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A SEMINAR ON
“HEAT TRANSFER OF JET IMPINGEMENT ”
Presented by; Shinde Sudhir MohanMM15M09
Savitribai Phule Pune UniversityDepartment of Technology
PuneMechanical & Material Science Engineering
INTRODUCTION It is method for removing a large amount of
heat from striking surface. The fluid exist the nozzles located a short
distance from the surface It is a method of achieving particularly high
heat transfer coefficients in many engineering applications.
like cooling of turbine blades, electronics components
APPLICATION
Internal cooling of turbine blade Cooling of laser weapons, microeletronics
components . Quenching and annealing of non ferros sheet
metal. cooling in grinding processes
LITERATURE REVIEW
PRINCIPLE OF IMPINGEMENT
NOMENCLATURE r/d =radial distance from the stagnation point, d = jet or nozzle diameter, m h = heat transfer coefficient, W/m2K. H = distance between orifice and impingement
plates, m q = heat flux, W/m2 Q = volumetric flow rate, m3/s r = radial distance from the stagnation point, m Re = Reynolds number, dimensionless T = temperature, K ε = emissivity, dimensionless μ = dynamic viscosity, kg/ms ρ = density, kg/m3
OBJECTIVE
To study :The effect of jet width to height
ratio and Reynolds number on the heat transfer characteristics of a laminar flow slot jet impinging on a constant heat flux wall
DESIGN CONSIDERATIONS
Jet type (round of slot) Nozzle to target surface spacing Location of exhaust ports Induced or imposed cross flow Surface motion Angle of impingement Nozzle design Temperature differences between the jet and
the impingement surface
NUMBER OF IMPINGEMENT NOZZLES
Most studies carried out with single nozzles
All industrial applications use array of nozzles where the air jets may interact with each other.
DISTANCE FROM NOZZLE TOIMPINGEMENT SURFACE
Maximum Nusselt number occurs at the stagnation point when the jet is at a distance of six to eight diameters away from the impingement surface. This is the end of the potential core.
A spatial variation in convective heat transfer coefficient occurs away from the stagnation point.
When the distance from nozzle to impingement surface is small (h/D<6), there is a secondary maximum of Nusselt number at a radial distance of 0.5 to 2 nozzle diameters due to the transition from laminar to turbulent boundary layer flow.
EXPERIMENTAL SET-UPa) air jet impinging
b) water jet impinging
Gas Flow Meter recorded the air flow rate in standard liters per minute
(SLPM)
positive displacement pump 0.75kW 2900rpm
JET IMPINGEMENT TEST SECTIONNozzles of 0.5mm, 1mm and 1.5mm diameterOrifice plates 5mm thickness
stainless steel foil of 25μm thickReynolds number Re from 1000 to
20000
jet to target spacing H from 0.5d to 6d
copper bus bar electrodes(50mm x 10mm x 10mm)
Temperature measurement a FLIR ThermaCAM™ A40 infrared camera
HEAT TRANSFER COEFFICIENT
heat flux, q Ts surface
temperature
REYNOLDS NUMBERQ = volumetric flow rate, m3/sρ = density, kg/m3μ = dynamic viscosity, kg/ms
RESULTS AND DISCUSSION
Air Jet
low Reynolds numbers, high heat transfer coefficients can be achieved by small diameter nozzles.
d = 0.5mm; H/d = 2, 4; Re = 1000, 5000
d = 0.5mm, 1mm, 1.5mm; H/d = 2; Re =5000;
d = 1.5mm, H/d = 1, 2, 4; Re = 20000
CONCLUSIONS
for jet diameters of 0.5mm to 1.5mm, Reynolds numbers of 1000 to 20000 and dimensionless jet-to-target spacings of 1 to 4 was investigated.
low jet-to-target spacings and high Reynolds numbers.
the area averaged heat transfer increases with decreasing jet diameter and this is attributed to the higher jet velocities involved when smaller nozzles are used.
The water jets also exhibit secondary peaks, however these have only been observed at a low Reynolds number of 10000 and a low H/d of 1
REFERENCES Babic, D., Murray, D. B., Torrance, A. A., Mist Jet Cooling of
Grinding Processes, Int. J. Mach. Tools Manufact. 45, pp. 1171-1177, 2005
Narumanchi, S. V. J., Amon, C. H., Murthy, J. Y., Influence of Pulsating Submerged Liquid Jets on Chip-Level Thermal Phenomena, Transactions of the ASME, Vol. 125, pp. 354-361, 2003.
Hollworth, B. R., Durbin, M., Impingement Cooling of Electronics, Journal of Heat Transfer, ASME, Vol. 114, pp. 607-613, 1992.
Fitzgerald, J. A., Garimella, S. V., Flow Field Effects on Heat Transfer in Confined Jet Impingement, Transactions of the ASME, Vol. 119, pp. 630-632, 1997.
Thank you!