To determine the temperature distribution of the PIN - FIN for forced convection and to find the FIN efficiency
Duct width (b) = 150mm
Duct height (w) = 100mm
Orifice Diameter (dO) = 24mm
Orifice coefficient (Cdd) = 0.6
Fin length (L)= 14.5cm
Fin diameter (Df) = 12mm (Characteristic length)
S. No. | Mode | Manometer reading (cm)/h1/h1/h = h1-h2 | Power (watts)/V/I/Q= V x I | Temperature/T1/(°C)/T2/(°C)/T3/(°C)/T4/(°C)/T5/(°C)/T6/(°C)/T7/(°C) | Amb temp/T8/(°C) |
1 | Forced convection | ||||
2 | |||||
3 | |||||
4 | |||||
5 |
Ref:-Heat and Mass Transfer Data book by C.P Kothandaraman & Subramannian , New Age publishers.
Flim Temperature (Tf) = --------------
Vo = Cd*a1*a2*V2gha/(a21- a22)
Where Cd = Co-efficient of orifice = 0.6
g= Gravitational constant = 9.81 m/sec 2
h = heat of pipe (pw/pa)h
a1= area of the Pipe
a2 = area of the orifice
W = width of duct
B = Breadth of the duct
Where Va - Velacity of the duct
ρa = Density of the duct
μa= Viscosity of air at T8 ° C
Where Cpa = Specific heat of air
μa = Viscosity of air
Ka = Thermal conductivity of air
Nusselt number (Nnu)
For 40 < NRe < 4000
Nnu = 0.683 (NRe) * 0.466 (Npr)0.331
For 1 < NRe < 4
Nnu = 0.989 (NRe) 0.33 (Npr) 0.33
For 4< NRe < 40
For 4000 < NRe < 40000 NRe
Nnu = 0.193 ( NRe) 0.618 (Npr) 0.33
For NRe > 40000
Nnu = 0.0266 ( NRe) 0.805 (Npr) 0.333
Heat transfer co - efficient h = Nnu * (Ka / L)
Ka = Thermal conductivity of air
L = Length of Fin
H= heat transfer co-efficient
L = Length of the fin
m = V(hp / (Kbx A))
P = Perimeter of the fin = ( μ* Diameter of the fin)
A = cross section area of the fin
Kb= Themal conductivity of brass rod
Temperature distribution = T x = { [(Cosh m(L-X) /Cosh (M )] * (To -Ta)} + T
X= distance between thermocouple and heater
Distance between thermocouples = 20 mm
Nnav = (hD)/K = 1.1 (Gr Pr) 1/6 for 1/10 < Gr Pr < 104
Nnav = 0.53 (Gr Pr)1/4 for 104 < Gr Pr < 109
Nnav = 0.13 (Gr Pr) 1/3 for 109 < Gr Pr < 1012
Where Nnav = average Nusselt Number = (h D)/K
D= Diameter of fin
K = Thermal conductivity of air
Gr = Grashof number - g β Δ;D3/ γ2
β = Coefficient of thermal expansion - 1/ ( Tav + 273) ΔT = (Tav -T amb)
Pr = Prandtl number = (μCp/K)
The heat transfer rates of the fin is determined and the values are
Temperature distribution:
Fin efficiency:Orifice- meter is used to measure discharge.
Blower is an external mechanical device which is essential for forced convection process
The rate equations for convective heat transfer between a surface and an adjacent fluid is prescribed by Newton’s law of cooling
Range of 'h'for natural convection in gases is 3-25W/m2 -k & for liquids it is 50- 350W/m2 -k.. Boundary layer is a thin layer at the surface where gradients of both velocity& temperature are large.
Nusselt Number represents the enhancement of heat transfer through a fluid layer as a result of convection relative to conduction across a same layer. Larger the Nu, more effective is convection.
Boundary layer is a thin layer at the surface where gradients of both velocity & temperature are large.
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