1. CHE/ME 109 Heat Transfer in Electronics LECTURE 17 – INTERNAL FORCED CONVECTION FUNDAMENTALS

2. INTERNAL FORCED CONVECTION DESCRIPTIONS HEAT TRANSFER IN DUCTS IS A VERY COMMON PROCESS USED FOR COOLING FLUIDS FOR RADIATORS AND HEAT SINKS USED FOR HEAT REJECTION SYSTEMS IN REFRIGERATORS HEAT EXCHANGE PROCESSES MAY TAKE PLACE IN HEAT EXCHANGERS NEED A LARGE AMOUNT OF TRANSFER AREA IN A SMALL FLUID VOLUME DESIGNED FOR EASE OF FABRICATION http://www2.electronicproducts.com/Liquid _cooling_targets_advanced_microelectron ics-article-farr_cooligy_may2008- html.aspx

3. CONVECTION HEAT TRANSFER CORRELATIONS BASED ON MOMENTUM TRANSFER MODELS ERRORS FOR CORRELATIONS + 20% MINOR FACTORS SUCH AS VISCOUS HEATING MAY END UP IN THE NOISE FOR THESE CALCULATIONS, SO ARE IGNORED IN MANY SYSTEMS

4. MEAN VELOCITY AND MEAN TEMPERATURE FLOW REGIMES LAMINAR FLOW IS DEFINED BY Re < 2300 THE VELOCITY PROFILE IS TYPICALLY PARABOLIC FOR DEVELOPED LAMINAR FLOW SEE DEVELOPMENT IN SECTION 8-2

5. MEAN VELOCITY THE VELOCITY IS ZERO- VALUED AT EACH WALL AND GOES TO A MAXIMUM IN THE CENTER THE MEAN VELOCITY IS OBTAINED FROM NOTE THE MEAN VELOCITY WILL NOT BE AT THE CENTER OF THE FLOW

6. MEAN (MIXING CUP) TEMPERATURE IS CALCULATED AS THE AVERAGE TEMPERATURE IN A DUCT CROSS SECTION THE EQUATION FOR CALCULATION IS:

7. TURBULENT FLOW DEFINED BY Re>10000 AVERAGE VELOCITY AND MEAN TEMPERATURES ARE CALCULATED THE SAME AS FOR LAMINAR SYSTEMS THE TURBULENT PROFILE IS TYPICALLY UNIFORM EXCEPT AT THE SURFACES

8. TURBULENT/TRANSITION FLOW THE VALUES FOR AVERAGE VELOCITY AND MEAN TEMPERATURES ARE VERY CLOSE TO THE CENTERLINE VALUES FOR TURBULENT FLOW TRANSITION FLOW IS 2300 < Re < 10000 THERE ARE NO CORRELATIONS FOR THE TRANSITION REGION

9. NON-CIRCULAR DUCTS ADAPTING THESE CORRELATIONS TO NON- CIRCULAR DUCTS ACCOMPLISHED USING THE HYDRAULIC DIAMETER IN THE SAME EQUATIONS. SAME LIMITS FOR FLOW REGIMES ARE NORMALLY APPLIED TO NON-CIRCULAR DUCTS

10. ENTRANCE EFFECTS THE HYDRODYNAMIC ENTRY LENGTH IS THE SECTION OF THE PIPE FROM THE ENTRY TO FULLY DEVELOPED FLOW AS SHOWN IN THIS FIGURE

11. ENTRANCE EFFECTS THE THERMAL ENTRY LENGTH IS THE SECTION OF THE PIPE FROM THE ENTRY TO FULLY DEVELOPED FLOW AS SHOWN IN THIS FIGURE

12. ENTRANCE FLOW CHARACTERISTICS THE BOUNDARY LAYER IS CONTINUOUSLY CHANGING IN THIS REGION THE FRICTION FACTOR CHANGES WITH DISTANCE THE HEAT TRANSFER COEFFICIENT CHANGES WITH DISTANCE BOUNDARY LAYER IN THE ENTRY LENGTH MAY START AS LAMINAR FOR TURBULENT FLOW CONDITIONS, THE BOUNDARY LAYER BECOMES TURBULENT OVER A SHORT DISTANCE

13. ENTRANCE FLOW CHARACTERISTICS

14. ENTRY LENGTH LIMITS FULLY DEVELOPED FLOW IS DEFINED BY THE FRICTION FACTOR AND HEAT TRANSFER COEFFICIENT STAYING CONSTANT ENTRY LENGTH EFFECTS ARE SIGNIFICANT WHEN THE TOTAL LENGTH IS RELATIVELY SHORT (L/D H < 50) EXTENT OF ENTRY LENGTHS FOR LAMINAR FLOW: FOR TURBULENT FLOW:

15. LIMITING SYSTEMS IDEAL SYSTEM MODELS ARE BASED ON EITHER CONSTANT SURFACE TEMPERATURE OR CONSTANT SURFACE FLUX FOR CONSTANT SURFACE HEATING, THE VALUE OF ΔT = T s - T m STAYS CONSTANT T s INCREASES AS T m INCREASES

16. LIMITING SYSTEMS FOR CONSTANT VALUES OF C p AND A s THE RATE OF INCREASE CAN BE EVALUATED AS: THIS RELATIONSHIP DOES NOT APPLY IN THE ENTRY LENGTH

17. LIMITING SYSTEMS FOR CONSTANT SURFACE TEMPERATURE THE VALUE OF ΔT IS ALWAYS CHANGING EVENTUALLY THE BULK TEMPERATURE WILL MATCH THE WALL TEMPERATURE THE DIMENSIONLESS TEMPERATURE CAN BE EXPRESSED AS AN EXPONENTIAL DECAY FUNCTION:

18. CONSTANT SURFACE TEMPERATURE TOTAL HEAT TRANSFER OVER THE DUCT USE AN AVERAGE ΔT FOR THE CALCULATIONS –MATH AVERAGE ΔT : –LOG-MEAN AVERAGE ΔT