z z = z / h -.5 z = z / h -.5 r=. Eq. () Eq. () z C/D = r=.6 C/D =..4.6.8....4 Eq. () Eq. ().5 Eq. ().5 Eq. () z = z / h z = z / h -.5 -.5 z z C/D = r=.4 C/D = r=.6....4....4 Figure 5. Comparison of dimensionless radial velocity profiles and experimental for various radial coordinates r. 47
. DISCUSSION The two velocity profiles (Equations and ) describe with sufficient accuracy the radial velocity distribution in the range of the dimensionless radius r of to.. The velocity distributions along the impeller blades are comparable, and are consistent with the experimental. The average relative error of Eq. () in relation to the measurement is 9.87%, while average relative error of Eq. () is 8.%. The differences between the accuracies in determining these profiles corresponds to the form of expression of the governing equations for the models. Three parameters of Eq. () were calculated by the method of the least squares of the best fit correlation (Eqs., and 4), but parameters A and A of Eq. () depend on the radial coordinate r according to the model (Eqs. and ). However, the phenomenological turbulent flow model in the discharge stream from the turbine impeller enables some turbulent characteristics (e. g. the eddy viscosity) to be determined, while the empirical model is based on the best fit of the chosen formula to the experimentally determined velocity profile W r =W(r). On the basis of the experimental results, it can be concluded that, in the case of impeller off bottom clearance C/T = /, parameter A in the phenomenological model (Eq. ) is different from zero and must be taken into account. However, for impeller off bottom clearance C/T = / its value amounts zero [9]. It follows from our experimental that the dependence of parameter A on the dimensionless radial coordinate is expressed by the power form Eq. 6. For a dimensionless radius greater than.4, the compared velocity distributions show significant differences. In this case, the error of Eq. () is 55.% and the error of Eq. () is 7.9%. Fluid flow in the range of r > is already determined by the effects of baffles. This is not consistent with the adopted model of free and uninterrupted flow in the impeller discharge stream. Acknowledgment The authors are grateful for financial support from the National Science Centre in Poland (Grant: No.: 64/B/H//4) and the Czech Science Foundation (Grant No. 4/9/9). 4. REFERENCES [] Talaga, J.,. Badania prędkości przepływu w strumieniu wylotowym cieczy dla mieszadła turbinowego tarczowego, Inż. Aparat. Chem., 4, 4-5. [] Talaga, J.,. Untersuchungen zur Fluiddynamik von ein- und zweiphasigen Rührwerksströmungen, in: Process Engineering and Chemical Plant Design, (G. Wozny, Ł. Hady, eds), Universitätsverlag der TU Berlin, pp. 8-48. [] Cutter L. A., 966. Flow and turbulence in stirred vessels, AICHE J.,, 5-44. [4] Fořt I., Möckel H.-O., Drbohlav J. and Hrach M., 979. The flow of liquid in a stream from the standard turbine impeller, Coll. Czech. Chem. Commun., 44, 7-7. [5] Obeid A., Fořt I. and Bertrand J., 98. Hydrodynamic characteristics of flow in systems with turbine impeller, Coll. Czech. Chem. Commun., 48, 568-577. [6] Drbohlav J., 976. PhD Thesis. Prague Institute of Chemical Technology, Prague (Czech Republic). [7] Bertrand J., 98. PhD Thesis. Institut du Genie Chimique, Toulouse (France). [8] Möckel H. O., 978. PhD Thesis. Ingenieur Hochschule Köthen, Köthen (Germany). [9] Drbohlav J., Fořt I., Máca K. and Ptáček J., 978. Turbulent characteristics of discharge flow from turbine impeller, Coll. Czech. Chem. Commun., 4, 48-6. 47