The solution shown above is absolutely correct. The enthalpy value at each point before entry and exit are taken from the saturated water enthalpy table from steam table.
The pump work is m.v( P2-P1). Here, v is specific volume at saturated water at 10 kPa.
The enthalpy at point 4 (exit of turbine) is calculated from formula h = hf + x( hg - hf) at pressure 10 kPa..
Since, from first law of thermodynamics, the net heat transfer is equal to net work transfer in the cycle. So the entropy change is zero.
And, thermal efficiency of the actual cycle is 28.8% and that of ideal cycle is 38.05%.
Thermal efficiency= 1 - T2/T1
= 1 - 293/473
= 38.05%.
So, the process is irreversible.
Solution kg a. Wump(2088.9W kg kg h2 is from table C-4, and hi is from table C-1 at 20 °C. Altern...
8.21 Figure P8.21 provides steady-state operating data for a vapor power plant using water as the working fluid. The mass flow rate of water is 15 kg/s. The turbine and pump operate adiabatically but not reversibly. Determine di (b) AC 8 o anidhu od o mpo? (b) the rates of heat transfer Qin and Qout, each in kW. (a) the thermal efficiency Steam generator Turbine m= 15 kg/s 10 out 5 PROBE N Condenser Pump Analyzing Bank 3 is the...
This is from a practice test and I want to be able to check my
answers so any help you can give will be greatly appreciated!
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1. (20 points) Consider a cogeneration system operating at steady state. Superheated steam enters the first turbine stage at 6 MPa, 540 °C. Between the first and second stages, 45% of the steam is extracted at 500 kPa and diverted to a process heating load of 5 x 108 kl/h. Condensate exits the process heat exchanger at 450 kPa with specific enthalpy of 589.13 kl/kg and is mixed with liquid exiting the lower pressure pump at 450 kPa. The entire...
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A=0
B=3
C=4
D=0
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