Following on the Second Law developed in **Chapter
5** we consider the **Clausius
Inequality** which leads to the definition
of a new property **Entropy**
(S - kJ / K) as follows:

A very strange definition indeed, and difficult to comprehend. It is defined in differential format as the reversible heat transfer divided by the temperature. In an attempt to try and understand it we rewrite the definition as follows:

It is advantageous to compare this definition with the equivalent definition of work as follows:

Thus it begins to make sense. Work done requires both
a driving force (pressure P) *and* movement (volume change **d**V).
We implicitly evaluated the work done for reversible processes -
always neglecting friction or any other irreversibility. Similarly we
can state that heat transfer requires both a driving force
(temperature T) and some equivalent form of "movement"
(entropy change **d**S). Since temperature can be considered as
represented by the vibration of the molecules, it is this transfer of
vibrational energy that we define as entropy.

We now continue with the **Increase
in Entropy Principle** which is also
derived from the Clausius Inequality, and states that for any
process, the total change in entropy of a system or control volume
together with its enclosing adiabatic surroundings is always greater
than or equal to zero. This total change of entropy is denoted the
**Entropy Generated**
during the process (S_{gen}
[kJ/K] or s_{gen}
[kJ/kg.K]. For reversible processes the entropy
generated will always be zero.

We use the differential form of the energy equation
to derive the T.**d**s
relations which can be used to **evaluate
the change of entropy** (Δs) for processes
involving 2-phase fluids (Steam, R134a, CO_{2}),
solids or liquids, or ideal gasses.

Finally we present a convenient **Entropy
Equation Summary Sheet** which summarises
the relevant relations concerning entropy generation and evaluation
of entropy change Δs. The **Isentropic
Processes Summary Sheet** extends the
relations of entropy change to enable the evaluation of isentropic
processes.

One of the important applications of isentropic
processes is in determining the efficiency of various adiabatic
components. These include turbines, compressors and aircraft jet
nozzles. Thus we have made the statement that steam turbines are
designed to be adiabatic, and that any heat loss from the turbine
will result in a reduction in output power, however only now can we
make the statement that the ideal turbine is isentropic. This enables
us to evaluate the **Adiabatic
Efficiency** (sometimes referred to as
isentropic efficiency) of these components, and we extend the
isentropic process sheet with an **Adiabatic
Efficiency Summary Sheet**.

There are two property diagrams involving entropy in
common usage, the temperature-entropy (*T-s*) and
enthalpy-entropy (*h-s*) "Mollier" diagrams. We will
find that the *h-s* diagram is extremely useful for evaluating
adiabatic turbines and compressors, and complements the *P-h*
diagram which we used in Chapter 4 to evaluate entire steam power
plants or refrigerator systems. The *h-s* diagram for steam is
presented below:

The important characteristic of the h_s diagram is that the ideal adiabatic turbine can be conveniently plotted as a vertical line, allowing an intuitive visual appreciation of the turbine performance. We define the turbine adiabatic efficiency as follows:

Notice that for the for the actual turbine there will always be an increase in entropy, which means that the turbine adiabatic efficiency will always be less than 100%.

**An Adiabatic Steam Turbine
Example**

Consider an adiabatic steam turbine having a turbine
adiabatic efficiency η_{T} = 80%, operating under the
conditions shown in the following diagram:

Using

**steam tables**, determine the enthalpy and entropy values at station (1) and station (2s) assuming that the turbine is isentropic. [h_{1}= 3479 kJ/kg, s_{1}= 7.764 kJ/kg.K; h_{2s}= 2461 kJ/kg, s_{2s}= s_{1}]From the definition of turbine adiabatic efficiency (shown on the diagram), and given that η

_{T}= 80%, determine the actual enthalpy and entropy values as well as the temperature at station (2a). [h_{2a}= 2665 kJ/kg, s_{2a}= 8.38 kJ/kg.K, T_{2a}= 88°C]Plot the actual and isentropic turbine processes (Stations (1)-(2a) and (1)-(2s)) on the enthalpy-entropy

*h-s*"Mollier" diagram, and indicate the actual turbine specific work (w_{a}) as well as the isentropic turbine specific work (w_{s}) on the diagram.Determine the actual power output of the turbine (kW). [1629 kW]

The *h-s* diagram plot follows. Notice that we
have indicated all the enthalpy and entropy values (which we
determined from the steam tables) on the plot. This allows a check on
the feasibility of our results.

We take a somewhat simpler approach for incompressible liquids, as in the following problem.

Unfortunately we find that at supercritical pressures and temperatures > 100°C, liquid water no longer behaves as an incompressible liquid, as in the following:

**Refrigerant R134a Compressors**

One of the interesting aspects of compressors is that they can be made more efficient by cooling. The reason why we still consider the adiabatic efficiency of compressors that are normally found in refrigeration, air-condition and heat pump systems is that it is considered to be impractical to cool them. Thus the ideal compressor (absorbing a minimum of power) is considered to be isentropic, and we define compressor adiabatic efficiency as follows:

We have also provided an **R134a
enthalpy-entropy (****h-s****)
diagram** which we find useful for
evaluating adiabatic compressors that are normally found in
refrigeration, air-condition and heat pump systems.

**Solved Problem 6.5 -****Adiabatic Efficiency of a R134a Compressor****Problem 6.7 -**Recall in**Chapter 4c**that we provided**Problem 4.7**concerning a home refrigerator, and examining it's performance before and after adding an internal heat exchanger.a) Plot the actual and the isentropic compressor processes on the

**enthalpy-entropy (****h-s****) diagram**provided, for both cases - with and without the internal heat exchanger.b) Using the R134a tables determine the actual compressor adiabatic efficiency (η

_{C}) for both cases [75%, 76%]

**Problem 6.8 -**Recall in**Chapter 4c**that we provided**Problem 4.9**concerning an innovative home air conditioner and hot water heating system, in which we determined the COP for both the air conditioning and the water heating systems. Do sections a) and b) specified in Problem 6.7 above on the compressor of this home air conditioning system. [η_{C}= 76%]**Problem 6.9 -****Adiabatic Efficiency of a High Pressure R134a Compressor**

We will also extend the *h-s* diagram into the
ideal gas region and use it to advantage when we consider gas turbine
and jet engine systems in Part b) that follows.

______________________________________________________________________________________

Engineering Thermodynamics by Israel
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