This Solved Problem is an extension of **Solved
Problem 4.1** in which we extend the
**de-aerator**
by tapping steam from the Low Pressure turbine at 800
kPa and feeding it into the de-aerator at the same pressure, thus
converting it into an **Open
Feedwater Heater**, as shown in the
following diagram:

This system is referred to as a **Regenerative
Reheat** cycle, and we will find that
this simple extension of our previous sytem will result in an
increase in thermal efficiency of the power plant.

Note that prior to doing any analysis we always first
sketch the complete cycle on a **P-h****diagram** based on the
pressure, temperature, and quality data presented on the system
diagram. This leads to the following diagram:

On examining the *P-h* diagram plot we notice
the following:

A mass fraction of the steam y is tapped from the LP turbine at the turbine tap (t) such that mixing it with (1-y) of the liquid water at station (6) will result in the fluid reaching a saturated liquid state at staion (7).

The feedwater pump then pumps the liquid to station (8), thus saving a significant amount of heat from the steam generator in heating the fluid from station (8) to the turbine inlet at station (1). It is true that with a mass fraction of (1-y) there is less power output due to a reduced mass flow rate in part of the LP turbine from the tap (t) to station (4), however the following analysis shows that the net result is an increase in thermal efficiency.

Thus once more we see that in spite of the complexity
of the system, the *P-h* diagram
plot enables an intuitive and qualitative initial understanding of
the system. Using the methods described in **Chapter
4b** for analysis of each component, as
well as the **steam
tables** for evaluating the enthalpy at the
various stations (shown in red), and neglecting kinetic and potential
energy effects, determine the following:

a) Assuming that the open feedwater heater is adiabatic, determine the mass fraction of steam y required to be bled off the LP turbine which will bring the fluid from station (6) to a saturated liquid state in the

**de-aerator**. [y = 0.18]

b) Assuming that both the condensate pump and the feedwater pump are adiabatic, determine the power required to drive the two pumps [236 kW].

On examining the system diagram above we noticed something very strange about the feedwater pump. Until now we considered liquid water to be incompressible, thus pumping it to a higher pressure did not result in an increase of its temperature. However on a recent visit to the Gavin Power Plant we discovered that at 25MPa pressure and more than 100°C water is no longer incompressible, and compression will always result in a temperature increase. We cannot use the simple incompressible liquid formula to determine pump work, however need to evaluate the difference in enthalpy from the**Compressed Liquid Water**tables, leading to the following results:

c) Assuming that both turbines are adiabatic, determine the new (reduced) combined power output of both turbines. Recall from

**Solved Problem 4.1**that the power output of the turbines was found to be 10.6 MW if no steam is bled from the LP turbine [9.65 MW]

Thus as expected we find that the net power output is slightly less than the previous system without the turbine tap. However power control is normally done by changing the feedwater pump speed, and we normally find a liquid water storage tank associated with the de-aerator in order to accomodate the changes in the water mass flow rate. In our case we simply need to increase the water mass flow rate from 7 kg/s to 8 kg/s in order to regain our original power output.

d) Determine the total heat transfer to the steam generator, including the reheat system [22.2 MW].

e) Determine the overall thermal efficiency of this power plant. (Thermal efficiency (η

_{th}) is defined as the net work done (turbines, pumps) divided by the total heat supplied externally to the steam generator and reheat system) [42 %].

f) Determine the heat rejected to the cooling water in the condenser [-12.9 MW].

g) Assume that all the heat rejected in the condenser is absorbed by cooling water from the Hocking River. To prevent thermal pollution the cooling water is not allowed to experience a temperature rise above 10°C. If the steam leaves the condenser as saturated liquid at 40°C, determine the required minimum volumetric flow rate of the cooling water [18.5 cubic meters/minute].

Note that it is always a good idea to validate ones calculations by evaluating the thermal efficiency using only the heat supplied to the steam generator and that rejected by the condenser.

**Discussion:** Thus we find
that the open feedwater heater did in fact raise the efficiency from
40% to 42%. This may not seem like a significant amount, however all
the basic components were already in place, since without a
**de-aerator**
the dissolved oxygen and carbon dioxide in the feedwater
will cause serious corrosion damage in the boiler. Furthermore, if
the reduction in power output is not acceptable, then it can be
easily remedied by increasing the mass flow rate in the system
design. Notice that no matter how complex the system is, we can
easily plot the entire system on a *P-h*
diagram in order to obtain an immediate intuitive
understanding and evaluation of the system performance. It is helpful
to check each value of enthalpy read or evaluated from the steam
tables and compare them to the values on the enthalpy axis of the *P-h*
diagram.

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