ＯＴＥＣ
Vol. 22 (2017)，65〜75

Performance Evaluation of Heat Exchangers for Application
to Ocean Thermal Energy Conversion System

Performance Evaluation of Heat Exchangers for Application
to Ocean Thermal Energy Conversion System
Takeshi YASUNAGA*1, Kevin FONTAINE*2,3, Takafumi MORISAKI*1 and Yasuyuki IKEGAMI*1*1 Institute of Ocean Energy, Saga University
1-honjo, Saga-shi, Saga, 840-8502, Japan*2 Master of Physics, Phelma graduate school of Engineering
3 Parvis Louis Neel – CS 50257, 38016 Grenoble Cedex 01, France*3 EPF, graduate school of Engineering
3 bis Rue Lakanal, 92330 Sceaux, France

Abstract
Ocean thermal energy conversion (OTEC) is a system to convert the ocean thermal energy, which is stored
as the vertical temperature gradient in the ocean, into the electricity and the heat exchanger performance issignificantly important. Theoretical maximum power output and the relationship between heat exchanger
performances have been formulated in finite-time thermodynamics. And considering the seawater intake
pumping powers in OTEC system, the thermal efficiency in case of the maximum net power has shown by
introducing the ideal heat exchanges from heat source to heat engine. Considering the OTEC system without
seawater intake system, the required pumping power of surface and deep seawaters will be the same magnitude
of power as the generated power in the heat engine, and they might be able to get over the generated power due
to the balance of the heat transfer performance and pressure drop in the heat exchangers. For each heatexchangers, heat transfer performance and pressure drop can be measured and summarized. However, for theapplication of the OTEC as an evaporator and a condenser, the effect of both characteristics on the net power in
OTEC are same magnitude and very important. Therefore, the total performance evaluation method of heatexchangers is required for the selection and design of the heat exchangers as well as the development of the heatexchanger performance. This study describes about the theoretical relationship between heat transfer
performance of heat exchangers including pressure drop and power output from the heat engine and shows theresults of the comparison of the available power output from the power generation system using existing 3 plate
heat exchangers (PHEs).
Key words : OTEC, Heat Exchanger Performance index, Maximum Power, Optimization Method, Optimum
Function, Power output maximization, Plate heat exchanger

1. Introduction

Ocean thermal energy conversion (OTEC) is a system to convert the ocean thermal energy, which is stored as thevertical temperature gradient in the ocean, into the electricity. Thermal efficiency of OTEC is theoretically low due toquite low available temperature difference between heat sources, and thus, an abundant heat source quantity is requiredcompared to conventional power plants. In closed cycle OTEC system, the heat exchangers are applied as an evaporator
and a condenser to transfer the thermal energy between the heat sources and the engine (Uehara, 1982, Avery and Wu,
1994). In general, since the system uses the thermal energy stored as the sensible heat of seawater, harnessing the thermalenergy from heat source yields the change of the heat source temperature, this temperature change causes the reductionof the available temperature difference for the heat engine, which declines the thermal efficiency of heat engine, thentheoretical maximum power output is formulated in finite-time thermodynamics (Ibrahim, 1992 and Bejan, 1998)..
Ikegami and Bejan (1998) consider the seawater intake pumping powers in OTEC system by using the ideal heat engine,
Date of Manuscript Acceptance: 2017. 8.10
E-mail of corresponding author: yasunaga@ioes.saga-u.ac.jp

*

65

66

Takeshi YASUNAGA, Kevin FONTAINE, Takafumi MORISAKI and Yasuyuki IKEGAMI

2. Nomenclature

A : heat transfer area (m2)
BWR: backwork ratio (-)
C : heat capacity flow rate (W/K)
cp : specific heat (J/kgK)
Deq : equivalent diameter (m)f : friction factor (-)݉ሶ : mass flow rate (kg/s)
NTU : number of transfer unit (-)
Q: heat transfer rate (W)r : ratio of warm seawater heat capacity flow rate (-)
S : total cross sectional area in PHE (m2)
T : Temperature (K), (oC)Tm : logarithmic Temperature (K)U : overall heat transfer coefficient (W/m2K)
v : mean velocity in the plate (m/s)
W: power output (W)P: pumping power (W)Greek symbols
 : Heat transfer coefficient (W/m2K)

 : Density (kg/m3)
 : Thermal conductivity (W/mK) : kinetic viscosity coefficient (m2/s)
 : Efficiency (W/mK) : Performance index for OTEC heat exchanger (-)
Subscripts
C : cold deep seawater
H : high heat working temperature in irreversible heatengineHS : heat source
L : low heat working temperature in irreversible heatenginem : maximized
NTU : considered the number of transfer unit
O : outlet of heat exchanger
P : pump
pt : plate
W : warm surface seawater

introduce the ideal heat exchange from heat source to heat engine, and show the thermal efficiency in case of the
maximum net power. Considering the OTEC system without seawater intake system, the required pumping power ofsurface and deep seawaters will be the same magnitude of power as the generated power by the heat engine, and theymight be able to get over the generated power due to the balance of the heat transfer performance and pressure drop in
the heat exchangers (Yasunaga, et al., 2008). To achieve the development of the net power output from OTEC system,
the ideal practical heat exchanger is required, which has enhanced heat transfer performance and low pressure drop. On
the other hand, the performance evaluation of the heat exchangers is generally conducted to evaluate the heat transfer
performance and pressure drop produced by friction. For each heat exchangers, heat transfer performance and pressure
drop can be measured and summarized. So, the individual comparison of heat exchanger performance considering heattransfer performances or pressure drop is definitely obtained. However, in the case of an OTEC system in which heatexchangers are used as evaporator and condenser, both characteristics have an important effect on the net power output
and are of the same magnitude.
Therefore, the total performance evaluation method of heat exchangers is required for the selection and design of theheat exchangers as well as the development of the heat exchanger performance. This study describes about the theoretical
relationship between heat transfer performance of heat exchangers including pressure drop and power output from theheat engine and shows the results of the comparison of the available power output from the power generation systemusing existing heat exchangers.

3. Fundamental Equations
3.1 Principle of OTEC system

Fig.1 shows the OTEC power generation system model using reversible heat engine. The ocean thermal energy is thetemperature difference between the surface seawater and the depth. To harvest the thermal energy, both seawaters should
be continuously flowed to the heat exchangers to transfer the heat to with the heat engine by heat exchangers. The power
output from heat engine W, heat transfer rate from warm seawater QW and to the cold deep seawater QC are, respectively,ܹ ൌ ܳௐ െ ܳ஼ܳௐ ൌ ‫ܥݎ‬ுௌ ൫ܶௐ െ ܶௐǡை ൯ܳ஼ ൌ ሺͳ െ ‫ݎ‬ሻ‫ܥ‬ுௌ ൫ܶ஼ǡை െ ܶ஼ ൯

(1)
(2)
(3)

67

Performance Evaluation of Heat Exchangers for Application
to Ocean Thermal Energy Conversion System

Where CHS is the total heat source heat capacity flow rate, which is the summation of the surface heat capacity flow rate
and the depth. Fig. 2 shows the conceptual T – s diagram of OTEC with reversible heat engine. In case of reversible heatengine, the entropy generation will be zero,
ொೈ
்ಹ

െ

ொ಴
்ಽ

(4)

ൌͲ

The thermal efficiency th and the power output W can be calculated as,
ௐ

ொೈ

ൌͳെ

ܹ ൌ ܳௐ ߟ௧௛

்ಽ

(5)

்ಹ

(6)

TW

Heat exchanger

TW,O

TH
Reversible
heat engine
TL

TC,O

TC

Heat exchanger
Deep Seawater
Intake Pump

Warm Seawater
Intake Pump

Surface seawater
Deep seawater

Fig. 1. OTEC power generation system model using reversible heat engine.

TW
TW,O

Temperature T

ߟ௧௛ ൌ

TH
Heat Engine
TL
TC,O
TC

Specific entropy s

Fig. 2. Conceptual T–s diagram of OTEC power generation system.

68

Takeshi YASUNAGA, Kevin FONTAINE, Takafumi MORISAKI and Yasuyuki IKEGAMI

3.2 Heat exchanger performance for OTEC power output

In heat exchange process, heat exchangers are used and the heat flow rate depends on the performance of the heatexchangers. Using overall heat transfer coefficient U and logarithmic mean temperature Tm, the heat transfer rates canbe expressed as,(7)(8)

�� � �� �� ���� ���� � �� �� ���� ��

From Eq.(1) to (6), the work output can be the one degree of freedom as function of TW,O or TC,O. Then the work output
can be maximized by �� ⁄����� � � or �� ⁄����� � � . The maximum work considering the heat exchanger
performance Wm,NTU can be expressed as,������ ���������� ����

(9)

�

Here,

��

���

��� �����

�

�

(10)

�

(11)

��� �����

����� � ���� � �� �

Where, NTU is the heat transfer unit and is defined as follows;
��� �

��

(12)

����

If NTU is infinite, the maximum power output Eq.(9) will be as follows,(13)�� � ��� � ����� ����Fig.3 shows the relationship between the ratio of maximum available power output Wm,NTU / Wm and the heat transfer
performance as net transfer unit NTUW and NTUC. According to Fig.3, the ratio of maximum available power will be
63%, 86% and 95% when NTU is 1.0, 2.0 and 3.0, respectively.
In the OTEC system, the pressure drop due to the friction of the stream in the heat exchanger is not negligible. The
pressure drop yields the pumping power for the seawaters, which can be calculated as,� � ��

��

(14)

���

Where P is the mechanical efficiency of the seawater pumps and simplified P can be the pressure drop of the heatexchangers. The total pressure drop in the stream of the seawaters is related the friction factors of the each heat exchangers,
piping, valves and the mean velocities in the each equipment. Then, the net power output is calculated as,(15)���� � � � ��� � �� �

Then, the maximum net power using reversible heat engine will be,���������� ���������� ������ ��� � �� �

(16)

69

Performance Evaluation of Heat Exchangers for Application
to Ocean Thermal Energy Conversion System

Ratio of maximum available power output
Wm,NTU/Wm [%]

100%
80%
60%
40%
20%
0%

0

0.5

1

1.5

2

2.5

3

3.5

4

4.5

5

Net transfer unit NTUW=NTUC

Fig. 3 Dependency of the ratio of maximum available power output and net transfer unit in case TW=30
C, TC=5 oC and r=0.5.

oAccording to Eq.(14), the heat exchangers in OTEC system has a significant role and is the one of the key equipment
to increase the net power output. For the increase of net power output in OTEC system, the enhancement of heat transfer
performance (positive element) is required as well as decreasing the pressure drop (negative element). However, toenhance the heat transfer performance contradicts the reduction of the pressure drop.
In general, the heat exchanger performance and pressure drop are evaluated respectively. However, for comparison of
the heat exchanger performance in the system, performance evaluation method is required since the net power is thebalance of the two opposite elements.

4. Heat exchanger performance evaluation models
4.1 Ratio of maximum power output

For the evaluation of the heat exchanger performance in the system, the maximum available power output and thepressure drop are assumed as the function of the mean velocity of heat source in the heat exchanger. For comparison ofvariable heat exchanger, the net power output per unit heat transfer are is the most important if we consider the cost of
materials. Hence, Eq.(16) is expressed as,��������������� ���� ���� ������ �
��

�

����
�

�

��� ���� ���� ������ ������ ��� ��� �
�
�
� ��

(17)

Where the efficiency of the heat source pump is assumed to be 100% (P=1) to avoid the effect of the efficiency on theheat exchanger performance evaluation, and also assumed the ratio of heat capacity flow rate as 0.5 because the warmand cold seawater condition is same.
Now, to normalize the net power, the ratio of maximum available power output for heat exchanger performance can becalculated using backwork ratio (BWR), which is generally used in Gas-turbine cycle (Jones and Hawkins, 1986) ,����������
��

��� �

� �� � � ������ � � ������������ ���� ���

(18)
(19)

Eq.(17) indicates the available net power output by unit heat transfer area and is used to applied as the design
optimum function of optimization in OTEC system (Uehara and Ikegami, 1990, and Ikegami and Uehara, 1992)
considering that the heat transfer is the dominant parameter for the capital expenditure of OTEC system. On the other
hand, Eq.(19) is the theoretical performance evaluation that indicates the available power output from the potential energyof unit mass flow rate of heat source in the system. Now, to consider the characteristics of Eq.(17) and Eq.(18), the70Takeshi YASUNAGA, Kevin FONTAINE, Takafumi MORISAKI and Yasuyuki IKEGAMI

following performance index for OTEC heat exchanger  is proposed,�������������� ������ ������ �����

(20)

�

3.2 Optimization of maximum power

The heat transfer performance UA is expressed as,
�� �

1

��� �

�

1

��
1
�
�� � �

(21)

��
1
1
�
�
��
�� � � ��� �

�22�

�

��� �

�

Taking the assumption that the heat resistance of the heat source heat transfer coefficient is dominant,
1

��� �

�

�

�

��� �
�
��� ���
� �Re� Pr �
�� �
λ

�2��

Where, Nu, Re and Pr are Nusselt, Reynolds and Prandtl numbers, respectively. Hence, Eq.(21) can be expressed as,

�� �

�

�
��
��� �

�

�

���� �� � ��

(24)

�

��� ������ ��� ��With the following definitions:μ��ρ��� �
� Re �μλ
RePrλ�
���� � ����� ������ � ρ���

Pr �

(25)
(26)

Therefore, NTU can be calculated as,

��� �

�

�Re� Pr � λA

��Re��� Pr �� �����������λ�
���� � ��Re� Pr � λA����� � ��Re� Pr � λA��
���

(27)

The seawater pumping power at the warm and cold side respectively which depend of the pressure loss in the heatexchangers.
�� �

4�� ρv �
��� 2

(28)

With (25) and (28)��4����� � � 2��Re� �� ���� ��2��� ����ρ�� � �Re� � ��

(29)
(30)

71

Performance Evaluation of Heat Exchangers for Application
to Ocean Thermal Energy Conversion System

Finally, with (9) to (11) and (27) to (29),��m,net,NTU �

�

����

������
��������� ��
���

�

�

�

������
�������� ��
�
���

�

��

������ �� �
� ��
���

� ��
�

������ �� �
� ��
���

�

�

(31)

The Matlab function “fminsearch” is used. It is an optimization algorithm based on a derivative-free method (NelderMead simplex algorithm) to find a local minimum to a function. However, “fminsearch” does not allow the user to add
constraints nor boundaries for the parameters. Thus the function “minimize” written by Rody Oldenhuis (2017) is usedinstead. It is based on Matlab “fminsearch” algorithm and allows constraints and boundaries.
This function need, as input, the function to minimize, a starting point (values of the parameters where the algorithm
starts to search for a local minimum), linear inequality constraints, linear equality constraints, lower boundary, upperboundary and nonlinear inequality and equality constraints. In this case only nonlinear constraints and boundaries will
be used.
As the function is designed to find a local minimum, the function Wnet,net,NTU is minimized. Moreover, the functionneeds to be used several times at random starting points within the boundaries in order to search for a global maximum.

5. Results and discussions
5.1 Ratio of maximum power output

As one of the example of the evaluation using the ratio of maximum power output, 3 different plate type heatexchangers are used (Kushibe, et al., 2005). Table 1 shows the heat exchanger specifications. By referring theperformance date on the paper, each overall heat transfer performance and pressure drop are approximated as the functionof the mean velocity of heat source in the exchangers. The approximation coefficients are listed on the Table 2.
Figure 4 shows the net power output per unit heat transfer area as function of the mean velocity of heat source in theplate. In each PHE, the maximum power output per unit area forms a parabolic path. The maximum power output is abalance of the increase of maximum power and the heat source pumping power. The NTU increases with the increase of
the mean velocity of heat source, however, the increase of the pressure drop is higher than the maximum power output,
then as a results, the net power output will be form the parabolic curve. The optimum heat source mean velocities are
0.30, 0.47 and 0.39 for PHE1, PHE2 and PHE3, respectively. In case PHE2, the optimum heat source mean velocity isover the range of the overall heat transfer coefficient experimental data and then the calculation was assumed that the
0.40 m/s to 0.59 m/s will varies the same trend as the experimental date range.
The parameters of the optimum mean heat source velocity is listed in Table 3. And Fig. 5 shows the ratio of the net
power output, backwork ratio and ratio of other losses during the heat exchange process. According to Table 3 and Fig.5,
the performance of PHE1 is highest ratio of the net power output of 60%, and PHE3 follows that of 52% and in case of
PHE2 is only 41%. The results shows that PHE2 is the lowest NTU at the optimum heat source mean velocity rather thanthat of PHE1 and PHE3. This means that the system applied PHE2 is the highest heat source consumer. On the other
hand, with regard to BRW, PHE2 is the lowest compare with the other two PHEs. Regarding the performance index for
OTEC heat exchanger , PHE2 is almost triple of both PHE1 and PHE3. From Eq.(13), the maximum power output is
proportional to the mass flow rate of the heat source,  in PHE2 is the best overall performance.

5.2 Optimized maximum power evaluation

Calculations are done with a Reynolds number taken so that the water velocity in the heat exchangers is between 0.2 m/s
and 1.8 m/s. Wnet/A is calculated and plotted as a function of Rews and Recs. This calculation is limited to the Reynolds
boundary specified. Axis are set so that only Wm,net,NTU corresponding to reachable Reynolds is displayed. For each heatexchangers the Nusselt correlation and friction factor are used. These values are given in the table 4. And Fig. 6 to 8
show Wm,net,NTU as a function of Reynolds number for PHE1, PHE2 and PHE3 in case of TW=30 oC and TC=5 oC. Actual
power output of an OTEC power plant using the specified heat exchanger should be less than these results as calculations
are based on a Carnot cycle and if pressure drop is considered, required power for water ducting is not. However, results
give the optimum Reynolds numbers and show that, for a non-negligible range of Reynolds number, net power output
can be null or negative (dark blue areas). Flow rate should then be controlled rigorously to adjust Reynolds number inthe heat exchanger.

72

Takeshi YASUNAGA, Kevin FONTAINE, Takafumi MORISAKI and Yasuyuki IKEGAMI

Table 1 Heat exchangers specifications.

Heat exchanger
Length (mm)Width (mm)Plate Thickness (mm)Space between plates (mm)equivalent diameter (mm)Material
Surface pattern
Number of plates
Total heat transfer area(m²)
Total cross surface area
(m²)

PHE1
960
576
0.7
4
8
SUS316
Herringbone (72°)
120
100.3
0.14

PHE2
718
325
0.5
3.96
7.9
Titanium
Herringbone (30°)
20
3.96
0.012

PHE3
1765
605
0.6
2.68
5.36
titanium
Fluting & drainage
52
40.6
0.041

Table 2 Approximation coefficients.

Heat exchanger
Overall heat transfer
coefficient U (kW/m2K)

Pressure drop P (kPa)

PHE1

PHE

PHE3

Multiplier factor 

4.197

5.637

3.254

Exponential factor 

0.223

0.359

0.456

Data range VHS

0.20-0.44

0.59-1.20

0.29-0.59

Multiplier factor 

306.31

65.38

182.30

Exponential factor 

1.863

2.210

2.004

Data range VHS

0.16-0.45

0.60-0.19

0.48-0.59*The data is approximated as an exponential function as U= VHS  and P = VHS Fig. 4 The net power output per unit heat transfer area as function of the mean velocity of heat source in theplate. In case the TW=30 oC, TC=5 oC, cp=4.0 kJ/kgK and =1,025 kg/m3.The chain line in PHE2 shows theextended from experimental range. The circular plots show the maximum point of power output and i.e. theoptimum mean velocity of heat source in each plate heat exchanger.

73

Performance Evaluation of Heat Exchangers for Application
to Ocean Thermal Energy Conversion System

Table 3 Optimum mean velocity condition.

Heat exchanger

PHE1

PHE2

PHE3

VHS, opt (m/s)

0.39

0.60

0.49

UHS,opt (kW/kgK)

3.39

4.58

2.36

PHS,opt (kPa)

51.8

18.3

44.3

1,57

0.65

1.14

Wm,net, NTU,m / A (kW/m )

0.18

0.39

0.14

Wm,NTUnet,m / Wm (%)

60

41

52

 (m )

0.36

0.98

0.33

NTUHS,opt (-)
2-2*The condition of calculation corresponds in case of Fig.4.

Fig. 5 The unit maximum work ratio, backwork ratio and other losses during heatexchange at the optimum mean heat source velocity in PHE. The condition of
calculation corresponds in case of Fig.4.
This work allows to compare heat exchangers between them in order to choose the best one for OTEC application by
predicting the maximum power output. However, this should not be the only parameter to consider but also the theaccuracy of the Reynolds number control.
Comparing the optimum points in Table 3 and Fig.6 to 8, the trend of the maximum available power per total heattransfer area is comparable in the two different calculation. Therefore, it is confirmed that the perfomance evaluationindex fro OTEC  is effective for the evaluation to compare the perforamnce of PHE.

6. Summary

For the purpose of the development of the total performance evaluation method of heat exchangers for OTEC, thetheoretical relationship between heat transfer performance of heat exchangers including pressure drop and power output
from the heat engine is derived and the results of the comparison of the available power output from the power generation
system using 3 plate heat exchangers were shown. The results shows the performance index of the heat exchanger for
OTEC is able to show the performance for OTEC system.
And the optimization of heat exchanger for reversible heat engine OTEC system has conducted using the assumptionof the heat source heat transfer coefficient is the dominant thermal resistance. As the result, the 3 plate heat exchanger
maximum available powers have been clarified.
Comparing the optimum points of two different method, the tendency of the maximum available power per totalheat transfer area is comparable. Therefore, it is confirmed that the perfomance evaluation index fro OTEC theperformance index of the heat exchanger for OTEC is effective for the evaluation to compare the perforamnce of PHEs.

74

Takeshi YASUNAGA, Kevin FONTAINE, Takafumi MORISAKI and Yasuyuki IKEGAMI

Table 4 Nusselt and friction factor correlations.

Heat exchanger
PHE1
PHE2
PHE3

Nusseltܰ‫ ݑ‬ൌ ͲǤͳͳͳܴ݁ ଴Ǥ଼ ܲ‫ݎ‬ଵȀଷܰ‫ ݑ‬ൌ ͲǤͲͷͺܴ݁ ଴Ǥ଼ ܲ‫ݎ‬ଵȀଷܰ‫ ݑ‬ൌ ͲǤͲͷͳܴ݁ ଴Ǥ଼ ܲ‫ݎ‬ଵȀଷ

Fig. 6 Maximum net power output of an OTEC power plantusing PHE1 as both evaporator and condenser as a function of
Reynolds.

Friction factor݂ ൌ ͳǤͶͺ͸͵ܴ݁ ି଴Ǥ଴଺ହସ݂ ൌ ͸ǤͷͲͷͻܴ݁ ି଴Ǥଷଶଽଶ݂ ൌ ͲǤ͹͵͹ͳܴ݁ ି଴Ǥଵଶ଻ସ

Fig. 7 Maximum net power output of an OTEC power plantusing PHE2 as both evaporator and condenser as a functionof Reynolds.

Fig 8 Maximum net power output of an OTEC power plantusing PHE3 as both evaporator and condenser as a functionof Reynolds.

References

Uehara, H., OTEC reader, Ohm sha (1982), pp.61-113
Avery, H. W. and Wu, C., Renewable Energy from the Ocean, Oxford University Press, (1994), pp.90-151
Bejan, A., Advanced Engineering Thermodynamics, Wiley, New York, (1998)
Ibrahim, O. M., Effect of Irreversibility and Economics on the Performance of a Heat Engine, Transaction of ASME
Journal of Solar Energy Engineering, Vol.114, (1992), pp.267-271
Ikegami Y., and Bejan, A., On the thermodynamic optimization of power plants with heat transfer and fluid flow

Performance Evaluation of Heat Exchangers for Application
to Ocean Thermal Energy Conversion System

irreversibilities, Transaction of ASME Journal of Solar Energy Engineering, Vol.120, (1998), pp.139-144
Yasunaga, T., Ikegami, Y. and Monde, M, Performance Test of OTEC with Ammonia/water as Working Fluid Using Shell
and Plate Type Heat Exchangers (Effect of Heat Source Temperature and Flow Rate), Transaction of JAME,, B,
Vol.74, No.738, (2008), pp.445-452
Uehara, H., and Ikegami Y., Optimization of a Closed-Cycle OTEC system, Transaction of ASME Journal of Solar
Energy Engineering, Vol.112, (1990), pp.247-256
Ikegami Y. and Uehara, H., PERFORMANCE ANALYSIS OF OTEC PLANTS AT OFF-DESING CONDITIONS:AMMONIA AS WORKING FLUID, Transaction of ASME Journal of Solar Energy Engineering, No.G0656A,(1992), pp.633-638
Jones, J. B. and Hawkins, G. A., Engineering Thermodynamics an Introductory Textbook, second edition, John Wiley &Sons, Inc., (1986), p.578
Rody Oldenhuis, Matlab minimization algorithm “minimize” version 1.7, (2017) available on the website:
http://nl.mathworks.com/matlabcentral/fileexchange/24298-minimize
Kushibe, M., Ikegami, Y., Monde, M. and Uehara, H., Evaporation Heat Transfer of Ammonia and Pressure Drop ofWarm Water for Plate Type Evaporator, Transaction of the JSRAE, Vol.22, No.4, (2005), pp.403-415 (in Japanese)75