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1. CHAPTER
5
MEC 451
Thermodynamics
Air Standard
Cycle
Lecture Notes:
MOHD HAFIZ MOHD NOH
HAZRAN HUSAIN & MOHD
SUHAIRIL
Faculty of Mechanical Engineering
Universiti Teknologi MARA, 40450
Shah Alam, Selangor
For students EM 220 and EM 221 only

2. ηth
net
in
W
Q
=
ηth Carnot
L
H
T
T
, = −
1
Upon derivation the performance of the real cycle is often
measured in terms of its thermal efficiency
The Carnot cycle was introduced as the most efficient heat
engine that operate between two fixed temperatures TH and TL.
The thermal efficiency of Carnot cycle is given by
Review – Carnot Cycle
2

3. The ideal gas equation is defined as
mRT
PV
or
RT
Pv =
=
where P = pressure in kPa
v = specific volume in m3
/kg (or V = volume in
m3
)
R = ideal gas constant in kJ/kg.K
m = mass in kg
T = temperature in K
Review – Ideal Gas Law
3 3

4. The Δu and Δh of ideal gases can be expressed as
)
( 1
2
1
2 T
T
C
u
u
u v −
=
−
=
∆
)
( 1
2
1
2 T
T
C
h
h
h P −
=
−
=
∆
Δu - constant volume process
Δh - constant pressure process
4

5. Process Description Result of IGL
isochoric constant volume (V1
= V2
)
isobaric
constant pressure (P1
=
P2
)
isothermal
constant temperature
(T1
= T2
)
polytropic -none-
isentropic constant entropy (S1
= S2
)
 According to a law of constant
=
n
V
P
2
2
1
1
T
P
T
P
=
2
2
1
1
T
V
T
V
=
2
2
1
1 V
P
V
P =
1
2
1
1
2
2
1
−








=








=
n
n
n
T
T
V
V
P
P
Review – Thermodynamics Processes
5

6. R = 0.2871 kJ/kg.K
Cp = 1.005 kJ/kg.K
Cv = 0.718 kJ/kg.K
k = 1.4
where R = ideal gas constant
Cp = specific heat at constant pressure
Cv = specific heat at constant volume
k = specific heat ratio
Review – Properties of Air
6

7.  IC Engine – combustion of fuel takes place inside an engine’s
cylinder.
Introduction
7

8.  Air continuously circulates in a closed loop.
 Always behaves as an ideal gas.
 All the processes that make up the cycle are internally
reversible.
 The combustion process is replaced by a heat-addition
process from an external source.
Air-Standard Assumptions
8

9.  A heat rejection process that restores the working fluid to
its initial state replaces the exhaust process.
 The cold-air-standard assumptions apply when the
working fluid is air and has constant specific heat
evaluated at room temperature (25o
C or 77o
F).
 No chemical reaction takes place in the engine.
Air-Standard Assumptions
9

10.  Top dead center (TDC), bottom dead center (BDC), stroke,
bore, intake valve, exhaust valve, clearance volume,
displacement volume, compression ratio, and mean
effective pressure
Terminology for Reciprocating Devices
10

11.  The compression ratio r of an
engine is defined as
r
V
V
V
V
BDC
TDC
= =
max
min
 The mean effective pressure
(MEP) is a fictitious pressure
that, if it operated on the piston
during the entire power stroke,
would produce the same
amount of net work as that
produced during the actual
cycle.
MEP
W
V V
w
v v
net net
=
−
=
−
max min max min11

12. Otto Cycle
The Ideal Cycle for Spark-Ignition Engines
12

13.  The processes in the Otto cycle are as per following:
Process Description
1-2 Isentropic compression
2-3 Constant volume heat addition
3-4 Isentropic expansion
4-1 Constant volume heat rejection
13

14.  Related formula based on basic thermodynamics:
1
2
1
1
2
2
1
−








=








=
n
n
n
T
T
V
V
P
P
1
2
1
1
2
2
1
−








=








=
n
n
n
T
T
V
V
P
P
( )
3 2
in v
Q mC T T
= −
( )
4 1
out v
Q mC T T
= −
14

15.  Thermal efficiency of the Otto cycle:
ηth
net
in
net
in
in out
in
out
in
W
Q
Q
Q
Q Q
Q
Q
Q
= = =
−
= −
1
 Apply first law closed system to process 2-3, V = constant.
 Thus, for constant specific heats
Q U
Q Q mC T T
net
net in v
,
, ( )
23 23
23 3 2
=
= = −
∆
,23 ,23 23
3
,23 ,23 ,23
2
0 0
net net
net other b
Q W U
W W W PdV
− = ∆
= + = + =
∫
15

16.  Apply first law closed system to process 4-1, V = constant.
 Thus, for constant specific heats,
Q U
Q Q mC T T
Q mC T T mC T T
net
net out v
out v v
,
, ( )
( ) ( )
41 41
41 1 4
1 4 4 1
=
= − = −
= − − = −
∆
 The thermal efficiency becomes
ηth Otto
out
in
v
v
Q
Q
mC T T
mC T T
,
( )
( )
= −
= −
−
−
1
1 4 1
3 2
,41 ,41 41
1
,41 ,41 ,41
4
0 0
net net
net other b
Q W U
W W W PdV
− = ∆
= + = + =
∫
16

17. ηth Otto
T T
T T
T T T
T T T
,
( )
( )
( / )
( / )
= −
−
−
= −
−
−
1
1
1
1
4 1
3 2
1 4 1
2 3 2
 Recall processes 1-2 and 3-4 are isentropic, so
 Since V3 = V2 and V4 = V1,
3 3
2 4
1 4 1 2
T T
T T
or
T T T T
= =
1
1
3
2 1 4
1 2 4 3
k
k
T
T V V
and
T V T V
−
−
 
 
= =  ÷
 ÷
   
17

18.  The Otto cycle efficiency becomes
ηth Otto
T
T
, = −
1 1
2
 Since process 1-2 is isentropic,
 where the compression ratio is
r = V1/V2 and
ηth Otto k
r
, = − −
1
1
1
1
2 1
1 2
1 1
1 2
2 1
1
k
k k
T V
T V
T V
T V r
−
− −
 
=  ÷
 
   
= =
 ÷  ÷
 
 
18

19. An Otto cycle having a compression ratio of 9:1 uses air as the
working fluid. Initially P1 = 95 kPa, T1 = 17°C, and V1 = 3.8
liters. During the heat addition process, 7.5 kJ of heat are
added. Determine all T's, P's, ηth, the back work ratio and the
mean effective pressure.
Example 5.1
Solution:
Data given:
1
1
2
23
1
1
290
9
7.5
95
3.8
T K
V
V
Q kJ
P kPa
V Litres
=
=
=
=
=
19

20. Example 5.1
( )
( )
( )
( )
1
0.4
2 1
2
1 2
1
1.4
2 1
2
1 2
290 9 698.4
95 9
Pr 1 2
Pr 2 3 .
2059
1 :
k
k
st
net net
T V
T K
T V
P V
P kPa
P V
law Q W
ocess isentropiccompression
ocess Const volumeheat addition
−
−
 
= ⇒ = =
 ÷
 
 
−
−
= ⇒ = =
 ÷
 
−
( )
( ) 3
0
23 3 2
1 1 1 1
23 1
23 23
1
0.2871 290
: 0.875
95
1727
v
m
kg
kJ
kg
U
Q mC T T
IGL Pv RT v
Q v
q Q
m V
= ∆
= −
= ⇒ = =
= = =
20

21. Example 5.1
( )
( )
( )
( )
( )
3 2
3 2
23 3 2
3 2
3 3
3
1
0.4
3
4
4 3
3 4
1.4
3
4
4 3
3 4
:
0.718 698.4 9.15
3103.7
1/ 9 1288.8
1/ 9 422
Pr 3 4 exp
v
k
k
ocess isentr
Back to IGL ButV V
P P
q C T T
T T
T P MPa
T K
V
T
T T
opic ansi
K
T V
V
P
P P kPa
P
on
V
−
=
= − =
= − =
=
 
= ⇒ = =
 ÷
 
 
= ⇒ = =
 ÷
 
−
21

22. Example 5.1
( )
( )
( )
( )
41 4 1
41 4 1
0.718 1288.8 290
717.
Pr 4 1 .
1
v
v
kJ
kg
Q mC T
ocess Const volumeheat rejec
T
q C T
tion
T
= −
=
−
−
= −
=
Then:
( )
23 41
,
1009.6
0.585 58.5%
net in out
kJ
kg
net
th Otto
in
W q q
q q
W
q
η
= −
= −
=
= =
22

23. Example 5.1
What else?
( )
( ) ( )
max min max min
1 2 1 2 1
1
1
12
exp 34
1 /
1009.6
1298
1 0.875 1 1/ 9
net net
net net
net
r
v
compr
bw
ans
W w
MEP
V V v v
w w
v v v v v
w
kPa
v
C
w u
r
w u
= =
− −
= =
− −
= = =
− −
∆
= = =
−∆
( )
2 1
v
T T
C
−
( )
( )
3 4
0.225 22.5%
T T
−
=
23

24. Supplementary Problems 5.1
1. An ideal Otto cycle has a compression ratio of 8. At the beginning of
the compression process, air is at 95 kPa and 27°C, and 750 kJ/kg
of heat is transferred to air during the constant-volume heat-
addition process. Taking into account the variation of specific heats
with temperature, determine (a) the pressure and temperature at
the end of the heat addition process, (b) the net work output, (c) the
thermal efficiency, and (d) the mean effective pressure for the cycle.
[(a) 3898 kPa, 1539 K, (b) 392.4 kJ/kg, (c) 52.3 percent,(d ) 495 kPa]
2. The compression ratio of an air-standard Otto cycle is 9.5. Prior to
the isentropic compression process, the air is at 100 kPa, 35°C, and
600 cm3
. The temperature at the end of the isentropic expansion
process is 800 K. Using specific heat values at room temperature,
determine (a) the highest temperature and pressure in the cycle; (b)
the amount of heat transferred in, in kJ; (c) the thermal efficiency;
and (d) the mean effective pressure.
[(a) 1969 K, 6072 kPa,(b) 0.59 kJ, (c) 59.4 percent, (d) 652 kPa]
24

25.  The processes in the Diesel cycle are as per following:
Diesel Cycle
25

26. c
v r
ratio
off
Cut
v
v
and
r
ratio
n
Compressio
v
v
,
,
2
3
2
1
−
=
=
Diesel Cycle
26

27.  Related formula based on basic thermodynamics:
1
2
1
1
2
2
1
−








=








=
n
n
n
T
T
V
V
P
P
1
2
1
1
2
2
1
−








=








=
n
n
n
T
T
V
V
P
P
( )
3 2
in P
Q mC T T
= −
( )
4 1
out v
Q mC T T
= −
27

28.  Thermal efficiency of the Diesel cycle
ηth Diesel
net
in
out
in
W
Q
Q
Q
, = = −
1
 Apply the first law closed system to process 2-3, P = constant.
 Thus, for constant specific heats
Q U P V V
Q Q mC T T mR T T
Q mC T T
net
net in v
in p
,
,
( )
( ) ( )
( )
23 23 2 3 2
23 3 2 3 2
3 2
= + −
= = − + −
= −
∆
( )
,23 ,23 23
3
,23 ,23 ,23
2
2 3 2
0 0
net net
net other b
Q W U
W W W PdV
P V V
− = ∆
= + = + =
= −
∫
28

29.  Apply the first law closed system to process 4-1, V = constant
Q U
Q Q mC T T
Q mC T T mC T T
net
net out v
out v v
,
, ( )
( ) ( )
41 41
41 1 4
1 4 4 1
=
= − = −
= − − = −
∆
 Thus, for constant specific heats
 The thermal efficiency becomes
ηth Diesel
out
in
v
p
Q
Q
mC T T
mC T T
,
( )
( )
= −
= −
−
−
1
1 4 1
3 2
,41 ,41 41
1
,41 ,41 ,41
4
0 0
net net
net other b
Q W U
W W W PdV
− = ∆
= + = + =
∫
29

30. PV
T
PV
T
V V
T
T
P
P
4 4
4
1 1
1
4 1
4
1
4
1
= =
=
where
 Recall processes 1-2 and 3-4 are isentropic, so
PV PV PV PV
k k k k
1 1 2 2 4 4 3 3
= =
and
 Since V4 = V1 and P3 = P2, we divide the second equation by
the first equation and obtain
 Therefore,
3
4
4 2
k
k
c
V
P
r
T V
 
= =
 ÷
 
( )
, 1
1
1
1
1
k
c
th Diesel k
c
r
r k r
η −
−
= −
−
30

31. An air-standard Diesel cycle has a compression ratio of 18 and
a cut-off ratio of 2.5. The state at the beginning of compression
is fixed by P = 0.9 bar ant T = 300K. Calculate:
i. the thermal efficiency of the cycle,
ii. the maximum pressure, Pmax, and
iii. The mean effective pressure.
Example 5.2
Solution:
Data given:
1
2
3
2
18
2.5
V
V
V
V
=
=
31

32. Example 5.2
( )
( )
( )
( )
( )
1
0.4
2 1
2
1 2
3 3
2
2 3 3 2
2 3 2
4 1 2
3 2 3
4
Pr 1 2
Pr 2 3
300 18 953.3
2383.
.
Pr 3 4 exp
3
. 18 1/ 2.5 7.2
k
ocess isentropiccompression
ocess Const pressureheat addition
ocess isentropic ansio
T V
T K
T V
V V
V
P P T T K
T T V
V V V
V V V
T
n
−
 
= ⇒ = =
 ÷
 
 
= ⇒ = ⇒ = =
 ÷
 
= = =
−
−
−
( )
1
0.4
3
4
3 4
2383.3 1/ 7.2 1082
k
V
T K
T V
−
 
= ⇒ = =
 ÷
  32

33. Example 5.2
( ) ( )
( ) ( )
23 3 2 3 2
41 4 1 4 1
1437.15
561.48
875.67
kJ
in P in p kg
kJ
out P out p kg
kJ
net in out kg
Q Q mC T T q C T T
Q Q mC T T q C T T
w q q
= = − ⇒ = − =
= = − ⇒ = − =
= − =
What we need?
( ) ( )
( )
( )
( )
( ) ( )
,
max 2 3
1
2 2
2 max
1 1
1
0.6093 60.93%
5148
875.67
969.1
1 1/ 0.9566 1 1/18
net
th diesel
in
k
k
net
w
i
q
ii P P P
P T
P kPa P
P T
w
iii MEP kPa
V r
η
−
= =
= =
   
= ⇒ =
 ÷  ÷
   
= = =
− −
33

34. Supplementary Problems 5.2
1. An ideal diesel engine has a compression ratio of 20 and uses air as
the working fluid. The state of air at the beginning of the
compression process is 95 kPa and 20°C. If the maximum
temperature in the cycle is not to exceed 2200 K, determine (a) the
thermal efficiency and (b) the mean effective pressure. Assume
constant specific heats for air at room temperature.
[ (a) 63.5 percent, (b) 933 kPa]
2. An ideal diesel cycle has a compression ratio of 16 to 1. The
maximum cycle temperature is 1700°C and the minimum cycle
temperature is 15°C. Calculate:
i. the specific heat transfer to the cycle
ii. the specific work of the cycle
iii. the thermal efficiency of the cycle
34

35.  Dual cycle gives a better approximation to a real engine. The
heat addition process is partly done at a constant volume and
partly at constant pressure. From the P-v diagram, it looks like
the heat addition process is a combination of both Otto and
Diesel cycles.
Dual Cycle
35

36.  The same procedure as to Otto and Diesel cycles can be applied to
Dual cycle. Upon substitutions, the thermal efficiency of Dual
cycle becomes
( ) ( )
[ ] 1
1
1
1
1 −
−
+
−
−
−
= k
v
c
p
p
k
c
p
th
r
r
c
k
r
r
r
η
Dual Cycle
36

37. At the beginning of the compression process of an air-standard
dual cycle with a compression ratio of 18, the temperature is
300 K and the pressure is 1 bar. The pressure ratio for the
constant volume part of the heating process is 1.5 to 1. The
volume ratio for the constant pressure part of the heating
process is 1.2 to 1. Determine (a) the thermal efficiency and (b)
the mean effective pressure. (WRONG SOLUTION!!)
Example 5.3
Solution:
1 1
2 2
4
1
3
1
18 1.5
300 1.2
1
V P
V P
V
T K
V
P bar
= =
= =
=
Data given:
37

38. ( )
( )
( )
( )
( )
1
0.4
2 1
2
1 2
3 3
2
2 3 3 2
2 3 2
4 1 2
3 2 3
4
Pr 1 2
Pr 2 3
300 18 953.3
2383.
.
Pr 3 4 exp
3
. 18 1/ 2.5 7.2
k
ocess isentropiccompression
ocess Const pressureheat addition
ocess isentropic ansio
T V
T K
T V
V V
V
P P T T K
T T V
V V V
V V V
T
n
−
 
= ⇒ = =
 ÷
 
 
= ⇒ = ⇒ = =
 ÷
 
= = =
−
−
−
( )
1
0.4
3
4
3 4
2383.3 1/ 7.2 1082
k
V
T K
T V
−
 
= ⇒ = =
 ÷
  38

39. ( )
( ) ( )
1
1 1
5 3
4 4 4
5 4 4
4 5 5 3 5
0.4
1
18
1715.94 1.2
5
Pr 4 5
84.85
exp
k
k k
ocess isentropic ansio
T V
V V V
T T T
V
n
T V V V
K
−
− −
 
      
= ⇒ = =  
 ÷  ÷  ÷ ÷
 
      
 
 
=  
=
−
Information needed?
( )
( ) ( )
51 5 1
23 34 3 2 4 3
204.52
629.65
kJ
out v kg
in v p
kJ
kg
Q Q C T T
Q Q Q C T T C T T
m
m m
= = − =
= + = − + −
=
39

40. Answer the questions ?
( ) ( )
( )
( )
( )
1
1
1
18
204.52
1 1 0.675 67.5%
629.65
1
425.13
0.8613 1
522.63
net in out out
th
in in in
net
r
W Q Q Q
a
Q Q Q
W
b MEP
v
kPa
η
−
= = = − = − =
=
−
=
−
=
40

41.  Indicated power (IP)
 Brake power (bp)
 Friction power (fp) and mechanical efficiency, ηm
 Brake mean effective pressure (bmep), thermal
efficiency and fuel consumption
 Volumetric efficiency, ηv
Criteria of Performance
41

42.  Defined as the rate of work done by the gas on the
piston as evaluated from an indicator diagram obtained
from the engine using the electronic engine indicator.
2
LANn
p
IP i
=
 For four-stroke engine,
 And for two-stroke engine,
LANn
p
IP i
=
Indicated Power
42
ip = work done per cycle × cycle per minute
n is the number of cylinders.

43. Indicated Power
43
constant
diagram
of
length
diagram
of
area
net
×
=
i
p
 Indicated mean effective pressure, pi given by:,
 For one engine cylinder
Work done per cycle = pi × A
× L
Where A = area of piston
L = length of stroke
time
unit
per
cycle
AL
P
ip i ×
=
 Power output = (work done per cycle) x (cycle per
minute)
 For four-stoke engines, the number of cycles per unit time
is N/2 and for two-stroke engines the number of cycles per
unit time is N, where N is the engine speed.
volume
nt
displaceme
cycle
per
done
work
=
i
p

44.  Brake power is a way to measure the engine power output.
 The engine is connected to a brake (or dynamometer) which
can be loaded so that the torque exerted by the engine can
be measured.
 The torque is obtained by reading off a net load, w at known
radius, r.
Wr
=
τ
Brake Power
44

45.  Therefore
τ
πN
bp 2
=
2
2
LANn
P
LANn
p
IP
bp b
i
m
m =
=
=
η
η
 Brake power is also can be expressed as
 Then the brake mean effective pressure (Pb) is
i
m
b P
P η
=
45

46. Friction Power
46
The difference between the Ip and bp is the friction power
(fp). It is the power that overcome the frictional resistance
of the engine parts.
bp
IP
fp −
=

47.  Power input to the shaft is usually bigger than the
indicated power due to frictional losses or the
mechanical efficiency.
power
indicated
power
brake
mech =
η
Mechanical Efficiency
47

48. Brake Mean Effective Pressure
48
 From the definition of Brake power IP
BP m
η
=
 Since
2
LANn
p
IP i
= for 4 stroke engine
and 2
2
LANn
P
LANn
p
bp b
i
m
=
=
η
 Since and Pi are difficult to obtain, they may be combined and
replaced by a brake mean effective pressure, Pb
m
η
m
η
 Equating this equation to another definition of bp: NT
LANn
Pb
η
2
2
=
T
LAn
Pb
η
4
=
 So:
 Its observed that bmep is proportional to torque.

49. Brake Thermal Efficiency
49
 The power output of the engine is obtained from the chemical energy of
the fuel supplied. The overall engine efficiency is given by the brake
thermal efficiency,
m
η
v
net
f
p
fe
p
bp
Q
m
b
P
b
,
power
equivalent
fuel
power
brake
given
power
power
brake
=
=
=
=
η
 mf = mass flow fuel , Qnet,v = net calarofic value of the fuel.

50.  sfc is the mass flow rate of fuel consumed per unit power
output and is a criterion of economical power production.
bp
m
sfc
f

=
Specific Fuel Consumption
50

51.  Volumetric efficiency is only used with four-stroke cycle
engine, which have a distinct induction process.
 The parameter used to measure the effectiveness of an
engine’s induction process is the volumetric efficiency.
s
V
V
V
=
η
Volumetric Efficiency
51

52. An engine operating at 2400 rpm consumes 12 ml of fuel (s.g. 0.85) in
60 second. The engine indicates a load of 30 N on the pony brake
system and the brake’s torque arm is 20 cm. Determine (a) the brake
power, (b) the mass flow rate of fuel, and (c) the specific fuel
consumption.
Example 5.4
Solution:
52

53. A four-cylinder petrol engine has a bore of 57 mm and a stroke of 90
mm. Its rated speed is 2800 rpm and it is tested at this speed against a
brake which has a torque arm of 0.356 m. The net brake load is 155 N
and the fuel consumption is 6.741 l/h. The specific gravity of the petrol
used is 0.735 and it has a net calorific value of 44,200 kJ/kg. The
engine is tested in an atmospheric condition at 101.325 kPa and 15 oC
at air-fuel ratio of 14.5/1. Calculate for this speed, the engine torque,
the bmep, the brake thermal efficiency, the specific fuel consumption
and the volumetric efficiency of the engine.
Example 5.4
Solution:
53

54. 2
LANn
p
IP i
=
τ
πN
bp 2
=
Real Case
54