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International Journal of Scientific & Engineering Research, Volume 3, Issue 10, October-2012 ISSN 2229-5518 Recovery Exchanger Table 1.[1-3] Description Location Design ambient Air temperature Waste Heat Details: Primary heat source Engines Model Number of engines employed Exhaust Gas Mass Flow from 1 No. unit Exhaust Gas Mass Flow from 1 No. unit Exhaust Gas Mass Flow from 1 No. unit Exhaust Gas Mass Flow from 8 Nos. Unit Exhaust gas tempera- ture Outlet temperature Restriction Hot oil Temperature at HEX Inlet Hot oil Temperature at HEX Outlet Total Hot Oil Flow from 1 No. HEX Total Hot Oil Flow from 8 Nos. HEX Net Total Heat Recov- ery In 1 No.HEX Net Total Heat Recov- ery In 8 Nos.HEX 285/145 ̊C 42/60 ̊C Thermal Oil Heater are given. Value Bangladesh - 35 ̊C - Exhaust gas - from engines MWM - TCG2032V16 8 - 5.77 (kg/s) 20770 (kg/hr) 20770 (kg/hr) 166160 (kg/hr) 479 ̊C 190 ̊C 3 working fluid transported into the WHOH, the working fluid is not exposed to very high temperatures and the consequent thermal stability issues. The total volume of working fluid is also minimized. The thermal oil subsystem contains a control valve to limit the maximum input thermal energy to the level required by the ORC turbo generator to produce the rated electrical power. Signals from the ORC turbo generator to the control valve ac- tuator command a position change to satisfy this criterion. The control valve position is returned to the ORC turbo generator controller for confirmation. If the maximum temperature of the thermal source exceeds the use temperature of available oils, a means to cool the oil (e.g. radiator) or to bypass the WHOH is required for periods when the thermal source is flowing but the turbo generator is off line (i.e. not removing heat from the oil).Considering the characteristics of the fore- casted power plant, the suitable ORC solution is the employ- ment of one Turboden 30 –HR is being selected; in the table 1 the performance of the unit, data for designing of Waste Heat Net Total Heat Recov- ery In 8 Nos.HEX Allowable pressure Drop Across HEX & Diverter valve SHC of the heat source Heat source cool down to Thermal loss consider Overall thermal power recover ORC units employable ORC hot hot source ORC thermal power input Hot source nominal temperature in/out [+/- 5̊ C] Cooling water tempera- ture in/out [+/- 5̊ C] Exhaust Gas Composi- tion (V/V%) customer to confirm in writing CO2 8% 14.68 (MW) 500 (mmWC) 1,116 Kj/kgk 170 Deg.C 1% - 15.752 MWt Turbonden 30- - HR Thermal oil - 15.752 MWt Unit Engine Ex- haust gas 12624180 (kcal/hr) 160 O2 H2O N2 Gross ORC active elec- tric power [+/- 10̊ C] ORC captive consump- tion(*) Net ORC active electric power output [+/- 10%] Electric generator 10.1 % 4.8 % 77.1 % 2.63 MWe 130 kWe 2500 kWe Asynchronous, - 3 phase, 50 Hz, M.V. ̊C 280 ̊C 24312 (kg/hr) 194493 (kg/hr) 1578023 (kcal/hr) (*) Net of ORC internal consumption (mainly feed pump). No external consump- tion are included (i.e. thermal oil system, heat dissipation system, etc). 5 Results By considering thermal losses 1% for the eight units, the gross ORC active electric power can be achieved (+/10%) 2.630 MWe.[1] 6 Conclusion For the cogeneration of industrial waste, the use of ORC offers some potentiality. As the cost of energy increases day by day, the use of organic Rankine cycles for effective energy utiliza- tion can be expected to become more important in developing IJSER © 2012 http://www.ijser.orgPDF Image | Waste Heat Recovery System by Using ORC
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