1. Heat Transfer/Heat Exchanger How is the heat transfer? Mechanism of Convection Applications. Mean fluid Velocity and Boundary and their effect on the rate of heat transfer. Fundamental equation of heat transfer Logarithmic-mean temperature difference. Heat transfer Coefficients. Heat flux and Nusselt correlation Simulation program for Heat Exchanger

2. How is the heat transfer? Heat can transfer between the surface of a solid conductor and the surrounding medium whenever temperature gradient exists. Conduction Convection Natural convection Forced Convection

3. Natural and forced Convection  Natural convection occurs whenever heat flows between a solid and fluid, or between fluid layers.  As a result of heat exchange Change in density of effective fluid layers taken place, which causes upward flow of heated fluid. If this motion is associated with heat transfer mechanism only, then it is called Natural Convection

4. Forced Convection  If this motion is associated by mechanical means such as pumps, gravity or fans, the movement of the fluid is enforced.  And in this case, we then speak of Forced convection.

5. Heat Exchangers A device whose primary purpose is the transfer of energy between two fluids is named a Heat Exchanger.

6. Applications of Heat Exchangers Heat Exchangers prevent car engine overheating and increase efficiency Heat exchangers are used in Industry for heat transfer Heat exchangers are used in AC and furnaces

7. The closed-type exchanger is the most popular one. One example of this type is the Double pipe exchanger. In this type, the hot and cold fluid streams do not come into direct contact with each other. They are separated by a tube wall or flat plate.

9. Principle of Heat Exchanger First Law of Thermodynamic: “Energy is conserved.” 0 000 Control Volume Qh Cross Section Area HOT COLD Thermal Boundary Layer

10. Q hot Q cold ThTh T i,wall T o,wall TcTc Region I : Hot Liquid- Solid Convection NEWTON’S LAW OF CCOLING Region II : Conduction Across Copper Wall FOURIER’S LAW Region III: Solid – Cold Liquid Convection NEWTON’S LAW OF CCOLING THERMAL BOUNDARY LAYER Energy moves from hot fluid to a surface by convection, through the wall by conduction, and then by convection from the surface to the cold fluid.

11. Velocity distribution and boundary layer When fluid flow through a circular tube of uniform cross- suction and fully developed, The velocity distribution depend on the type of the flow. In laminar flow the volumetric flowrate is a function of the radius. V = volumetric flowrate

12.  In turbulent flow, there is no such distribution. The molecule of the flowing fluid which adjacent to the surface have zero velocity because of mass-attractive forces. Other fluid particles in the vicinity of this layer, when attempting to slid over it, are slow down by viscous forces. r Boundary layer

13. Accordingly the temperature gradient is larger at the wall and through the viscous sub-layer, and small in the turbulent core. The reason for this is 1) Heat must transfer through the boundary layer by conduction. 2) Most of the fluid have a low thermal conductivity (k) 3) While in the turbulent core there are a rapid moving eddies, which they are equalizing the temperature. heating cooling Tube wall h

14. Region I : Hot Liquid – Solid Convection Region II : Conduction Across Copper Wall Region III : Solid – Cold Liquid Convection + U = The Overall Heat Transfer Coefficient [W/m.K] roro riri

15. Calculating U using Log Mean Temperature Hot Stream : Cold Stream: Log Mean Temperature

16. CON CURRENT FLOW COUNTER CURRENT FLOW T1 T2 T4 T5 T3 T7 T8 T9 T10 T6 Counter - Current Flow T1 T2 T4 T5 T6 T3 T7 T8 T9 T10 Parallel Flow Log Mean Temperature evaluation T1T1 A 1 2 T2T2 T3T3 T6T6 T4T4 T6T6 T7T7 T8T8 T9T9 T 10 Wall ∆ T 1 ∆ T 2 ∆ A A 1 2

17. T1T1 A 1 2 T2T2 T3T3 T6T6 T4T4 T6T6 T7T7 T8T8 T9T9 T 10 Wall

18. DIMENSIONLESS ANALYSIS TO CHARACTERIZE A HEAT EXCHANGER Further Simplification: Can Be Obtained from 2 set of experiments One set, run for constant Pr And second set, run for constant Re h

19. For laminar flow Nu = 1.62 (Re*Pr*L/D) Empirical Correlation Good To Predict within 20% Conditions: L/D > 10 0.6 < Pr < 16,700 Re > 20,000 For turbulent flow

20. Overall Coefficient Overall Heat Transfer Coefficient An essential requirement for heat exchanger design or performance calculations. Contributing factors include convection and conduction associated with the two fluids and the intermediate solid, as well as the potential use of fins on both sides and the effects of time-dependent surface fouling. With subscripts c and h used to designate the hot and cold fluids, respectively, the most general expression for the overall coefficient is:

21. Overall Coefficient  Assuming an adiabatic tip, the fin efficiency is  

22. LMTD Method A Methodology for Heat Exchanger Design Calculations - The Log Mean Temperature Difference (LMTD) Method - A form of Newton’s Law of Cooling may be applied to heat exchangers by using a log-mean value of the temperature difference between the two fluids: Evaluation of depends on the heat exchanger type. Counter-Flow Heat Exchanger:

23. LMTD Method (cont.) Parallel-Flow Heat Exchanger:  Note that T c,o can not exceed T h,o for a PF HX, but can do so for a CF HX.  For equivalent values of UA and inlet temperatures, Shell-and-Tube and Cross-Flow Heat Exchangers:

24. Energy Balance Overall Energy Balance Assume negligible heat transfer between the exchanger and its surroundings and negligible potential and kinetic energy changes for each fluid. Assuming no l/v phase change and constant specific heats, Application to the hot (h) and cold (c) fluids:

25. Special Conditions Special Operating Conditions  Case (a): C h >>C c or h is a condensing vapor – Negligible or no change in  Case (b): C c >>C h or c is an evaporating liquid – Negligible or no change in  Case (c): C h =C c. –