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Frontiers of Chemical Science and Engineering

ISSN 2095-0179

ISSN 2095-0187(Online)

CN 11-5981/TQ

Postal Subscription Code 80-969

2018 Impact Factor: 2.809

Front. Chem. Sci. Eng.    2018, Vol. 12 Issue (4) : 619-629    https://doi.org/10.1007/s11705-018-1736-5
RESEARCH ARTICLE
Accounting for local features of fouling formation on PHE heat transfer surface
Petro Kapustenko1(), Jiří J. Klemeš2, Olga Arsenyeva1,3, Olexandr Matsegora4, Oleksandr Vasilenko4
1. National Technical University “Kharkiv Polytechnic Institute,” 61002 Kharkiv, Ukraine
2. Sustainable Process Integration Laboratory – SPIL, NETME Centre, Faculty of Mechanical Engineering, Brno University of Technology – VUT Brno, 616 69 Brno, Czech Republic
3. University of Paderborn, Chair of Fluid Process Engineering, Paderborn, Germany
4. AO Spivdruzhnist-T LLC, 61002 Kharkiv, Ukraine
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Abstract

The fouling phenomena can create significant operational problems in the industry by deteriorating heat recuperation, especially in heat exchangers with enhanced heat transfer. For a correct prediction of fouling development, the reliable fouling models must be used. The analysis of existing fouling models is presented. The chemical reaction and transport model developed earlier for a description of fouling on intensified heat transfer surfaces is used for modeling of plate heat exchanger (PHE) subjected to fouling. The mathematical model consists of a system of differential and algebraic equations. The integration of it is performed by finite difference method with developed software for personal computer. For countercurrent streams arrangement in PHE the solution of two-point boundary problem is realized on every time step. It enables to estimate local parameters of heat transfer process with fouling formation and its development in time with the growth of deposited fouling layer. Two examples of model application in cases of PHEs working at sugar factory and in district heating network are presented. The comparison with experimental data confirmed the model validity and the possibility of its application to determine the performance of PHE subjected to fouling.

Keywords heat transfer      fouling      plate heat exchanger      mathematical model     
Corresponding Author(s): Petro Kapustenko   
Just Accepted Date: 19 April 2018   Online First Date: 01 August 2018    Issue Date: 03 January 2019
 Cite this article:   
Petro Kapustenko,Jiří J. Klemeš,Olga Arsenyeva, et al. Accounting for local features of fouling formation on PHE heat transfer surface[J]. Front. Chem. Sci. Eng., 2018, 12(4): 619-629.
 URL:  
https://academic.hep.com.cn/fcse/EN/10.1007/s11705-018-1736-5
https://academic.hep.com.cn/fcse/EN/Y2018/V12/I4/619
Fig.1  PHE plate sketch. 1: Heat media entrance and exit; 2, 5: flow distribution parts; 3: elastomer gasket; 4: corrugated field
Fig.2  Corrugation forms. 1, 2: Intersection of corrugations of plates forming the channel; 3: cross sections of channel for sinusoidal corrugations; 4: cross sections of channel for triangular corrugations
Time q, h 144.0 216.0 264.0 312.0
The mass flowrate of juice G2/(m3·h-1) 260.0 270.0 277.0 265.0
Temperature of incoming juice t21/°C 101.0 100.5 102.0 101.7
Temperature at juice exit: experimental t22exp/°C
Calculated t22clc/°C
105.1
104.9
106.1
105.9
106.9
106.7
106.0
105.8
Temperature of incoming condensate t11/°C 123.5 123.5 123.5 123.5
Temperature at condensate exit: experimental t12exp/°C
Calculated t12clc/°C
102.7
102.5
104.9
104.5
106.0
105.8
104.9
104.7
Fouling thermal resistance: experimental Rfe× 104/(m2·K/W) 1.11 1.56 1.68 1.91
average by modeling Rfm× 104/(m2·K/W) 1.04 1.41 1.64 1.92
Overall heat transfer coefficient: under clean conditions U0/(W·(м2·К)-1) 2219 2667 2685 2381
experimental with fouling Ufe/(W·(м2·К)-1) 1785 1886 1854 1641
calculated by model Ufm/(W·(м2·К)-1) 1768 1944 1871 1639
calculated by Eq. (23) Uf*/(W·(м2·К)-1) 1805 1938 1861 1638
Ratio Ufe/U0× 100% 80.41 70.72 69.01 68.81
Tab.1  The measured parameters and simulated results for PHE M15M thin juice heater
Fig.3  The distribution of fouling thermal resistance along heat transfer surface. Example 1: (1) 28th day of operation; (2) 13th day. Example 2: (3) 28th day of operation with flow velocity w2 = 0.26 m·s-1; dots are experimental data
Fig.4  Overall heat transfer coefficients. Experimental (black dots) and calculated (hollow dots): 1, w2 = 0.57 m·s-1; 2, w2 = 0.40 m·s-1; 3, w2 = 0.26 m·s-1
Fig.5  Simulated averaged values of fouling thermal resistance. 1: w2 = 0.26 m·s-1; 2: w2 = 0.40 m·s-1; 3: w2 = 0.57 m·s-1
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