Urecol Journal.
Part D:
Applied Sciences Vol.
2 No.
eISSN: 2797-2089 Design of Shell and Tube Heat Exchanger for Production Aluminium Nitride Nanoparticle in Application Industry Ranggaweny Al-Ghani1.
Asep Bayu Dani Nandiyanto1 .
Teguh Kurniawan2 1Department of Chemical Education.
Universitas Pendidikan Indonesia.
Indonesia 2Department of Chemical Engineering.
Universitas Sultan Ageng Tirtayasa.
Indonesia nandiyanto@upi.
https://doi.
org/10.
53017/ujas.
Received: 13/02/2022 Revised: 25/03/2022 Accepted: 28/03/2022 Abstract The current industrial implementation process is required to be carried out efficiently and environmentally friendly, this can be done with the presence of a heat exchanger.
However, heat exchangers in the production of aluminum nitride nanoparticles are still rare.
The purpose of this research is to analyze and improve the heat exchanger design in the production process of aluminum nitride nanoparticles at low cost.
The heat exchanger can be designed based on several parameters of the TEMA standard by dimensional specification and specifications of hot and cold fluids.
The method is calculated using a Microsoft excel application to evaluate the heat exchanger design according to the TEMA standard.
The results showed that the shell and tube heat exchanger was designed with 39 tubes and an effective value of 85.
These results have met the TEMA standard and it is hoped that the design and evaluation of this heat exchanger can be used as a reference in the aluminum nitride nanoparticle production industry.
Keywords: Aluminum nitride nanoparticle.
Fluids.
Heat exchanger.
Industry Introduction According to a report from the International Energy Agency (IEA).
World energy demand grew by around 2.
1% in 2017, a doubling of the previous year.
In detail, the production of carbon emissions results from most of the energy consumption in the form of thermal and most of the heat energy production process .
In order to minimize this energy consumption and reduce carbon emissions, heat exchangers are found to be an important tool part used in thermal energy systems such as power plants, refrigeration systems, and petrochemical units .
A heat transfer device that moves heat energy from one medium to another is called a heat exchanger.
Two fluids with different temperatures will be separated on the hot side or the cold side by a separating medium in order to achieve the ideal thermal in the heat transfer process.
An advantage of a heat exchanger is that it is affordable and has high thermal efficiency .
A heat exchanger is a device that functions as a flow of heat energy between two or more fluids at different temperatures .
Heat exchangers are widely used in various industrial applications, such as food processing, pharmaceutical industry, heat removal from nuclear reactors, etc .
, .
In addition, heat exchangers are used in process, electricity, transportation, air conditioning and refrigeration, cryogenics, heat recovery, alternative fuels, and manufacturing industries .
Until now, there have been many papers that explain the rapid development of heat exchangers in the industrial world.
Fattahi et al.
investigating the application of Urecol Journal.
Part D: Applied Sciences.
Vol.
2 No.
Ranggaweny Al-Ghani et al aluminum nitride as an advanced ceramic for making heat exchangers.
The results showed that the heat exchanger fabrication made of AlN showed an increase in heat effectiveness by 26% from the maximum value.
Nekahi et al.
investigating effectiveness can measure the ideal performance of a heat exchanger, whereby it transfers the maximum amount of heat.
Shirvan et al.
also proposed a new model for the analysis of heat transfer sensitivity and effectiveness of a heat exchanger in the form of a double pipe heat exchanger.
Gasia et al.
investigating the effect of convection forces in a cylindrical shell-and-tube heat exchanger in which water is used as PCM and circulated during the smelting process.
increasing the PCM, the flow rate in the heat exchanger, the melting period, effectiveness and heat transfer rate are improved.
This study aims to design and design the types of tubes and shells of heat exchangers in the production of Aluminum Nitride (AlN) nanoparticles.
Figure 1 shows a laboratory scale production of AlN production which requires a 70 AC heat device to mix all the precursors.
Assuming industrial-scale production processes, laboratory-scale heating is replaced by heat It is necessary to design a heat exchanger for aluminum nitride nanoparticles because there is still little research on heat exchangers in this industry.
To evaluate the performance of a heat exchanger, focus on calculations based on thermal load (Q), logarithmic mean temperature difference (LTMD), heat transfer surface area (A), and number of tubes (N.
of the heat exchanger to obtain dimensional spesification and specifications of hot and cold fluids in the design of heat exchanger device.
Figure 1.
Illustration of Aluminium Nitride Particle Production Method The design of the heat exchanger chosen in this study is a shell and tube type heat This type was chosen because it is easy to manufacture in various sizes and flow configurations, easy to use at various operating temperatures and pressures .
, and its adaptability to different operating conditions .
Shell and tube heat exchangers also have a larger heat transfer surface to volume ratio than other heat exchangers .
This heat exchanger is designed according to several parameters of the Standard of Tubular Exchanger Manufacturers Association (TEMA) to obtain data regarding the specifications and evaluate the performance of the heat exchanger design according to the These parameters are listed in Table 1.
Urecol Journal.
Part D: Applied Sciences.
Vol.
2 No.
Ranggaweny Al-Ghani et al Table 1.
Calculation of Heat Exchanger Parameters Section Basic Parameter The transferred (Q) Logarithmic mean difference (LMTD) Correction factor Heat Transfer Field Area (A) Number of Tubes (N) Shell Diameter Baffle spacing Tube Surface Total Area of Heat Equation Qin = Qout ycoyca y yaycyyca y OIycNyca = ycoEa y yaycyEa y OIycNEa Where.
Q = the energy transferred (W.
m = the mass dflow rate of the fluid (Kg/.
Cp = the specific heat OIycN = the fluid temperature difference (AC).
cNEaycn Oe ycNycaycn ) Oe .
cNEaycu Oe ycNycaycu ) yaycAycNya = .
cN Oe ycNycaycn ) ycoycu Eaycn .
cNEaycu Oe ycNycaycu ) Where, ycNEaycn = temperature of the hot fluid inlet (AC) ycNEaycu = temperature of the hot fluid outlet (AC) ycNycaycn = temperature of the cold fluid inlet (AC) ycNycaycu = temperature of the cold fluid outlet (AC) ycNEaycn Oe ycNEaycu ycI= ycNycaycu Oe ycNycaycn ycNycaycu Oe ycNycaycn ycE= ycNEaycn Oe ycNycaycn 1OeycE OoycI 1 ycoycu ycoycu .
Oe ycEycI] ya= 2 Oe ycE.
cI 1 Oe OoycI2 1 .
cI Oe .
ycoycu ycoycu ( 2 Oe ycE.
cI 1 OoycI2 1 ycE ya= ycO y yaycNycAya Where, ycE = the energy transferred (W) ycO = the overall heat transfer coefficient LMTD = the logarithmic mean temperature ya ycA= yuU y yaycu y yco Where.
N = the number of tubes A = the area of the heat transfer area .
, yuU = 3.
yaycu = tube diameter .
yco = tube diameter .
Oo yaya y (.
a y .
cEycI)2 y yaycu 1 yaycNycE yayc = 0.
yco Where, yayc = shell diameter .
ya = the area of the heat transfer area .
R = the correction factor yaycu = tube diameter .
For CTP value .
ne tube pass = 0,93.
two tube pass = 0,90.
and three tube pass = 0,.
and CL value .
A and 45A = 1,00.
and 30A and 60A = 0,.
Baffle spacing = 0,2 ycu yayc Where, yayc = shell diameter .
ycaAyc ycayc = ycAyc ycu Urecol Journal.
Part D: Applied Sciences.
Vol.
2 No.
Ranggaweny Al-Ghani et al Section Parameter Transfer in Tube .
Mass Flow Rate of Water in Tube (G.
Reynold (Re,.
Prandtl (Pr,.
Number Nusselt (Nu,.
Inside coefficient .
Shell Shell flow area .
ayc ) Mass Flow Rate of Water in Shell (G.
Equivalent diameter .
ccyce ) Equation Where, ycayc = the total heat transfer surface area in the tube .
ycAyc = the number of tubes ycaAyc = the flow area in the tube .
n = the number of passes.
ycoEa yayc = ycayc Where, yayc = the mass flow of water in the tube .
g/m2.
ycoEa = the mass flow rate of the hot fluid (Kg/.
ycayc = the flow area tube .
2 yccycnyc y yayc ycIyceyc = yuN Where, ycIyceyc = the Reynolds number in tube yccycnyc = the inner tube diameter .
, yayc = the mass flow of water in the tube .
yuN = the dynamic viscosity (Kg/m.
yaycy y yuN 1 ycEyc = ( ya Where.
Pr = Prandtl number Cp = the specific heat of the fluid in the tube yuN = the dynamic viscosity of the fluid in the tube (Kg/m.
K = the thermal conductivity of the tube material (W/mAC).
ycAyc = 0.
023 y ycIyceyc 0.
8 y ycEyc 0.
Eaycn = ycAyc y ya yccycn , yc Where.
Eaycn = the convection heat transfer coefficient in the tube (W/m2AC) K = the thermal conductivity of the material (W/mAC) yccycn , yc = the inner tube diameter .
yccyc y ya y yaA yayc = ycEyc ycAyc 1 yayca = yccycu ( )ycu1 yco1 Where, yccyc = shell diameter .
C = clearance .
cEyc -yccycu ) B = a shell bundle ycEyc = tube pitch .
25y yccycu ) .
ycoyca yayc = ycayc Where, ycoyca = the mass flow rate of the cold fluid (Kg/.
yayc = the shell flow area .
ycEyc 1 ycc 4( 2 y 0.
87 ycEyc Oe 2 yuU 4ycu,yc ) yccyce = 2 yuUyccycu,yc Urecol Journal.
Part D: Applied Sciences.
Vol.
2 No.
Ranggaweny Al-Ghani et al Section Parameter Reynold (Re,.
Prandtl (Pr,.
Number Nusselt (Nu,.
Convection Heat Transfer Coefficient .
Shell Tube Heat rate Actual Overall Heat Transfer Coefficient (Uac.
Hot Fluid Rate .
aEa ) Cold .
aya ) Fluid Rate Equation Where, ycEyc = tube pitch .
25y yccycu ) .
= 3.
yccycu,yc = tube outside diameter .
yccycnyc y yayc ycIyceyc = yuN Where, ycIyceyc = Reynold number yccycnyc = inner tube diameter .
yayc = the mass flow of water in the shell (Kg/m2.
yuN = the dynamic viscosity (Kg/m.
yaycy y yuN 1 ycEyc = ( ya Where.
Prs = Prandtl number = specific heat capacity .
J/kgAC) yuN = dynamic fluid viscosity (Kg/m.
= thermal conductivity (W/mAC).
ycAycyc = 0.
023 y ycIyceyc 0.
6 y ycEyc 0.
Where, ycIyceyc = Reynold number = Prandtl number ycAyc y ya Eaycu = yccyce Where.
Eaycu = convection heat transfer coefficient (W/m2AC) = thermal conductivity (W/mAC) yccyce = equivalent diameter .
ycOycaycayc = 1 OIyc 1 Eaycn yco Eaycu Where.
Eaycn = inside heat transfer coefficient (W/m2AC) Eaycu = outside heat transfer coefficient (W/m2AC).
OIyc = wall thickness .
= thermal conductivity(W/mAC) yaEa = ycoEa .
yaycyEa Where, yaEa = hot fluid rate (W/AC) yaycyEa = specific heat capacity (J/KgAC) ycoEa = mass flow rate of hot fluid (Kg/.
yaya = ycoyca .
yaycyyca Where, yayca = cold fluid rate (W/AC), yaycyEa = specific heat capacity (J/KgAC), ycoyca = mass flow rate of cold fluid (Kg/.
ycEycoycaycu = yaycoycnycu .
cNEa,ycn Oe ycNyca,ycn ) Where, ycEycoycaycu = maximum heat transfer (W) Cmin = minimum heat capacity rate (W/AC) Urecol Journal.
Part D: Applied Sciences.
Vol.
2 No.
Ranggaweny Al-Ghani et al Section Parameter ycNEa,ycn (AC) ycNyca,ycn (AC).
Effectivenes Heat Exchanger Effectiveness .
uA) Number
Transfer
(NTU)
Unit Fouling factor (R.
Equation = temperature of the hot fluid inlet = temperature of the cold fluid inlet yuA= ycEycaycayc y 100% ycEycoycaycu Where, ycEycaycayc = actual energy transferred (W) ycEycoycaycu = maximum heat transfer (W) ycOyya ycAycNycO = yaycoycnycu Where, ycO = overall heat transfer coefficient (W/m2AC = heat transfer area .
yaycoycnycu = minimum heat capacity rate (W/AC).
ycOyca Oe ycOycaycayc ycIyce = ycOyca y ycOycaycayc Where, = fouling factor ycOyca = overall heat transfer coefficient (W/m2AC) ycOycaycayc = actual overall heat transfer coefficient (W/m2AC) .
Results and Discussion When designing a heat exchanger, we must determine the materials used to make the heat exchanger according to the type of material and the amount of material with fluid as a heating medium in measuring dimensions.
Various designs are determined in estimating the best heat exchanger performance design, such as:
The heat exchanger design is shell and tube type .
wo shell pass and four tube pas.
The material for the heat exchanger design is carbon steel.
The fluid used is a light oil-water fluid system.
The flow system in this heat exchanger is counter flow.
The hot fluid is assumed to be on the shell side and the cold fluid is assumed to be on the tube side.
The specifications for the stationary head type .
ndicating front en.
, shell .
ndicating shell typ.
, and rear head .
ndicating rear end typ.
of the heat exchanger are AEW It is assumed that there is no heat leakage during the heat exchange process.
The overall coefficient (U) for light oil-hot and cold water fluids is 650 W/m2.
AC.
The orientation of the shell geometry is horizontal The baffle type is single segmental with perpendicular orientation The hot fluid is located on the tube side and the cold fluid is located on the shell side.
The dimensions of the heat exchanger are designed using several assumptions.
Table 2 shows the dimensions of the heat exchanger according to the TEMA standard and Table 3 shows the specifications of the fluids acting on the equipment.
Evaluation of equipment performance is necessary in designing heat exchangers.
The performance of the heat exchanger consists of the thermal load (Q), the logarithmic average temperature difference (LTMD), the heat transfer surface area (A), and the number of tubes Urecol Journal.
Part D: Applied Sciences.
Vol.
2 No.
Ranggaweny Al-Ghani et al (N.
of the heat exchanger.
Table 2 and Table 3 data are used to model the heat exchanger.
Based on the assumptions and calculation analysis, the designed heat exchanger follows the specifications in Table 4.
The specifications of the equipment used are based on the standards of The Tubular Exchanger Manufactures Association (TEMA).
Based on the calculation results, the resulting heat transfer rate is 690000 W .
ee Table .
Table 2.
Dimensional specifications of heat exchangers based on TEMA standards Parameters Conductivity Material (W/mAC) Tube Outer Diameter .
Tube Inner Diameter .
Wall Thickness .
Tube Length .
Tube arrangements Pitch Tube .
Tube-side passes Tube Characteristic Angle (A) Shell Outer Diameter .
Shell Inner Diameter .
Baffle Cut Baffle Spacing .
Specification four passes side Table 3.
Specification of hot and cold fluids Parameters Inlet Temperature (Th,in.
AC)
Outlet Temperature (Th,out.
AC)
Inlet Temperature (Tc,in.
AC)
Outlet Temperature (Tc,out.
AC)
Fluid Flow Rate .
Density .
g/m.
Viscosity (Nm.
s/m.
Thermal Conductivity (W/m.
Heat Spesific (J/kg.
Operating Pressure .
The specification in Tube Side (Cold Flui.
Water The specification in Shell Side (Hot Flui.
Light Oil Other parameters such as LMTD, surface area, number of tubes, overall heat exchanger transfer coefficient, and the effective with values of 45,53AC, 22,10 m2, 39 pcs, 650 W/m2.
72%, respectively .
ee Table .
Although the effectiveness value is quite good, some parameters do not meet the standards.
Figure 2 illustrate the tube arrangement and 2D tube layout drawing.
Figure 2.
Tube arrangement: Triangular 30A.
Two dimensional tube Urecol Journal.
Part D: Applied Sciences.
Vol.
2 No.
Ranggaweny Al-Ghani et al Table 4.
Performance Parameters of Heat Exchanger Designed Based On Calculations Parameter Initial Heat Transfer Rate (Q) Logarithmic Mean Temperature Difference (LMTD) Assumed Overall Fluid Heat Coefficient of Water (U.
Pressure Drop in Tube Pressure Drop in Shell Shell Inside Diameter .
iTm Area of Heat Transfer (A) Number of Tube (N.
Total Heat Transfer Surface Area in Tube .
Mass Flow Rate of Water Fluid in Tube (G.
Reynold Number in Tube (Re, .
Prandtl Number in Tube (Pr, .
Nusselt number (Nu,.
Convection Heat Transfer Coefficient in the Tube .
Baffle Spacing Bundle Shell (D.
Total Heat Transfer Surface Area in Shell .
Mass Flow Rate of Water Fluid in Shell (G.
Equivalent Diameter (D.
Reynold Number in Shell (Re, .
Prandtl Number in Shell (Pr, .
Nusselt Number in Shell (Nu, .
Convection Heat Transfer Coefficient in Shell .
Overall Heat Transfer Coefficient Actual (Uac.
Hot Fluid Rate (C.
Cold Fluid Rate (C.
HE Effectiveness .
uA) Number of Transfer Unit (NTU) Fouling Resistance Results 45,53AC 650 W/m2.
83 atm
0,52 atm
70 AC
22,10 m2 4,78 m2 1,04 m/s 0,0648 3,85 0,004 9,041 W/m2.
0,245 m 0592 m2 16,876 m/s 0,00065 m 069 W/m2.
507 W/m2.
2325 W/AC
12558 W/AC
1,7077
0,398 AC.
Conclusion Based on the hypothesis that the heat exchanger design for the production of aluminum nitride nanoparticle which refers to the TEMA standard has been successfully designed with good calculations.
The design uses the Shell and Tube type .
wo shell passes-four tube passe.
with a total of 39 tubes.
The heat transfer rate by the tool is 690000 watts with turbulent flow in the shell and laminar flow in the tube.
The effectiveness of the heat exchanger design reaches more than 85%.
So, the heat exchanger design has good performance.
And it is hoped that with the manufacture of heat exchangers in industry, it can make production at low costs and can reduce carbon emissions so that it is environmentally friendly.
Acknowledgements This study was supported by RISTEK BRIN (Grant: Penelitian Terapan Unggulan Perguruan Tinggi (PTUPT)) and Bangdos Universitas Pendidikan Indonesia.
References