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Presentation kumar


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Presentation kumar

  1. 1. CFD ANALYSIS OF CROSS FLOW AIR TO AIR TUBE TYPE HEAT EXCHANGER   Vikas Kumar 1* , D. Gangacharyulu 2* , Parlapalli MS Rao 3 and R. S. Barve 4 1 Centre for Development of Advanced Computing, Pune University Campus, Pune, India 2 Thapar Institute of Engineering & Technology, Patiala, India 3 Nanyang Technological University, Singapore 4 Crompton Greaves Ltd, Kanjur Marg, Mumbai, India
  2. 2. Introduction <ul><li>Closed Air Circuit Air Cooled (CACA) electrical motors are used in various industries for higher rating (500 kW and above) applications </li></ul><ul><li>Heat generation due to the energy losses in the windings of motors at various electrical loads under operating condition </li></ul><ul><li>Cold air is circulated in the motor to remove the heat generated </li></ul><ul><li>The hot air generated in the motor is cooled by using an air to air tube type cross flow heat exchangers </li></ul><ul><li>The motor designers are interested to know the temperature distribution of air in the heat exchanger and pressure drop across the tube bundle at various operating parameters, e.g., different hot & cold air temperatures and fluid (hot & cold) flow rates </li></ul>
  3. 3. Large Electrical Motor Heat exchanger Source: M/S Crompton Greaves Ltd. Mumbai, India
  4. 4. Heat Exchanger Geometry External cold air Internal hot air External hot air cooled air cooled air
  5. 5. OBJECTIVE <ul><li>  </li></ul><ul><li>Predictions of </li></ul><ul><li>Pressure </li></ul><ul><li>Air flow and </li></ul><ul><li>Temperature distributions </li></ul><ul><li>in the heat exchangers </li></ul>
  6. 6. Heat Exchanger Geometry
  7. 7. Table 1: Geometrical details of the heat exchanger 61 mm Transverse pitch 6. 41 mm Longitudinal pitch 7. 27 - No. of tubes 5. 1610 mm Tube length 4. 26 mm Tube outer diameter 3. 22 mm Tube inner diameter 2.   1760 x 100 x 765 mm Overall dimension 1. Value/Type Unit Description Sl. No.
  8. 8. <ul><li>Modeling Considerations </li></ul><ul><li>Geometry has symmetry in width wise. </li></ul><ul><li>A section of heat exchanger consisting of 9 rows & 3 columns has been considered for analysis. Each column has 9 tubes. </li></ul><ul><li>Tube is modeled as solid blockage, whereas, the inner volume of the tube has been modeled as blockage with gaseous properties to allow the ambient air to pass through it by using PHOENICS CFD Software. </li></ul><ul><li>Conduction takes place from the tube wall & convection takes place from the surface of the tube. </li></ul><ul><li>The partition plate and baffle participate in heat transfer. </li></ul><ul><li>Temperature & flow distributions have been considered to be three dimensional in nature. </li></ul><ul><li>k-ε turbulence model has been considered. </li></ul><ul><li>Hybrid difference scheme has been used. </li></ul>
  9. 9. The distribution of cells in the three directions are given below: X Direction : 55 Y Direction : 48 Z Direction : 232 The total number of cells in the computational domain is 612,480. Grid generation for heat exchanger
  10. 10. Fig. 3: Side view of the grid
  11. 11. Table 2: Operating boundary conditions of the heat exchanger 228.80 (6.48) cfm (cu.m/m) Volumetric flow rate of hot air 4. 388 (10.98) cfm (cu.m/m) Volumetric flow rate of cold air 3. 63 o C Temperature of hot air 2. 35 o C Temperature of cold air 1. Value Unit Input parameters Sl. No.
  12. 12. Results & Discussions <ul><li>The highest pressure region has been observed nearby the top of the separating plate, which may be due to the large change in the momentum of the cold fluid caused by the plate. </li></ul><ul><li>Hot fluid recirculation has been observed at the top corner of 1 st & 4 th section. </li></ul><ul><li>The temperature drop of the hot air in the 1 st section of the heat exchanger is higher than 4 th section because of the high temperature difference between the cold air and the hot air. </li></ul>
  13. 13. Fig. 4: Pressure distribution in the heat exchanger
  14. 14. Fig. 5: Velocity distribution in the heat exchanger
  15. 15. Fig. 6: Temperature distribution in the heat exchanger
  16. 16. Fig. 7: Temperature distribution in the tube bundle of the heat exchanger
  17. 17. Table 3: Comparison of air temperature prediction at various outlets 44.32 43.68 46.8 Cold air 50.9 49.55 51.8 Hot air 4 th section 65 63 63 Hot air 3rd section 61 63 63 Hot air 2 nd section Hot air 1 st section PHOENICS Simulation 43.68 34.4 3. PHOENICS Simulation 44.70 34.4 2. Experimental 41.9 34.4 1. Cold air Remarks Outlet temperature, o C Inlet temperature, o C Sl. No.  
  18. 18. Fig. 8: A comparison between the results of CFD simulation & experiments
  19. 19. Fig. 9: Temperature distribution in the heat exchanger – a case study
  20. 20. Fig. 10: Temperature distribution of the heat exchanger (after modification of central partition plate)
  21. 21. (Sun Ultra SPARC-450, 300 MHz) Fig. 11: Effect of number of processors in computing time using parallel PHOENICS
  22. 22. Conclusions <ul><li>A method for predicting the pressure, velocity & temperature distributions in the tube type heat exchanger associated with CACA large motor has been developed using PHOENICS CFD software. </li></ul><ul><li>The simulated results predict the temperature distribution reasonably at different locations of the heat exchanger. </li></ul><ul><li>The CFD model may be used to optimize its thermal performance by varying the location of the baffles & the partition plate in the heat exchanger and in turn to improve the performance of electrical motors. </li></ul><ul><li>The parallel PHOENICS can be used to reduce the design cycle of the equipment due to fast computation. </li></ul>
  23. 23. <ul><li>M/S Thapar Centre for Industrial Research & Development, Patiala, India for providing the necessary facilities to carry out this project </li></ul><ul><li>M/S Crompton Greaves, Mumbai, India for providing the funds in addition to drawing, design data and experimental results </li></ul><ul><li>M/S CHAM, U.K (support team) for technical help </li></ul><ul><li>M/S Centre for Development of Advanced Computing (C-DAC), Pune, India for providing the facility to use PARAM 10000 for running parallel PHOENICS and funding for presenting this paper </li></ul>Acknowledgements
  24. 24. THANK YOU