A multi-stagé high-pressure steam turbine is supplied with steam at a stagnation pressure of 7 MPa. and a stagnation temperature of 500°C. The corresponding specific enthalpy is 3410 kJ/kg. The steam exhausts from the turbine at a stagnation pressure of 0.7 MPa, the steam having been in a superheated condition throughout the expansion. It can be assumed that the steam behaves like a perfect gas over the range of the expansion and that y = 1.3. The specific volume of superheated steam is represented by pv = 0.231(h-1943) where p is in kPa, v is in m³kg and h is in kJkg. Given that the turbine flow process has a small-stage efficiency of 0.82, detemine the temperature and specific volume at the end of the expansion.

Air (MW=29 g/mol) at 115.00 kPa and 285.00  is compressed steadily to 600.0 kPa. The mass flow rate of the air is 2.00 kg/s and a heat loss of 32.1 kW occurs during the process. You may assume that changes in kinetic and potential energy are negligible, the temperature of the surroundings is 25 ∘C, and that the CP of air is 3.5 R. Given the compressor operates with a second law (reversible) efficiency of 0.60,calculate the following. What is the actual work interaction term in kW? What is the actual exit temperature of the air in Celcius?

Apply the first law of thermodynamics to nozzle. Assume that the process is reversible adiabatic. Draw the neat sketch and lable inlet and outlet properties

Write the expression of heat for an isothermal reversible expansion of a perfect gas from initial volume V1 to final volume V2.