DRAG FORCE AND VELOCITY PROFILES FOR A CYLINDER IN CROSSFLOW Tuesday May 6th, 2014 Xie Zheng – First Author, Theory, List of Equipment and Experimental Procedure Kanchan Bhattacharyya – Discussion and Conclusion Matthew Stevens–Abstract, Introduction Ting Zhang – Results Abstract In this experiment we determine the drag force on a cylinder in an airflow, as well as velocity profile of the incoming and exit streams of the airflow. The drag force acting on the cylinder is determined via measurement of the pressure distribution around the cylinder, which is also used to calculate the velocities of the respective inlet and exit streams. It is with these velocities that we are then able to quantify the time rate of change of mass within the control volume and verify that steady state conditions exist. Through the measured pressure and velocity profiles we are then able to verify the respective profiles, the existence of large Reynolds Numbers that arise in turbulent flow regimes, the respective contributions of pressure and friction to the overall drag force acting on the cylinder, and relatively constant mass flow rates throughout the system. We find that in such turbulent situations that pressure is the primary contributor to total drag experienced by the sphere, and that considerable mass flow defects exist in regions near the cylinder as opposed to regions further away from the surface of the cylinder. Finally, we are able to quantify the effects of boundary layers on stream velocity as we find slight variances in the steady state inlet and exit stream velocities. Introduction The ability to quantify the forces and velocities associated with fluid flow around objects is of great importance in the Engineering Sciences, as the measurement of such quantities enables us to fundamentally understand many of the physical phenomena we are exposed to on a regular basis and their mechanisms. For example, we can understand the variance in drag effects experienced by airplanes in flight and those experienced by cars, as well as the kinematic variances in the flight path of a baseball when a pitcher throws pitches with different grips and arm angles. [1] In such cases, the measurement of the pressure distribution acting on the surface of an object allows us to quantify the effects of forces such as drag, and give us the ability to identify the contributors to these effects. For 1 example, we can definitively attribute the presence of the drag acting on buildings to a dominating pressure drag in contrast to drag to friction. [1] Through these concepts and experimental evidence, we can identify many established trends while simultaneously finding validity in the laws that govern the world around us. For example, in measuring the pressure distribution around an object in turbulent flow we can determine the velocity of the fluid at various regions near the object with the help of Bernoulli’s equation describing the flow energy of a fluid in motion. Such velocities can then be used to calculate the Reynolds Number describing the flow scenario, and further quantify the existence of dominant inertial forces giving rise to the large Reynolds Numbers associated with Turbulent flow regimes. Through direct measurement of the pressure acting on a cylinder subjected to high velocity air in turbulent cross-flow, we will be able to determine the velocity of the air flow at various points. It is with these velocities that we can quantify the dominant presence of pressure as the primary contributor to the drag force experienced by the cylinder, as well as the existence of boundary layers that disrupt the flow in the regions neighboring the cylinder and large Reynolds numbers that describe such scenarios. Theory 1. Pressure Drag Measurement To determine the drag force on a cylinder in an airflow, we measure the pressure distribution around the cylinder. Referring to the Figure 1 in lab manual [1], the sum of two forces, pressure and a viscous shear, represent the total drag force experienced by the cylinder in the air stream. And mathematically the total drag force per unit length is: π·π₯ π = ∫2π[π(π)πππ π + π(π)π πππ]π ππ 2 Eq.1 where l is the length of cylinder, Dx is total drag force in x-direction, P is pressure, R is cylinder radius, τ is shear stress and π is angle along cylinder. And the drag coefficient, CD , is defined as: πΆπ·= π·π₯ Eq.2 1 2π π1/2ππ2 0 where ρ is the air density and U0 is the upstream velocity. Inserting Eq.1 for Dx/l and canceling common terms, Eq.2 becomes πΆπ· = 2π 1 ∫ [π(π) − π0 ]πππ πππ ππ02 0 Eq. 3 2. Velocity Profiles and Mass The cylinder retards the air flwoing over it, resulting in a decreased velocity in the wake behind the cylinder. Flowing fluids have two kinds of energy which is kinetic energy and potential energy. By inserting a thin tube, pitot tube, with the opening facing into the flow, the velocity at the opening to the tube can be measured as follows. The tube is connected to a manometer to measure the pressure inside the tube. Just outside the tube, the flow has a velocity and static pressure. The relation between stagnation pressure and static pressure could be written as: 1 ππ π‘ππ = ππ + 2 ππ’2 And π’ = √2 Eq. 4 ππ π‘ππ −ππ Eq. 5 π where Ps=101 Pa the inlet velocity distribution into the test cell is uniform. To measure the inlet velocity, only a single velocity measurement is required. The cylinder is rotated so that the pressure tap hole is oriented into the oncoming stream. Bernoulli’s equation can be written as 3 1 ππ π‘ππ,ππ¦π = ππ + 2 ππ02 Eq.6 Procedure Since the experiment was already setup in the lab, we check the connections of the equipment and make sure we have all the instruments we need. First of all, we opened up the blower to make it keeps flowing the air. After around 10 minutes, the reading of temperature shown on the thermometer first raised several degrees and then became stable, and we recorded the reading when the reading was stabilized. As for the height of the manometer, we also recorded the initial place of the top of the fluid. 1. Pressure Drag Measurement We inserted the circular cylinder with attached protractor through the back of the section, and then connected the cylinder pressure tap to the left port on the manometer. Also, for the upstream pressure port tap, we connected it to the right port of the manometer. So, the reading on manometer became different. We rotated the cylinder from 0 degree to 360 degree with increment of 5 degrees and also recorded the position of the top of the fluid. 2. Velocity Profiles and Mass conservation We connected the Pitot tube to the left port on the manometer and left the right manometer port open to the air. Then, we moved the pitot tube from y=0,, to y=100mm and recorded the position of the top of fluid at manometer. List of equipment Manometer (manufacturer: Dwyer): we used the manometer to measure the difference in pressure by comparing the heights of the fluid. Blower (AIR FLOW BENCH AF10): we use the blower to generate the air flow for experiment. 4 Results b. Plot P(θ)-P0 and (P-P0)COSθvs. θ Figure 1.This figure shows the relationship between P-P0 vs. θ. P-P0 vs. θ 1.5 1 P-P0 0.5 0 0 100 200 300 400 -0.5 -1 -1.5 -2 θ Figure2. This figure shows the relationship between (P-P0 )cosθ vs. θ. (P-P0)COSθ vs. θ 1.2000 1.0000 0.8000 (P-P0)COSθ 0.6000 0.4000 0.2000 0.0000 -0.2000 0 100 200 300 -0.4000 -0.6000 -0.8000 θ 5 400 c. Calculate the pressure drag coefficient governing equation: πΆπ· = 2π 1 ∫ [π(π) − π0 ]πππ πππ ππ02 0 Eq. 3 1 where ππ π‘ππ − π0 = 1.05 ππ π»2 π, according to Eq.2, ππ2 = 0.001913641. 0 2π In order to calculate ∫0 [π(π) − π0 ]πππ πππ, we use Simpson’s Rule, we found πΆπ· = 1.13 d. Calculate the Reynolds number, πΉπ = ππΌπ π /π Table 1. This figure shows the values of μ, ρ, diameter d, velocity U0 and calculated value for Reynolds number Re μ 0.00001511 density ρ (kg/m3) 1.1225 diameter (m) 0.01262 Velocity (U0) 21.5762 Re 20228.15158 According to the graph below, we can find that the CD=1.15 Figure 3 . This figure shows the relationship between CD and Reynolds number 6 Part2.Velocity Profile and Mass Conservation Measurement Calculate the exit velocity of the airflow by using the Eq.4 and Eq.5. Figure 4. . The Exit Velocity Profile Derived from Pitot Tube Measurement 35 30 Velocity m/s 25 20 15 10 5 0 0 20 40 60 80 100 120 Distance [mm] Calculate the mass flow defect by using the following equation: π·πππππ‘ = 1 − π’(π¦) π0 Eq. 7 Figure 5. Mass Flow Defect vs. distance 0.25 Flow Defect 0.2 0.15 0.1 0.05 0 -0.05 -0.1 0 20 40 60 Distance [mm] 7 80 100 120 Use Simpson’s rule again to integrate the exit velocity and calculate the error between inflow and outflow, π» ∫0 ππ’ ππ¦ = ππ0 π» (Simplified intergration) ππππ π = πΜππ −πΜππ’π‘ πΜππ × 100% ππππ π = −11.34% Eq. 8 Eq.9 Eq.10 DISCUSSION For a bluff body like a cylinder in a cross-flow, a boundary layer forms from the stagnation point and over both sides. Since the surface normal pressure is the greatest at the stagnation point and drops as a function of θ until a point near the top and bottom of the cylinder, there is a negative pressure gradient. In this region, where P-P0 decreases as a function of θ, the boundary layer “adheres” to the cylinder. However, the surface normal pressure reaches a minimum at the top and the bottom and gradually increases towards the back of the cylinder. In this region, the boundary layer experiences a positive pressure gradient opposite the flow direction, which will cause the fluid near the surface to eventually come to rest and cause the fluid to separate from the surface, leaving behind a wake region. In Figure 1, P-P0 vs. θ is plotted. In the region where π ≤ 70°, P-P0 continues to drop until reaching the minimum described earlier. After this point, there is a small increase until P-P0 remains constant, which is the wake region. The small increase in pressure is where the fluid will start to separate from the surface of the cylinder. At the end of the wake region, around π ≤ 300°, the pressure difference drops slightly and then rises steadily, and here we return to the boundary layer forming on the bottom face. In Figure 2, (P-P0)cosθ vs. θ is plotted, producing a very different graph. The area under this curve adds up to the pressure drag coefficient, πΆπ· where the body is assumed to be bluff and shear drag is negligible. The graph is cyclic, and has peaks in the pressure differences, appear at π = 8 0°, 170°, 360° where the surface is normal to the flow and therefore the pressure normal is the highest, and has troughs at π = 60° πππ 305° which are near the bounds of the wake region, where the fluid begins to separate from the surface, and have the lowest pressure normals. According to Table 1, the experimental Reynolds number Re ≈ 20228, and from Figure 3, this corresponds to πΆπ· = 1.15. In contrast, the πΆπ· obtained from this experiment’s results and using Simpson’s Rule to integrate numerically, was 1.13. These values are virtually identical and the discrepancy is likely due to the limits of accuracy of numerical integration. This strong agreement attests to the power of this experimental setup and the acceptability of neglecting the shear drag. Now examining the velocity profile in Figure 4, there is a clear dip in the constant free-stream π velocity π0 ≈ 32 π , in the middle of the pitot tube range. This is due to the fact that the air velocity in this region is what has merged together after passing over both sides of the cylinder, with some of the air trapped in the wake region, resulting in a lower velocity reading by the pitot tube. This effect is obviously less apparent the farther away from the cylinder, for streamlines that weren’t part of the viscous boundary layer. Similarly, the mass flow defect is also greatest in the pitot tube region blocked by the cylinder as shown in Fig. 5, as much of the air is trapped in the wake region. Using Simpson’s rule, the error in the inflow and the outflow of mass is ππππ π = −11.34% from Eq. 10. This negative result suggests that the outflow is higher than the inflow, which can only be due to overestimating the exit cross-sectional area, which is reduced because of boundary layers forming on the inner sides of the apparatus. Conclusion The apparatus used in this experiment involving systematically rotating about a cylinder and measuring the pressures normal to the surface as well as those parallel to the flow-lines, proved to be an extremely powerful setup. The pressure drag coefficient, πΆπ· calculated through the numerical 9 integration of (P-P0)cosθ over the domain of θ via Simpson’s Rule, was calculated to be 1.13, which compared to the value from the literature that is expected at the experimental Reynolds number Re ≈ 20228 of 1.15, is practically identical. Such agreement is uncanny and illustrates how accurate this direct measurement of pressure as a function of θ in calculating parameters such as πΆπ· , provided the increment in θ is sufficiently small and efforts are made to achieve a reasonable step size for the numerical integration. The separation of boundary layer flow from the cylinder surface when the pressure normal reaches a minimum and begins to rise is also well represented from the graphs obtained in Fig. 1 and Fig. 2. If there is an issue with this experimental setup, is that there is a significant −11.34% mass flow defect coming from a reduced effective area from boundary layers growing on the inner surfaces of the chamber, causing the actual exit velocity to be higher than assumed. To reduce this effect, introducing a correction factor for the area may prove helpful, which can be done by approximating the size of the boundary layer where the pitot tube measurements are made – that is at the end of the chamber. This can be done after simply after determining whether the flow on the inside of the chamber (different surface) is laminar or turbulent, and applying the correct semi-empirical relation between πΏ and π₯. In general, ~ π π 1/2, and since π π is a function of π₯, it is simple to approximate what the true effective area is at the end of the chamber. REFERENCES 1. F. P. Chiang and T. Y. Hsu, Manual for experiments in solid Mechanics, 2014 10 Appendix Table 2. Data measured and calculated for Pressure Drag Measurement θ (deg.) P(θ) P(θ)-P0 cosθ (P-P0)COSθ 0 2.89 1.05 1.0000 1.0500 5 2.91 1.07 0.9962 1.0659 10 2.91 1.07 0.9848 1.0537 15 2.86 1.02 0.9659 0.9852 20 2.74 0.9 0.9397 0.8457 25 2.63 0.79 0.9063 0.7160 30 2.4 0.56 0.8660 0.4850 35 2.14 0.3 0.8192 0.2457 40 1.88 0.04 0.7660 0.0306 45 1.73 -0.11 0.7071 -0.0778 50 1.30 -0.54 0.6428 -0.3471 55 1.06 -0.78 0.5736 -0.4474 60 0.84 -1 0.5000 -0.5000 65 0.65 -1.19 0.4226 -0.5029 70 0.46 -1.38 0.3420 -0.4720 75 0.52 -1.32 0.2588 -0.3416 80 0.58 -1.26 0.1736 -0.2188 85 0.68 -1.16 0.0872 -0.1011 90 0.74 -1.1 0.0000 0.0000 95 0.78 -1.06 -0.0872 0.0924 100 0.79 -1.05 -0.1736 0.1823 105 0.8 -1.04 -0.2588 0.2692 110 0.8 -1.04 -0.3420 0.3557 115 0.79 -1.05 -0.4226 0.4437 11 120 0.77 -1.07 -0.5000 0.5350 125 0.77 -1.07 -0.5736 0.6137 130 0.76 -1.08 -0.6428 0.6942 135 0.76 -1.08 -0.7071 0.7637 140 0.76 -1.08 -0.7660 0.8273 145 0.75 -1.09 -0.8192 0.8929 150 0.75 -1.09 -0.8660 0.9440 155 0.74 -1.1 -0.9063 0.9969 160 0.75 -1.09 -0.9397 1.0243 165 0.75 -1.09 -0.9659 1.0529 170 0.75 -1.09 -0.9848 1.0734 175 0.76 -1.08 -0.9962 1.0759 180 0.76 -1.08 -1.0000 1.0800 185 0.76 -1.08 -0.9962 1.0759 190 0.76 -1.08 -0.9848 1.0636 195 0.76 -1.08 -0.9659 1.0432 200 0.76 -1.08 -0.9397 1.0149 205 0.76 -1.08 -0.9063 0.9788 210 0.75 -1.09 -0.8660 0.9440 215 0.74 -1.1 -0.8192 0.9011 220 0.75 -1.09 -0.7660 0.8350 225 0.74 -1.1 -0.7071 0.7778 230 0.75 -1.09 -0.6428 0.7006 235 0.75 -1.09 -0.5736 0.6252 240 0.76 -1.08 -0.5000 0.5400 245 0.76 -1.08 -0.4226 0.4564 250 0.77 -1.07 -0.3420 0.3660 255 0.78 -1.06 -0.2588 0.2743 12 260 0.78 -1.06 -0.1736 0.1841 265 0.79 -1.05 -0.0872 0.0915 270 0.78 -1.06 0.0000 0.0000 275 0.78 -1.06 0.0872 -0.0924 280 0.77 -1.07 0.1736 -0.1858 285 0.72 -1.12 0.2588 -0.2899 290 0.62 -1.22 0.3420 -0.4173 295 0.55 -1.29 0.4226 -0.5452 300 0.55 -1.29 0.5000 -0.6450 305 0.62 -1.22 0.5736 -0.6998 310 0.76 -1.08 0.6428 -0.6942 315 0.98 -0.86 0.7071 -0.6081 320 1.25 -0.59 0.7660 -0.4520 325 1.55 -0.29 0.8192 -0.2376 330 1.82 -0.02 0.8660 -0.0173 335 2.05 0.21 0.9063 0.1903 340 2.34 0.5 0.9397 0.4698 345 2.54 0.7 0.9659 0.6761 350 2.73 0.89 0.9848 0.8765 355 2.84 1 0.9962 0.9962 360 2.9 1.06 1.0000 1.0600 Table3 Data calculated for Profile and Mass Conservation Measurement Distance [mm] Pstage [Pa] Pstage-Ps [Pa] Density kg/m3 u [m/s] 0 642.0072 541.0072 1.1225 30.28137 2 637.0304 536.0304 1.1225 30.14177 4 651.9608 550.9608 1.1225 30.55866 6 651.9608 550.9608 1.1225 30.55866 13 8 651.9608 550.9608 1.1225 30.55866 10 651.9608 550.9608 1.1225 30.55866 12 656.9376 555.9376 1.1225 30.69637 14 681.8216 580.8216 1.1225 31.37584 16 691.7752 590.7752 1.1225 31.64354 18 691.7752 590.7752 1.1225 31.64354 20 691.7752 590.7752 1.1225 31.64354 22 681.8216 580.8216 1.1225 31.37584 24 681.8216 580.8216 1.1225 31.37584 26 681.8216 580.8216 1.1225 31.37584 28 681.8216 580.8216 1.1225 31.37584 30 681.8216 580.8216 1.1225 31.37584 32 676.8448 575.8448 1.1225 31.24113 34 661.9144 560.9144 1.1225 30.83346 36 637.0304 536.0304 1.1225 30.14177 38 592.2392 491.2392 1.1225 28.85496 40 547.448 446.448 1.1225 27.50803 42 502.6568 401.6568 1.1225 26.09165 44 487.7264 386.7264 1.1225 25.60212 46 457.8656 356.8656 1.1225 24.59384 48 447.912 346.912 1.1225 24.24843 50 447.912 346.912 1.1225 24.24843 52 452.8888 351.8888 1.1225 24.42175 54 472.796 371.796 1.1225 25.10304 56 497.68 396.68 1.1225 25.9295 58 522.564 421.564 1.1225 26.73042 60 572.332 471.332 1.1225 28.26425 62 612.1464 511.1464 1.1225 29.43382 14 64 646.984 545.984 1.1225 30.42033 66 666.8912 565.8912 1.1225 30.96995 68 691.7752 590.7752 1.1225 31.64354 70 696.752 595.752 1.1225 31.77655 72 696.752 595.752 1.1225 31.77655 74 696.752 595.752 1.1225 31.77655 76 696.752 595.752 1.1225 31.77655 78 696.752 595.752 1.1225 31.77655 80 696.752 595.752 1.1225 31.77655 82 696.752 595.752 1.1225 31.77655 84 691.7752 590.7752 1.1225 31.64354 86 686.7984 585.7984 1.1225 31.50998 88 676.8448 575.8448 1.1225 31.24113 90 671.868 570.868 1.1225 31.10583 92 671.868 570.868 1.1225 31.10583 94 666.8912 565.8912 1.1225 30.96995 96 666.8912 565.8912 1.1225 30.96995 98 646.984 545.984 1.1225 30.42033 100 537.4944 436.4944 1.1225 27.19965 15