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Fig. 3. Temperature variation across (A) Shell Side and (B) Tube Side.

Figure 3 Temperature variation across (A) Shell Side and (B) Tube Side.

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Design specifications of heat exchanger. Table 1 To verify the accuracy of the numerical model, an experimental setup was used for the selected model. The experimental setup is shown in Fig. 1, consist of two pumps for pumping the water from the heated tank to the shell side and to pump cold water from the respective tank to the tubes. The cold-water pump is of 0.37 kW and 2800 rpm, and for hot water, we can use the desert more cooling pump. An arrangement is used to bypass the flow, which helps to flow additional water from the pipes to the designated tank to maintain adequate flow. For measuring different variables like for flow measurement, flow meter/ rotameter is used. (Flow rate is in LPH). Similarly, for the measurement of tem- perature, J-type temperature sensors is used. Sensors of RTD PT100 type or K type may also be used. The range of a J type sensor is from
Design specifications of heat exchanger. Table 1 To verify the accuracy of the numerical model, an experimental setup was used for the selected model. The experimental setup is shown in Fig. 1, consist of two pumps for pumping the water from the heated tank to the shell side and to pump cold water from the respective tank to the tubes. The cold-water pump is of 0.37 kW and 2800 rpm, and for hot water, we can use the desert more cooling pump. An arrangement is used to bypass the flow, which helps to flow additional water from the pipes to the designated tank to maintain adequate flow. For measuring different variables like for flow measurement, flow meter/ rotameter is used. (Flow rate is in LPH). Similarly, for the measurement of tem- perature, J-type temperature sensors is used. Sensors of RTD PT100 type or K type may also be used. The range of a J type sensor is from
3.1. CFD approach Correlation for Nusselt number. Fig. 1. Shell and tube heat exchanger. Table 3
3.1. CFD approach Correlation for Nusselt number. Fig. 1. Shell and tube heat exchanger. Table 3
The increase in effectiveness is due to the formation of the less dead zone as compared to other geometries. The aligned baffle with baffle cut (AB-30) of 30° is taken for experimental study and the result ob- tained from the numerical result is validated with numerical simula- tion. In this study, the helical and segmental baffle is also compared experimentally. The helical baffle with a helix angle of 25° is taken and compared with the segmental baffle in terms of effectiveness, pressure drop, and Nusselt number. Fig. 5 showsthat the pressure drop for Fig. 2. Line diagram of heat exchanger apparatus.
The increase in effectiveness is due to the formation of the less dead zone as compared to other geometries. The aligned baffle with baffle cut (AB-30) of 30° is taken for experimental study and the result ob- tained from the numerical result is validated with numerical simula- tion. In this study, the helical and segmental baffle is also compared experimentally. The helical baffle with a helix angle of 25° is taken and compared with the segmental baffle in terms of effectiveness, pressure drop, and Nusselt number. Fig. 5 showsthat the pressure drop for Fig. 2. Line diagram of heat exchanger apparatus.
Correlation for friction factor. 3. Result and discussion Table 2
Correlation for friction factor. 3. Result and discussion Table 2
Fig. 4. Effectiveness of different baffles geometries. CFD data for different model. Table 4
Fig. 4. Effectiveness of different baffles geometries. CFD data for different model. Table 4
Heat Exchanger data with tube side. Table 5
Heat Exchanger data with tube side. Table 5
Properties of fluid in heatexchanger. Table 6
Properties of fluid in heatexchanger. Table 6
Fig. 6. Validation of the theoretical model. Stpri/3 — ¥ =j = f/2
Fig. 6. Validation of the theoretical model. Stpri/3 — ¥ =j = f/2
Fig. 5. Effect of Reynold’s number on A) friction factor B) Pressure drop C) Nusselt number (D) Heat transfer coefficient.
Fig. 5. Effect of Reynold’s number on A) friction factor B) Pressure drop C) Nusselt number (D) Heat transfer coefficient.
Fig. 8. Effect of mass flow rate on LMTD and effectiveness. Ram Kunwer: Conceptualization, Software, Validation, Formal
Fig. 8. Effect of mass flow rate on LMTD and effectiveness. Ram Kunwer: Conceptualization, Software, Validation, Formal
Fig. 7. Effect of mass flow rate on LMTD and effectiveness of.
Fig. 7. Effect of mass flow rate on LMTD and effectiveness of.
Fig. 9. Comparison of segmental and helical heat exchanger.
Fig. 9. Comparison of segmental and helical heat exchanger.
Fig. 11. Heat recovery analysis of AB-30.
Fig. 11. Heat recovery analysis of AB-30.
Fig. 10. Heat recovery analysis of heat exchanger without baffle.
Fig. 10. Heat recovery analysis of heat exchanger without baffle.
Fig. 14. Pumping power ratio of helical and Segmental heat exchanger. Fig. 13. Colburn factor of helical and Segmental baffle.
Fig. 14. Pumping power ratio of helical and Segmental heat exchanger. Fig. 13. Colburn factor of helical and Segmental baffle.
Related topics:
Materials ScienceMechanicsShell and Tube Heat Exchanger
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