Experimental and Numerical Study of Swirling ... - Solid Mechanics
Experimental and Numerical Study of Swirling ... - Solid Mechanics Experimental and Numerical Study of Swirling ... - Solid Mechanics
Experimental and Numerical Study of Swirling Flow in Scavenging Process for 2-Stroke Marine Diesel Engines downstream the flow. At position z 7 (z/D=4.116) and cylinder lengths (8D and 6D), the magnitude of radial velocity becomes very close to zero and then slowly starts increasing again. The mean axial vorticity has a Gaussian like profile at z 1 (z/D=0.963) i.e. for the regions at larger radial distance from the cylinder axis, except the near wall region, the vorticity is very weak and then in the vortex core region it gets very strong. With swirl decay downstream the flow, the vortex core loses its vortical strength by transferring it in outward radial directions. The rate of this vorticity transfer is higher in case of high Reynolds number thus leading to quicker decay of the weak vortical ‘annular region’ in the tangential velocity profile. The detection of vortex core position in the instantaneous PIV measurements at z 1 (z/D=0.963) show that the vortex core position is not stationary and moves in an area of r/R= ±0.2. This indicates a precessing vortex core (PVC) and LDA measurements show that the precession frequencies at Reynolds number of 65000 and 32500 are 5.8 Hz and 3.15 Hz. The precession frequency is found to increase linearly as a function of flow rate. The mean vortex core position is not aligned with the cylinder axis at all measuring positions indicating an asymmetric swirling flow with core following a helical path. The radius of the helical path is not same for all measuring positions and initially the radius of the helical path is smaller but then gradually increases. The helix rotation is in a clockwise direction similar to the swirl which is also in clockwise direction. This together with a Burgers vortex like tangential velocity profile and wake-like axial velocity profile indicate a left-handed helical vortex and having a negative pitch. For all the cylinder lengths the helical vortex core does not complete one revolution. In case of cylinder length 8D, the helical vortex path at the downstream positions, instead of rotating around the cylinder axis, re-twists at one side of the X-axis. In addition, at those far downstream positions the tangential velocity has forced vortex profile, the axial velocity and mean axial vorticity profiles become uniform showing an infinite pitch of the helical path. This indicates a transition of left handed to right handed helical vortex called as ‘L-transition’ and is one of characteristics of vortex breakdown. In the presence of a precessing vortex core (PVC), the measured values of Reynolds stresses are actually a combination of turbulence and vortex core oscillation. The Reynolds stress normal components are high in the vortex core and near wall regions. Considering the maximum values, for normal stresses (Cartesian coordinates) at z (z/D=0.963) ww uu vv . 1 Regarding the components in polar coordinates, v v and vrv r are larger near the wall and in the vortex core regions at z (z/D=0.963). The radial 1 distance, from the vortex center, where vrv r increases towards the vortex center, is larger than the v v and follows the same for both high and low Reynolds numbers. As the swirl decays downstream, the magnitude of radial and tangential fluctuations decrease but their spatial distribution increase to larger radial distances of the cylinder cross-section. 166 Summary & Conclusions
Experimental and Numerical Study of Swirling Flow in Scavenging Process for 2-Stroke Marine Diesel Engines In general the magnitudes of shear stress components, at different measuring positions are observed to be smaller than normal stress components. Considering the maximum values, for shear stresses (Cartesian coordinates) uw vw uv indicating anisotropy of the flow. However, with swirl decay downstream at z (z/D=3.068), the maximum values become almost 5 equal for individual components of both normal and shear stress components i.e. ww uu vv and uw vw uv . The Reynolds stresses decay with the swirl and distribution of normal and shear components tends to become comparatively and gradually more uniform in the flow domain. With swirl decay downstream, the flow at high Reynolds number has higher tendency towards a more uniform spatial distribution of individual Reynolds stress components in the flow domain. At z 1 (z/D=0.963) the turbulent kinetic energy is strong in the vortex core and near wall region. The maximum value is observed in the vortex core region and the contours show an asymmetric distribution. The turbulent kinetic energy decreases downstream. The flow at low Reynolds number is less responsive or in other words more resistive to the variations in vorticity, Reynolds stresses and turbulent kinetic energy as the swirl decays along the pipe. 1.1.2 Effect of Piston Position on the Confined Swirling Flow In this experiment the length of cylinder was kept 4D but the piston is translated and adjusted to fixed positions where it closes the intake to the cylinder by 0% (Fully Open intake port), 25%, 50% and 75%. For each piston position, stereoscopic PIV measurements were conducted at the aforementioned Reynolds numbers. When the piston is partially closing the cylinder intake port, the piston serves as a forward-step facing the incoming flow into the cylinder and affects the magnitude of radial velocity in particular and also tangential velocity to some extent. This consequently increases the axial velocity magnitude. Since the flow rate is kept constant but the inlet area is reduced, therefore, the average velocity at the inlet increases. The piston also behaves as a bluff-body in the flow path generating unsteady fluctuations/ disturbances at the sharp-edge interface of the piston top and outer wall. These fluctuations result in growth of instabilities and waves and are superimposed on already precessing helical vortical flow that is observed when the port is fully open. This indicates that the resulting in-cylinder swirling flow becomes more transient. This also puts some challenge for making non-time resolved PIV measurements. At 25% intake port closure and a given Reynolds number, the peak values of tangential velocity decreases and axial velocity increases. At z 1 (z/D=0.963), 167 Summary & Conclusions
- Page 135 and 136: Experi imental and Numerical N Stud
- Page 137 and 138: Experi imental and Numerical N Stud
- Page 139 and 140: Experi imental and Numerical N Stud
- Page 141 and 142: Experi imental and Numerical N Stud
- Page 143 and 144: Experi imental and Numerical N Stud
- Page 145 and 146: Experimental and Numerical Study of
- Page 147 and 148: Experi imental and Numerical N Stud
- Page 149 and 150: Experi imental and Numerical N Stud
- Page 151 and 152: Experi imental and Numerical N Stud
- Page 153 and 154: Experi imental and Numerical N Stud
- Page 155 and 156: Experimental and Numerical Study of
- Page 157 and 158: Experi imental and Numerical N Stud
- Page 159 and 160: Experi imental and Numerical N Stud
- Page 161 and 162: Experi imental and Numerical N Stud
- Page 163 and 164: Experi imental and Numerical N Stud
- Page 165 and 166: Experimental and Numerical Study of
- Page 167 and 168: Experimental and Numerical Study of
- Page 169 and 170: Experi imental and Numerical N Stud
- Page 171 and 172: Experimental and Numerical Study of
- Page 173 and 174: Experi imental and Numerical N Stud
- Page 175 and 176: Experi imental and Numerical N Stud
- Page 177 and 178: Experi imental and Numerical N Stud
- Page 179 and 180: Experi imental and Numerical N Stud
- Page 181 and 182: Experimental and Numerical Study of
- Page 183 and 184: Experimental and Numerical Study of
- Page 185: Experimental and Numerical Study of
- Page 189 and 190: Experimental and Numerical Study of
- Page 191 and 192: Experimental and Numerical Study of
- Page 193 and 194: Experimental and Numerical Study of
- Page 195 and 196: Experimental and Numerical Study of
- Page 197 and 198: Experimental and Numerical Study of
- Page 199 and 200: Experi imental and Numerical N Stud
- Page 201 and 202: Experi imental and Numerical N Stud
- Page 203 and 204: Experi imental and Numerical N Stud
- Page 205 and 206: Experi imental and Numerical N Stud
- Page 207 and 208: Experi imental and Numerical N Stud
- Page 209 and 210: Experi imental and Numerical N Stud
- Page 211 and 212: Experi imental and Numerical N Stud
- Page 213 and 214: Experi imental and Numerical N Stud
- Page 215 and 216: Experi imental and Numerical N Stud
- Page 217 and 218: Experi imental and Numerical N Stud
- Page 219 and 220: Experi imental and Numerical N Stud
- Page 221 and 222: Experi imental and Numerical N Stud
- Page 223 and 224: Experi imental and Numerical N Stud
- Page 225 and 226: Experi imental and Numerical N Stud
- Page 227 and 228: Experi imental and Numerical N Stud
- Page 229 and 230: Experi imental and Numerical N Stud
- Page 231 and 232: Experi imental and Numerical N Stud
- Page 233 and 234: Experi imental and Numerical N Stud
- Page 235 and 236: Experi imental and Numerical N Stud
<strong>Experimental</strong> <strong>and</strong> <strong>Numerical</strong> <strong>Study</strong> <strong>of</strong> <strong>Swirling</strong> Flow in Scavenging Process for 2-Stroke<br />
Marine Diesel Engines<br />
downstream the flow. At position z 7 (z/D=4.116) <strong>and</strong> cylinder lengths (8D<br />
<strong>and</strong> 6D), the magnitude <strong>of</strong> radial velocity becomes very close to zero <strong>and</strong><br />
then slowly starts increasing again.<br />
The mean axial vorticity has a Gaussian like pr<strong>of</strong>ile at z 1 (z/D=0.963) i.e. for<br />
the regions at larger radial distance from the cylinder axis, except the near<br />
wall region, the vorticity is very weak <strong>and</strong> then in the vortex core region it<br />
gets very strong. With swirl decay downstream the flow, the vortex core loses<br />
its vortical strength by transferring it in outward radial directions. The rate <strong>of</strong><br />
this vorticity transfer is higher in case <strong>of</strong> high Reynolds number thus leading<br />
to quicker decay <strong>of</strong> the weak vortical ‘annular region’ in the tangential<br />
velocity pr<strong>of</strong>ile.<br />
The detection <strong>of</strong> vortex core position in the instantaneous PIV measurements<br />
at z 1 (z/D=0.963) show that the vortex core position is not stationary <strong>and</strong><br />
moves in an area <strong>of</strong> r/R= ±0.2. This indicates a precessing vortex core (PVC)<br />
<strong>and</strong> LDA measurements show that the precession frequencies at Reynolds<br />
number <strong>of</strong> 65000 <strong>and</strong> 32500 are 5.8 Hz <strong>and</strong> 3.15 Hz. The precession<br />
frequency is found to increase linearly as a function <strong>of</strong> flow rate. The mean<br />
vortex core position is not aligned with the cylinder axis at all measuring<br />
positions indicating an asymmetric swirling flow with core following a<br />
helical path. The radius <strong>of</strong> the helical path is not same for all measuring<br />
positions <strong>and</strong> initially the radius <strong>of</strong> the helical path is smaller but then<br />
gradually increases. The helix rotation is in a clockwise direction similar to<br />
the swirl which is also in clockwise direction. This together with a Burgers<br />
vortex like tangential velocity pr<strong>of</strong>ile <strong>and</strong> wake-like axial velocity pr<strong>of</strong>ile<br />
indicate a left-h<strong>and</strong>ed helical vortex <strong>and</strong> having a negative pitch. For all the<br />
cylinder lengths the helical vortex core does not complete one revolution. In<br />
case <strong>of</strong> cylinder length 8D, the helical vortex path at the downstream<br />
positions, instead <strong>of</strong> rotating around the cylinder axis, re-twists at one side <strong>of</strong><br />
the X-axis. In addition, at those far downstream positions the tangential<br />
velocity has forced vortex pr<strong>of</strong>ile, the axial velocity <strong>and</strong> mean axial vorticity<br />
pr<strong>of</strong>iles become uniform showing an infinite pitch <strong>of</strong> the helical path. This<br />
indicates a transition <strong>of</strong> left h<strong>and</strong>ed to right h<strong>and</strong>ed helical vortex called as<br />
‘L-transition’ <strong>and</strong> is one <strong>of</strong> characteristics <strong>of</strong> vortex breakdown.<br />
In the presence <strong>of</strong> a precessing vortex core (PVC), the measured values <strong>of</strong><br />
Reynolds stresses are actually a combination <strong>of</strong> turbulence <strong>and</strong> vortex core<br />
oscillation. The Reynolds stress normal components are high in the vortex<br />
core <strong>and</strong> near wall regions. Considering the maximum values, for normal<br />
stresses (Cartesian coordinates) at z (z/D=0.963) ww uu vv .<br />
1<br />
Regarding the components in polar coordinates, v v <strong>and</strong> vrv r are larger<br />
near the wall <strong>and</strong> in the vortex core regions at z (z/D=0.963). The radial<br />
1<br />
distance, from the vortex center, where vrv r increases towards the vortex<br />
center, is larger than the v v <strong>and</strong> follows the same for both high <strong>and</strong> low<br />
Reynolds numbers. As the swirl decays downstream, the magnitude <strong>of</strong> radial<br />
<strong>and</strong> tangential fluctuations decrease but their spatial distribution increase to<br />
larger radial distances <strong>of</strong> the cylinder cross-section.<br />
<br />
166<br />
Summary & Conclusions