Vol. 4(12) ISSN © Austrian E-Journals of Universal...

International Journal of Mechatronics, Electrical and Computer Technology

Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543

http://www.aeuso.orgAvailable online at:

© Austrian E-Journals of Universal Scientif ic Organization

- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1175

Performance Evaluation of an Air-Standard Miller Cycle with

Consideration of Heat Losses

A. Mousapour 1* and M.M. Rashidi 2,3

1 Young Researchers and Elite Club, Karaj Branch, Islamic Azad University, Karaj, Iran.

2 Mechanical Engineering Department, University of Michigan-Shanghai Jiao Tong University Joint

Institute, Shanghai Jiao Tong University, Shanghai, Peoples Republic of China .

3 Mechanical Engineering Department, Engineering Faculty of Bu-Ali Sina University, Hamedan, Iran.

*Corresponding Author's E-mail: [email protected]

Abstract

There are heat losses during the cycle of an actual engine, which are neglected, in the air-

standard analysis. In this paper, performance of an air-standard Miller cycle with

consideration of heat losses is evaluated, assuming that the heat loss through the cylinder

wall only occurs during combustion and that to be proportional to the average temperature

of both the working fluid and cylinder wall. In addition, effects of various design

parameters, such as the compression ratio, the supplementary compression ratio, the initial

temperature of the working fluid and the constants related to combustion and heat transfer

through the cylinder wall on the net work output, the thermal efficiency, the maximum

work output and the corresponding compression ratio and thermal efficiency at maximum

work output are investigated. Miller cycle now is widely used in the automotive industry

and the results obtained in this paper will provide some theoretical guidance for the design

optimization of the Miller cycle.

Keywords: Air-standard cycle, Miller cycle, Combustion, Working fluid, Combustion,

Heat transfer, Compression ratio, Net work output, Thermal efficiency, Maximum work

output.

1. Introduction

The Miller cycle, named after R. H. Miller (1890 - 1967), is a modern modification of

the Atkinson cycle and has an expansion ratio greater than the compression ratio. This is

mailto:[email protected]


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1176

accomplished, however, in a much different way. Whereas an engine designed to operate

on the Atkinson cycle needed a complicated mechanical linkage system of some kind, a

Miller cycle engine uses unique valve timing to obtain the same desired results. The cycle

experienced in the cylinder of an internal combustion engine is very complex; to make the

analysis of an engine cycle much more manageable, the real cycle is approximated with an

ideal air-standard cycle, which differs from the actual by some aspects. In practice, the air-

standard analysis is quite useful for illustrating the thermodynamic aspects of an engine

operation cycle. Additionally, it can provide approximate estimates of trends as the major

engine operating variables change. For the air-standard analysis, air (as an ideal gas with

constant specific heats) is treated as the fluid flow through the entire engine, and property

values of air are used in the analysis. The real open cycle is changed into a closed cycle by

assuming that the amount of mass remains constant; combustion and exhaust strokes are

replaced with the heat addition and heat rejection processes, respectively; and actual engine

processes are approximated with ideal processes [1-4].

There are heat losses during the cycle of a real engine that strongly affect the engine

performance, but they are neglected in ideal air-standard analysis. In recent years, much

attention has been paid to effect of the heat transfer on performance of internal combustion

engines for different cycles. Klein [5] examined the effect of heat transfer through a

cylinder wall on the work outputs of the Otto and Diesel cycles. Chen et al. [6,7], Akash [8]

and Hou [9] studied the effect of heat transfer through a cylinder wall during combustion

on the net work output and the thermal efficiency of the air-standard Otto, Diesel and Dual

cycles. Hou [10] also applied to performance analysis and comparison of the air-standard

Otto and Atkinson cycles with heat transfer consideration. Ge et al. [11,12], Chen et al.

[13], Al-Sarkhi et al. [14] investigated the effects of heat transfer, friction and variable

specific heats of the working fluid on the performance of the Atkinson, Diesel, Dual and

Miller cycles, respectively. The effects of heat loss as percentage of fuel’s energy, friction

and variable specific heats of the working fluid on the performance of the Otto, Atkinson,

Miller and Diesel cycles have been analyzed by Lin and Hou [15-18]. This paper will


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1177

investigate the performance of an air-standard Miller cycle with consideration of heat

transfer through a cylinder wall during combustion.

Figure 1: The P-v and T-s diagrams for an air-standard Miller cycle.

2. Thermodynamic analysis

Since thermodynamic analysis of internal combustion engines in practical conditions is

too complicated, for this reason the real cycles are approximated with ideal air-standard

cycles by applying a number of assumptions. The P – v and the T – s diagrams of an air-

standard Miller cycle are shown in Fig. 1. It can be seen that Process 1→2 is reversible

adiabatic compression. Process 2→3 is isochoric heat addition. Process 3→4 is reversible

adiabatic expansion and processes 4→5 and 5→1 are isochoric and isobaric heat rejection,

respectively.

Assuming that the working fluid is an ideal gas with constant specific heats, the net work

output per unit mass of the working fluid of the cycle can be written in the form:

net 23 45 15 V 3 2 V 4 5 P 5 1,w q q q C T T C T T C T T (1)

where, 23q is the heat added to the working fluid per unit mass during the process 2→3.

45q and 51

q are the heats rejected by the working fluid per unit mass during the processes


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1178

4→5 and 5→1. P

C and V

C are the constant-pressure and constant-volume specific heats of

the working fluid, and 1

T , 2

T , 3

T , 4

T and 5

T are the absolute temperatures at states 1, 2, 3,

4 and 5, respectively.

Equation describing entropy change for a reversible process is, as follow:

i i

i j V

j j

ln ln .T V

s s C RT V

(2)

Using Eq. (2), for the isentropic processes (1→2) and (3→4), we will have

1

2 1 c,

kT T r

(3)

and

1

4 3 c,

kT T r r

(4)

where, k is the specific heat ratio P V,C C while

cr and r are the compression ratio

and the supplementary compression ratio, that are defined as:

1

c

2

,V

rV

(5)

and

5

1

.V

rV

(6)

Thus, for the adiabatic process (5→1) we have

5 1.T T r (7)

The heat added per unit mass of the working fluid of the cycle during the constant-

volume process (2→3) is represented by the following equation:

in 23 V 3 2.q q C T T (8)

The temperatures within the combustion chamber of an internal combustion engine reach

values on the order of 2700 (K) and up. Materials in the engine cannot tolerate this kind of

temperature and would quickly fail if proper heat transfer did not occur. Thus, because of

keeping an engine and engine lubricant from thermal failure, the interior maximum


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1179

temperature of the combustion chamber must be limited to much lower values by heat

fluxes through the cylinder wall during the combustion period. Since, during the other

processes of the operating cycle, the heat flux is essentially quite small and negligible due

to the very short time involved for the processes, it is assumed that the heat loss through the

cylinder wall occurs only during combustion. The calculation of actual heat transfer

through the cylinder wall occurring during combustion is quite complicated, so it is

approximately assumed to be proportional to the average temperature of both the working

fluid and cylinder wall and that, during the operation, the wall temperature remains

approximately invariant. The heat added per unit mass of the working fluid of the cycle by

combustion is given by the following linear relation [5]:

in 2 3,q A B T T (9)

Where, A and B are constants related to combustion and heat transfer, respectively.

Combining Eqs. (8) and (9) yields

V 2

3

V

.A C B T

TC B

(10)

Substituting Eq. (3) into Eq. (10) gives

1

V 1 c

3

V

.

kA C B T r

TC B

(11)

Substitution of Eq. (11) into Eq. (4) gives

1 1 1

c V 1

4

V

.

k k kAr r C B T r

TC B

(12)

By combining results obtained from Eqs. (3), (7), (11) and (12) into Eq. (1), the net work

output per unit mass of the working fluid of the cycle can be expressed as:

1 1 1 1

c 1 c V 1 V 1

net V P 1

V

1 21 .

k k k kA r r BT r C B T r C B T r

w C C T rC B

(13)

Similarly, by combining Eqs. (3) and (11) into Eq. (8), for the heat added per unit mass

of the working fluid of the cycle, we have


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1180

1

1 c

in V

V

2.

kA BT r

q CC B

(14)

Dividing Eq. (13) by Eq. (14) gives the indicated thermal efficiency of the cycle

1 1 1

c V 1 V 1 V 1net

th 1

in 1 c

11 .

2

k k k

k

Ar r C B T r C B T r k C B T rw

q A BT r

(15)

Maximizing the net work output with respect to compression ratio, by setting

net

c

0w

r

(16)

We finally get

1 2 2

1 c2 0.

k kAr BT r

(17)

Solving Eq. (17), gives the corresponding compression ratio at maximum work output,

cm,r so we will have

1

1 2 1

cm

1

.2

k kArr

BT

(18)

Hence, the maximum work output, max

,w and the corresponding thermal efficiency at

maximum work output, m

, can be obtained by substituting c cm

r r into Eqs. (13) and (15)

as the following equations:

1

1 121 V 1 V 1

max V P 1

V

2 2

1 ,

k kA ABT r C B T r C B T r

w C C T rC B

(19)

and


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1181

1

1 121 V 1 V 1 V 1

m 1

1 21

2 1

1 .

2

k k

k

ABT r C B T r C B T r k C B T r

A ABT r

(20)

3. Numerical calculations and results

The following constants and parameters have been used in the calculations:

2500 – 4000 ,A kJ kg 0.5 1 2 . ,. kJ kg KB min 280 3 ,20T K

P 0.972 . ,8 kJ kgC K V

0.685 . ,8 kJ kgC K 1.2 1.8.r

Substituting above constants and parameters into obtained equations and then choosing a

suitable range for the parameter c,r we can get temperature ranges of different states, the

heat added, the heat rejected, the net work output, the thermal efficiency, the maximum

work output and corresponding compression ratio and thermal efficiency at maximum work

output in the specified range.

Figs. 2–5 show the effects of parameters ,r min

,T A and B on characteristic curves of

the net work output versus the thermal efficiency, respectively. Apparently, the curves of

the net work output versus the thermal efficiency are loop-shaped except for the special

case of 1.r Note that for this value according to Eq. (7), the thermodynamic states 1 and

5 overlap and thus the Miller cycle will be converted to the Otto cycle. It can be found that

for given values of ,r min

,T A and ,B the maximum amounts of both the net work output

and the thermal efficiency do not occur at similar compression ratios. The maximum work

output and the maximum thermal efficiency increase with increasing A and decreasing

minT and .B On the other hand, with increasing ,r the maximum work output increases,

whereas the maximum thermal efficiency decreases.

Figs. 6-8 depict the influences of parameters ,r minT

and A on the maximum work

output for different values of ,B respectively. It can be seen that with increasing B that

corresponds to enlarging heat loss and thus, decreasing the net amount of heat added to the


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1182

working fluid, the maximum work output decreases. This figures also illustrate that the

maximum value of net work output increases with a rise in r and A , and a fall in min

T , for

a given .B

Figs. 9-11 indicate the effects of parameters ,r min

T and A on the corresponding

compression ratio at maximum work output for different values of ,B respectively. It is

found that an increasing in B leads to a decrease of cm

.r Furthermore, this figures reveal

that the maximum value of net work output occurs at smaller compression ratios with

increasing r and min

T , and decreasing A , for a given .B

Figs. 12-14 illustrate the effects of parameters ,r min

T and A on the corresponding

thermal efficiency at maximum work output for different values of ,B respectively.

According to these figures, the corresponding thermal efficiency at the maximum

work output increases with the increase of r and A , and the decrease of min

T and .B

0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 10

100

200

300

400

500

600

Thermal efficiency, th

Net w

ork

outp

ut, w

net

(kJ/k

g)

Tmin

= 300 [K]

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

r = 1

r = 1.2

r = 1.5

r = 1.8

Figure 2: Effect of r on curve of the net work output versus the thermal efficiency.


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1183

0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 10

100

200

300

400

500

600


Net w

ork

outp

ut, w

net

(kJ/k

g)

r = 1.5

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

Tmin

= 280 [K]

Tmin

= 300 [K]

Tmin

= 320 [K]

Figure 3: Effect of min

T on curve of the net work output versus the thermal efficiency.

0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 10

100

200

300

400

500

600

700

800

900


Net w

ork

outp

ut, w

net

(kJ/k

g)

Tmin

= 300 [K]

r = 1.5

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

A = 2500 [kJ/kg]

A = 3000 [kJ/kg]

A = 3500 [kJ/kg]

A = 4000 [kJ/kg]

Figure 4: Effect of A on curve of the net work output versus the thermal efficiency.


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1184

0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 10

200

400

600

800

1000

1200


Net w

ork

outp

ut, w

net

(kJ/k

g)

Tmin

= 300 [K]

r = 1.5

A = 3000 [kJ/kg]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

B = 0.5 [kJ/kg.K]

B = 0.7165 [kJ/kg.K]

B = 1 [kJ/kg.K]

B = 1.2 [kJ/kg.K]

Figure 5: Effect of B on curve of the net work output versus the thermal efficiency.

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

100

200

300

400

500

600

700

800

900

1000

B (kJ/kg.K)

Maxim

um

work

outp

ut, w

max

(kJ/k

g)

Tmin

= 300 [K]

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

r = 1

r = 1.2

r = 1.5

r = 1.8

Figure 6: Effect of r on curve of the maximum work output versus .B


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1185

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

100

200

300

400

500

600

700

800

900

1000

B (kJ/kg.K)

Maxim

um

work

outp

ut, w

max

(kJ/k

g)

r = 1.5

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

Tmin

= 280 [K]

Tmin

= 300 [K]

Tmin

= 320 [K]


T on curve of the maximum work output versus .B

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

200

400

600

800

1000

1200

1400

1600

B (kJ/kg.K)

Maxim

um

work

outp

ut, w

max

(kJ/k

g)

Tmin

= 300 [K]

r = 1.5

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

A = 2500 [kJ/kg]

A = 3000 [kJ/kg]

A = 3500 [kJ/kg]

A = 4000 [kJ/kg]

Figure 8: Effect of A on curve of the maximum work output versus .B


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1186

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

5

10

15

20

25

30

B (kJ/kg.K)

Com

pre

ssio

n r

atio

at m

axim

um

work

outp

ut, r

cm

Tmin

= 300 [K]

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

r = 1

r = 1.2

r = 1.5

r = 1.8

Figure 9: Effect of r on curve of the compression ratio at maximum work output versus .B

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

5

10

15

20

25

30

B (kJ/kg.K)

Com

pre

ssio

n r

atio

at m

axim

um

work

outp

ut, r

cm

r = 1.5

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

Tmin

= 280 [K]

Tmin

= 300 [K]

Tmin

= 320 [K]


T on curve of the compression ratio at maximum work output versus .B


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1187

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

5

10

15

20

25

30

B (kJ/kg.K)

Com

pre

ssio

n r

atio

at m

axim

um

work

outp

ut, r

cm

Tmin

= 300 [K]

r = 1.5

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

A = 2500 [kJ/kg]

A = 3000 [kJ/kg]

A = 3500 [kJ/kg]

A = 4000 [kJ/kg]

Figure 11: Effect of A on curve of the compression ratio at maximum work output versus .B

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

0.1

0.2

0.3

0.4

0.5

0.6

0.7

0.8

0.9

1

B (kJ/kg.K)

Therm

al e

ffic

iency a

t m

axim

um

work

outp

ut,

m

Tmin

= 300 [K]

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

r = 1

r = 1.2

r = 1.5

r = 1.8

Figure 12: Effect of r on curve of the thermal efficiency at maximum work output versus .B


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1188

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

0.1

0.2

0.3

0.4

0.5

0.6

0.7

0.8

0.9

1

B (kJ/kg.K)

Therm

al e

ffic

iency a

t m

axim

um

work

outp

ut,

m

r = 1.5

A = 3000 [kJ/kg]

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

Tmin

= 280 [K]

Tmin

= 300 [K]

Tmin

= 320 [K]


T on curve of the thermal efficiency at maximum work output versus .B

0.5 0.6 0.7 0.8 0.9 1 1.1 1.20

0.1

0.2

0.3

0.4

0.5

0.6

0.7

0.8

0.9

1

B (kJ/kg.K)

Therm

al e

ffic

iency a

t m

axim

um

work

outp

ut,

m

Tmin

= 300 [K]

r = 1.5

B = 1 [kJ/kg.K]

Cp = 0.9728 [kJ/kg.K]

Cv = 0.6858 [kJ/kg.K]

A = 2500 [kJ/kg]

A = 3000 [kJ/kg]

A = 3500 [kJ/kg]

A = 4000 [kJ/kg]

Figure 14: Effect of A on curve of the thermal efficiency at maximum work output versus .B


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1189

Conclusions

In this manuscript, the performance of an air-standard Miller cycle with consideration of

losses due to heat transfer through the cylinder wall during combustion has been

investigated. In addition, the influences of some relevant design parameters such as the

compression ratio, supplementary compression ratio, the initial temperature of the working

fluid and the combustion and heat transfer constants on the net work output, the thermal

efficiency, the maximum work output, the corresponding compression ratio at maximum

work output and the corresponding thermal efficiency at maximum work output has been

discussed, numerically. The obtained results show that the effects of these parameters on

the performance of the Miller cycle are non-negligible and should be considered in

practical Miller engines.

References

[1] W. W. Pulkrabek, Engineering fundamentals of the internal combustion engine, Prentice-Hall, New

Jersey (1997).

[2] J. B. Heywood, Internal combustion engine fundamentals, McGraw-Hill, New York (1988).

[3] Y. A. Cengel, M. A. Boles, Thermodynamics: an engineering approach, 7th Ed, McGraw-Hill Book

Company, (2010).

[4] A. Bejan, Advanced engineering thermodynamics, Hoboken, John Wiley & Sons INC, New Jersey

(2006).

[5] S. A. Klein. An explanation for observed compression ratios in internal combustion engines. Journal of

Engineering for Gas Turbines and Power, 113( 4), (1991), pp. 511-513.

[6] L. Chen, C. Wu, F. Sun, S. Cao. Heat transfer effects on the net work output and efficiency

characteristics for an air standard Otto cycle. Energy Conversion and Management, 39(7), (1998), pp.

643-648.

[7] L. Chen, F. Zeng, F. Sun, C. Wu. Heat transfer effects on net work and/or power as functions of

efficiency for air standard Diesel cycles. Energy, 21(12), (1996), pp. 1201-1205.

[8] B. Akash. Effect of heat transfer on the performance of an air standard Diesel cycle. International

Communication in Heat and Mass Transfer, 28(1), (2001), pp. 87-95.

[9] S. S. Hou. Heat transfer effects on the performance of an air standard dual cycle. Energy Conversion

and Management, 45(18/19), (2004), pp. 3003-3015.


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1190

[10] S. S. Hou. Comparison of performances of air standard Atkinson and Otto cycles with heat transfer

considerations. Energy Conversion and Management, 48(5), (2007), pp. 1683-1690.

[11] Y. Ge, L. Chen, F. Sun, C. Wu. Performance of an Atkinson cycle with heat transfer, friction and

variable specific heats of the working fluid. Applied Energy, 83(11), (2006), pp. 1210-1221.

[12] Y. Ge, L. Chen, F. Sun, C. Wu. Performance of a Diesel cycle with heat transfer, friction and variable

specific heats of the working fluid. Journal of the Energy Institute, 80(4), (2007), pp. 239-242.

[13] L. Chen, Y. Ge, F. Sun, C. Wu. Effects of heat transfer, friction and variable specific heats of working

fluid on performance of an irreversible Dual cycle. Energy Conversion and Management, 47(18/19),

(2006), pp. 3224-3234.

[14] A. Al-Sarkhi, J. O. Jabber, S. D. Probert. Efficiency of a Miller engine. Applied Energy, 83(4), (2006),

pp. 343-351.

[15] J. C. Lin, S. S. Hou. Effects of heat loss as percentage of fuel’s energy, friction and variable specific

heats of working fluid on performance of air standard Otto cycle. Energy Conversion and

Management, 49(5), (2008), pp. 1218-1227.

[16] J. C. Lin, S. S. Hou. Influence of heat loss on the performance of an air standard Atkinson cycle.

Applied Energy, 84(9), (2007), pp. 904-920.

[17] J. C. Lin, S. S. Hou. Performance analysis of an air standard Miller cycle with considerations of heat

loss as a percentage of fuel’s energy, friction and variable specific heats of working fluid. International

journal of Thermal Sciences, 47(2), (2008), pp. 182-191.

[18] S. S. Hou, J. C. Lin. Performance analysis of a Diesel cycle under the restriction of maximum cycle

temperature with considerations of heat loss, friction and variable specific heats. Academic journal of

Acta Physica Polonica, 120(6), (2011), pp. 979-986.


Vol. 4(12), Jul, 2014, pp. 1175-1191, ISSN: 2305-0543



- - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1191

Authors

Ashkan Mousapour (A. Mousapour) is born in Ahvaz, Iran in 1987. He received his B.Sc. degree in

Mechanical Engineering from Is lamic Azad University of Karaj and received his M .Sc. degree in

Mechanical Engineering from Science and Research Branch of Islamic Az ad Univers ity. His current

research interest includes T hermodynamics and Energy . He published 2 journal papers (both are in

Scopus). He is a member of Young Researchers and Elite Club of Karaj Branch, Is lamic Az ad

University, Karaj, Iran. E-mail: [email protected]

Mohammad Mehdi Rashi di (M.M. Rashi di) is born in Hamedan, Iran in 1972. He received his B.Sc.

degree in Bu-Ali Sina Univers ity, Hamedan, Iran in 1995. He also received his M.Sc. and Ph.D.

degrees from T arbiat Modares Univers ity, Tehran, Iran in 1997 and 2002, respect ively. His research

focuses on Heat and Mass T ransfer, Thermodynamics, Comput ational F luid Dynamics (CFD),

Nonlinear Analysis, Engineering Mathemat ics, Exergy and Second Law Analysis, Numerical and

Experiment al Invest igations of Nanofluids F low for Increasing Heat Transfer and Study of

Magnetohydrodynamic Viscous F low. He is a professor (full) of Mechanical Engineering at the Bu -Ali

Sina University, Hamedan, Iran. Now He is working on some research projects at univers ity of

Michigan-Shanghai Jiao Tong university, Joint Inst itute. His works have been published in the journal

of Energy , Computers and Fluids, Communicat ions in Nonlinear Science and Numerical Simulation

and several other peer-reviewed int ernat ional journals . He has published two books : Advanced

Engineering Mathematics with Applied Examples of MATHEMATICA Software (2007) (320 pages) (in

Pers ian), and Mathemat ical Modelling of Nonlinear F lows of Micropolar Fluids (Germany, Lambert

Academic Press , 2011). He has published over 165 (100 of them are in Scopus) journal art icles and 43

conference p apers . Dr. Rashidi is a reviewer of several journals (over 110 refereed journals) such as

Applied Mathemat ical Modelling, Computers and Fluids , Energy, Computers and Mathemat ics with

Applications , International Journal of Heat and Mass Transfer, International journal of thermal science,

Mathemat ical and Computer Modelling, etc. He was an invit ed professor in Génie Mécanique,

Univers ité de Sherbrooke, Sherbrooke, QC, Canada J1K 2R (From Sep 2010 -Feb 2012), Univers ité

Paris Ouest, France (For Sep 2011) and Univers ity of the Witwat ers rand, Johannesburg, South Africa

(For Aug 2012). He is the editor of Forty four (44) Int ernat ional Journals, some of them are as follow:

Caspian Journal of Applied Sciences Research (ISI), Associate Editor of Journal of King Saud

Univers ity-Engineering Sciences (Elsevier), Scientific Research and Essays (indexed in SCOPUS),

Walailak Journal of Science and T echnology (indexed in SCOPUS) and Modern Applied Science

(indexed in SCOPUS).

E-mail: [email protected], [email protected]


http://www.nes.ru/en/science/intmag/

http://www.google.com.hk/url?sa=t&rct=j&q=caspian%20journal%20of%20applied%20science%20research&source=web&cd=1&ved=0CCoQFjAA&url=%68%74%74%70%3a%2f%2f%77%77%77%2e%63%6a%61%73%72%2e%63%6f%6d%2f&ei=4mM0Up-3CYbfkgWrhIHgDQ&usg=AFQjCNH4nvR8MyNdeTOP41Ccyoepr7MEYg&bvm=bv.52164340,d.dGI&cad=rjt



Vol. 4(12) ISSN © Austrian E-Journals of Universal...

Documents

Transcript of Vol. 4(12) ISSN © Austrian E-Journals of Universal...