STEAM RE-HEATING PROCESS INFLUENCE ON ENERGY EFFICIENCY AND LOSSES OF TWO-CYLINDER STEAM TURBINE V. Mrzljak 1 , H. Taletović 1 , J. Orović 2 and I. Poljak 2 1 Faculty of Engineering, University of Rijeka, Vukovarska 58, 51000 Rijeka, Croatia 2 Department of maritime sciences, University of Zadar, Mihovila Pavlinovića 1, 23000 Zadar, Croatia Email: [email protected], [email protected], [email protected], [email protected]Keywords: Steam Re-heating, Steam Turbine, Energy Efficiency, Energy Losses. Abstract: The paper presents an energy analysis of steam turbine with two cylinders and steam re-heater between them from conventional thermal power plant. Steam re-heating process is not performed as usual in such power plants but with one part of the steam delivered in re-heater directly from the steam generator. Observed turbine is analyzed in two operating regimes – with and without inclusion of steam re-heater into the turbine operating process. Regardless of all negative energy effects which steam re-heating process brings into the turbine operation, significant positive effect which compensates all the negative ones is notable reduction of moisture in the steam which expands through the low pressure turbine cylinder. Introduction Steam turbines which operate in conventional thermal power plants use steam re-heating (usually after steam expansion in high pressure cylinder) for increasing the steam temperature before its further expansion in other cylinders [1]. Such process increases the power of the whole steam turbine, decreases whole turbine energy loss and increases energy efficiency of the whole turbine in comparison with the process without steam re-heating [2], [3]. Steam re-heating (heat addition) is in the most of cases performed by additional fuel combustion, while the steam re-heater is usually mounted into the steam generator [4]. Nowadays some power plants, as for example nuclear power plants, also has steam re-heating, but it is combined of two independent processes - the first is moisture separation and the second is steam re-heating by using steam of the highest temperature in the process (a part of steam produced in the steam generators) for heating a steam with lower temperature at the high pressure turbine cylinder outlet [5]. Therefore, nuclear power plants do not use additional fuel for steam re-heating. In this paper the authors find in the literature one (and so far only) conventional thermal power plant which did not have steam re-heating process by using additional fuel combustion - re-heating of steam at high pressure turbine cylinder outlet is performed with one part of steam taken directly from the steam generator. Description and operating characteristics of the analyzed steam turbine with two cylinders and re-heater Analyzed steam turbine consists of two cylinders - High Pressure Cylinder (HPC) and Low Pressure Cylinder (LPC), Fig. 1. Between turbine cylinders is mounted steam re-heater for increasing the steam temperature before its entrance into LPC. Remaining steam after expansion, at the LPC outlet is delivered to steam condenser [6]. The analyzed steam turbine is part of entire conventional thermal power plant presented in [7]. The specificity of such turbine process is the steam re-heating principle, which is not common for conventional thermal power plants. Presented steam re-heating process is usually part of steam re-heating process in nuclear power plants (which included moisture separation and steam re-heating [8]). As usual in conventional thermal power plants, steam re-heating process is performed with heat addition by fuel combustion (regardless of re-heater position). In nuclear power plants, steam which exit from HPC is re-heated with part of steam directly delivered from steam generator(s). Steam turbine analyzed in this paper has the identical re-heating process as nuclear power plant. Fig. 1 Scheme and operating points of the analyzed two-cylinder steam turbine with steam re-heating between cylinders Equations for control volume energy analysis Overall energy analysis equations Energy analysis of any control volume or the entire system is based on the first law of thermodynamics [9]. Energy analysis (unlike exergy analysis [10]) is independent of the parameters of the ambient (temperature and pressure) in whom analyzed control volume or a system operates [11]. The basic balances in energy analysis are mass flow rate balance [12] and energy balance [13] which can be set for any control volume or a system in steady state (disregarding potential and kinetic energy): � � � out in m m � � , (1) 21
Transcript
STEAM RE-HEATING PROCESS INFLUENCE ON ENERGY EFFICIENCY
AND LOSSES OF TWO-CYLINDER STEAM TURBINE
V. Mrzljak 1, H. Taletović 1, J. Orović 2 and I. Poljak 2 1 Faculty of Engineering, University of Rijeka, Vukovarska 58, 51000 Rijeka, Croatia
2 Department of maritime sciences, University of Zadar, Mihovila Pavlinovića 1, 23000 Zadar, Croatia
Keywords: Steam Re-heating, Steam Turbine, Energy Efficiency, Energy Losses. Abstract: The paper presents an energy analysis of steam turbine with two cylinders and steam re-heater between them from conventional thermal power plant. Steam re-heating process is not performed as usual in such power plants but with one part of the steam delivered in re-heater directly from the steam generator. Observed turbine is analyzed in two operating regimes – with and without inclusion of steam re-heater into the turbine operating process. Regardless of all negative energy effects which steam re-heating process brings into the turbine operation, significant positive effect which compensates all the negative ones is notable reduction of moisture in the steam which expands through the low pressure turbine cylinder. Introduction Steam turbines which operate in conventional thermal power plants use steam re-heating (usually after steam expansion in high pressure cylinder) for increasing the steam temperature before its further expansion in other cylinders [1]. Such process increases the power of the whole steam turbine, decreases whole turbine energy loss and increases energy efficiency of the whole turbine in comparison with the process without steam re-heating [2], [3]. Steam re-heating (heat addition) is in the most of cases performed by additional fuel combustion, while the steam re-heater is usually mounted into the steam generator [4]. Nowadays some power plants, as for example nuclear power plants, also has steam re-heating, but it is combined of two independent processes - the first is moisture separation and the second is steam re-heating by using steam of the highest temperature in the process (a part of steam produced in the steam generators) for heating a steam with lower temperature at the high pressure turbine cylinder outlet [5]. Therefore, nuclear power plants do not use additional fuel for steam re-heating. In this paper the authors find in the literature one (and so far only) conventional thermal power plant which did not have steam re-heating process by using additional fuel combustion - re-heating of steam at high pressure turbine cylinder outlet is performed with one part of steam taken directly from the steam generator. Description and operating characteristics of the analyzed steam turbine with two cylinders and re-heater Analyzed steam turbine consists of two cylinders - High Pressure Cylinder (HPC) and Low Pressure Cylinder (LPC), Fig. 1. Between turbine cylinders is mounted steam re-heater for increasing the steam temperature before its entrance into LPC. Remaining steam after expansion, at the LPC outlet is delivered to steam condenser [6]. The analyzed steam turbine is part of entire conventional thermal power plant presented in [7]. The specificity of such turbine process is the steam re-heating principle, which is not common for conventional thermal power plants. Presented steam re-heating process is usually part of steam re-heating process in nuclear power plants (which included moisture separation and steam re-heating [8]). As usual in conventional thermal power plants, steam re-heating process is performed with heat addition by fuel combustion (regardless of re-heater position). In nuclear power plants, steam which exit from HPC is re-heated with part of steam directly delivered from steam generator(s). Steam turbine analyzed in this paper has the identical re-heating process as nuclear power plant.
Fig. 1 Scheme and operating points of the analyzed two-cylinder steam turbine with steam re-heating between cylinders
Equations for control volume energy analysis Overall energy analysis equations Energy analysis of any control volume or the entire system is based on the first law of thermodynamics [9]. Energy analysis (unlike exergy analysis [10]) is independent of the parameters of the ambient (temperature and pressure) in whom analyzed control volume or a system operates [11]. The basic balances in energy analysis are mass flow rate balance [12] and energy balance [13] which can be set for any control volume or a system in steady state (disregarding potential and kinetic energy):
��� outin mm �� , (1)
21
PhmQhm ������� outoutinin��� , (2)
where: in = inlet, out = outlet, m� = operating fluid mass flow rate (kg/s), h = operating fluid specific enthalpy (kJ/kg), Q� = heat
transfer (kW), P = produced power (kW). Energy power of any operating fluid flow can be defined, according to [14] and [15] as:
hmE �� �� , (3)
where: E� = energy power of fluid flow (kW).
General equation of energy efficiency, for any control volume or a system, is defined in [16] and [17] as:
inletEnergy
outletEnergy�� , (4)
where: � = energy efficiency (%).
Equations for energy analysis of observed steam turbine and both of its cylinders In this paper is used energy analysis of a steam turbine and both of its cylinders which is based on “black box” method [18], [19]. Such analysis does not take into account inner structure or composition of any turbine cylinder, it takes into account only energy flow streams which enters and exits (to or from) any cylinder and the entire turbine [20]. Equations for such energy analysis of the whole steam turbine and both of its cylinders are based on a calculation and comparison of turbine real (polytropic) and ideal (isentropic) power according to turbine operating points from Fig. 1. Used equations in this analysis are shown in Table 1. Similar analyses of several steam turbines are presented in [21] and [22]. Table 1. Equations for the energy analysis of the observed steam turbine and both of its cylinders
HPC LPC WHOLE TURBINE
Real power )()(
)(
a2221
211HPCre,
hhmm
hhmP
����
������
�
)()(
)()(
)()()(
)()(
10998765
988765
8776576
65655LPCre,
hhmmmmm
hhmmmm
hhmmmhh
mmhhmP
�������
�������
��������
������
�����
����
���
���
LPCre,HPCre,re,WT PPP ��
Isentropic power )()(
)(
isa,2is221
is211HPCis,
hhmm
hhmP
����
������
�
)()(
)()(
)()()(
)()(
10isis998765
9isis88765
8isis77657isis6
65is655LPCis,
hhmmmmm
hhmmmm
hhmmmhh
mmhhmP
�������
�������
��������
������
�����
����
���
���
LPCis,HPCis,WTis, PPP ��
Energy loss HPCre,HPCis,HPCL, PPE ��� LPCre,LPCis,LPCL, PPE ��� LPCL,HPCL,WTL, EEE ��� ��
Energy efficiency HPCis,
HPCre,HPC
P
P��
LPCis,
LPCre,LPC
P
P��
is,WT
re,WTWT
P
P��
Symbols in equations presented in Table 1 refer to Fig. 1. Additional symbols, which are not explained so far are: re = real (polytropic), is = ideal (isentropic), WT = Whole Turbine, L = loss. Isentropic steam expansion assumes always the same steam specific entropy, from the entrance until the exit of each turbine cylinder. Steam operating parameters of the analyzed turbine - with and without re-heat process Steam temperature, pressure and mass flow rate in each operating point of the observed turbine from Fig. 1 are found in [7] and presented in Table 2. Table 2 presents steam operating parameters in two analyzed turbine operating regimes - when steam re-heater is not in operation (without re-heating) and when steam re-heater is in operation (with re-heating). Additional steam operating parameters required for the turbine energy analysis are calculated by using NIST-REFPROP 9.0 software [23]. The results of observed steam turbine energy analysis and discussion A comparison of real (polytropic) and ideal (isentropic) power of the whole analyzed turbine and both of its cylinders with and without steam re-heat process is presented in Fig. 2. When observing HPC of the analyzed steam turbine, it can be seen that re-heat process decreases its both isentropic and polytropic power. When compared with the process without re-heating, steam re-heat process influenced HPC of the analyzed turbine in only one way – it reduces the steam mass flow rate which passes through HPC (from 66.58 kg/s to 60.39 kg/s - Table 2) and as a consequence reduces its power (both ideal and real). On the other side, steam re-heating process increases both power of the LPC. Regardless of lower steam mass flow rate which passes through LPC in the process with re-heating (in comparison with process without re-heating), increase in steam temperature and specific enthalpy at the LPC inlet compensate lower mass flow rate. Isentropic and polytropic power of the whole turbine decreases in the process with re-heating (when compared to the process which does not use re-heating) because the intensity of decrease in both power of HPC is higher than the intensity of increase in both power of LPC, Fig. 2.
Reducing of steam mass flow rate which passes through HPC in the process with re-heating reduces energy loss of HPC when compared with a process without re-heating (from 2364.05 kW to 2136.87 kW), Fig. 3. Simultaneously, increasing of steam temperature and specific enthalpy at the LPC inlet during the re-heating usage increases energy loss of the LPC in comparison with process without re-heating (from 3085.33 kW to 3591.83 kW). Comparison of processes with and without steam re-heating for the whole turbine gives as a result that steam re-heating increases energy loss of the whole turbine (from 5449.37 kW to 5728.70 kW), Fig. 3. Similar to ideal and real turbine power, the reason for such occurrence are found in different intensity of change in the energy loss of HPC and LPC.
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Table 2. Steam operating parameters of the analyzed turbine with and without re-heating process [7]
Fig. 2 Re-heat process influence on ideal (isentropic) and real (polytropic) power of the whole analyzed turbine and both of its cylinders
Fig. 3 The influence of re-heat process on energy losses of the whole analyzed turbine and both of its cylinders
Steam re-heating process, in comparison with the process without steam re-heating, decreases the energy efficiency of the whole analyzed turbine and both of its cylinders. In comparison with the process without steam re-heating, inclusion of steam re-heating before LPC resulted with a decrease in energy efficiency of the whole turbine for 0.61% (from 90.83% without re-heating to 90.22% with re-heating), Fig. 4.
Fig. 4 The influence of re-heat process on energy efficiencies of the whole analyzed turbine and both of its cylinders
Presented steam re-heating process resulted with a fact that energy parameters of the whole turbine are worsened, but LPC in first three operating points (operating points 5, 6 and 7 – Fig. 1) operate with superheated steam, only last three operating points has wet steam (operating points 8, 9 and 10 – Fig. 1 and Fig. 5). Steam content in last three operating points of LPC is significantly higher when steam re-heater is in operation (if compared to process without steam re-heating), Fig. 5. With steam re-heating process, steam content at the
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condenser inlet is equal to 85.08%. Therefore, steam re-heating will result with turbine maintenance and reparation after long operation and with much longer periods after which turbine blades will be replaced.
Fig. 5 Change in steam content of LPC with and without re-heating process Conclusions Regardless of all negative energy effects which steam re-heating process brings into the turbine operation, there is one significant positive effect - re-heating process significantly reduces moisture in the steam which expands through the low pressure turbine cylinder. Moisture reduction will result with turbine maintenance and reparation after long operation period and with much longer period after which turbine blades will be replaced. Therefore, all the negative effects of steam re-heating process are compensated with significant increasing of the turbine operation period without any major problems or replacements. Acknowledgment This research has been supported by the Croatian Science Foundation under the project IP-2018-01-3739, CEEPUS network CIII-HR-0108, European Regional Development Fund under the grant KK.01.1.1.01.0009 (DATACROSS) and University of Rijeka scientific grant uniri-tehnic-18-275-1447. References [1] Mitrović, D., Živković, D., Laković, M. S.: Energy and Exergy Analysis of a 348.5 MW Steam Power Plant, Energy Sources, Part A,
32, p. 1016–1027, 2010. (doi:10.1080/15567030903097012) [2] Kostyuk, A., Frolov, V.: Steam and gas turbines, Mir Publishers, Moscow, 1988. [3] Koroglu, T., Sogut, O. S.: Conventional and Advanced Exergy Analyses of a Marine Steam Power Plant, Energy 163, p. 392-403,
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Energy Reviews 56, p. 454–463, 2016. (doi:10.1016/j.rser.2015.11.074) [5] Naserbegi, A., Aghaie, M., Minuchehr, A., Alahyarizadeh, Gh.: A novel exergy optimization of Bushehr nuclear power plant by
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of LNG Carrier, International Journal of Maritime Science & Technology "Our Sea" 64 (1), p. 20-25, 2017. (doi:10.17818/NM/2017/1.4)
[10] Mrzljak, V., Poljak, I., Prpić-Oršić, J.: Exergy analysis of the main propulsion steam turbine from marine propulsion plant, Shipbuilding: Theory and Practice of Naval Architecture, Marine Engineering and Ocean Engineering Vol. 70., No. 1, p. 59-77, 2019. (doi:10.21278/brod70105)
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[12] Mrzljak, V., Poljak, I., Žarković, B.: Exergy Analysis of Steam Pressure Reduction Valve in Marine Propulsion Plant on Conventional LNG Carrier, International Journal of Maritime Science & Technology "Our Sea" 65(1), p. 24-31, 2018. (doi:10.17818/NM/2018/1.4)
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[16] Mrzljak, V., Prpić-Oršić, J., Senčić, T.: Change in Steam Generators Main and Auxiliary Energy Flow Streams During the Load Increase of LNG Carrier Steam Propulsion System, Scientific Journal of Maritime Research 32 (1), p. 121-131, 2018. (doi:10.31217/p.32.1.15)
[17] Poljak, I., Orović, J., Mrzljak, V.: Energy and Exergy Analysis of the Condensate Pump During Internal Leakage from the Marine Steam Propulsion System, Scientific Journal of Maritime Research 32 (2), p. 268-280, 2018. (doi:10.31217/p.32.2.12)
[18] Blažević, S., Mrzljak, V., Anđelić, N., Car, Z.: Comparison of energy flow stream and isentropic method for steam turbine energy analysis, Acta Polytechnica 59 (2), p. 109-125, 2019. (doi:10.14311/AP.2019.59.0109)
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[21] Mrzljak, V., Poljak, I.: Energy Analysis of Main Propulsion Steam Turbine from Conventional LNG Carrier at Three Different Loads, International Journal of Maritime Science & Technology "Our Sea" 66 (1), p. 10-18, 2019. (doi:10.17818/NM/2019/1.2)
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[23] Lemmon, E.W., Huber, M.L., McLinden, M.O.: NIST reference fluid thermodynamic and transport properties-REFPROP, version 9.0, User’s guide, Colorado, 2010.
25
International Conference on Innovative Technologies
IN-TECH 2019
Belgrade
Proceedings
IN-TECH 2019
Proceedings of International Conference on Innovative Technologies
Editors:
� Car Zlatan – Croatia
� Kudláček Jan – Czech Republic
IN-TECH 2019 Organization Committee:
� Car Zlatan – Croatia
� Kudláček Jan – Czech Republic
� Črpić Gordan – Croatia
� Meštrić Hrvoje – Croatia
� Pepelnjak Tomaž – Slovenia
� Elitza Markova-Car – Croatia
� Zoubek Michal – Czech Republic
� Drašnar Petr – Czech Republic
� Anđelić Nikola – Croatia
� Blažević Sebastijan – Croatia
Publisher: Faculty of Engineering, University of Rijeka
University of Belgrade Faculty of Mechanical Engineering
https://www.mas.bg.ac.rs
University of Rijeka Faculty of Engineering
www.riteh.uniri.hr
Czech Technical University in Prague Faculty of Mechanical Engineering
www.fs.cvut.cz
SPONSORS & SUPPORTERS
University of Belgrade http://bg.ac.rs Czech Technical University in Prague Faculty of Mechanical Engineering www.fs.cvut.cz University of Rijeka Faculty of Engineering www.riteh.uniri.hr Central European Exchange Program for University Studies, HR – 108 network www.ceepus.info
SCIENTIFIC COMMITTEE
Ali Hashem, O. (Egypt) Abramov, A (Russia) Bozek, P. (Slovakia) Brdarevic, S. (B & H) Burger, W. (Germany) Car, Z. (Croatia) Carjali, E. (Romania) Carlos Bernardo (Portugal) Castilla Roldán, M. V. (Spain) Cep, R. (Czech Republic) Chen, W. (Netherland) Cizek, J. (Singapure) Cosic, P. (Croatia) Cotetiu, R. (Romania) Crisan, L. (Romania) Czan, A. (Slovakia) Duda, J. (Poland) Durakbasa, N. (Austria) Elhalabi, M. (Egypt) Evin, E. (Slovakia) Frietsch, M. (Germany) Filipović, N. (Serbia) Galvao, J. R. (Portugal) Genis, V. (USA) Gomez, M. E. (Columbia) Greenhut, V. (USA) Guarino, S (Italy) Gyenge, C. (Romania) Hodolič, J. (Serbia) Ivanov, K. (Russia) Jung, J. (Korea) Katalinić, B. (Austria) Kiss, I. (Romania) Klobčar, D. (Slovenia) Kocov, A. (Macedonia) Koršunov, A (Russia) Kozak, D. (Croatia) Kreibich, V. (Czech Republic) Kudláček, J. (Czech Republic) Kundrak, J. (Hungary)
Kuric, I. (Slovakia) Kuzmanović, S. (Serbia) Lee, J. H. (Korea) Legutko, S. (Poland) Li, M. (China) Majstorović, V. (Serbia) Makis, V. (Canada) Mamuzić, I. (Croatia) Math, M. (Croatia) Matsuda, H. (Japan) Miltenovic, V. (Serbia) Ohkura, K. (Japan) Ohmura, E. (Japan) Omran, A (Malaysia) Pepelnjak, T. (Slovenia) Plančak, M. (Serbia) PopIliev, R. (Canada) Raos, P. (Croatia) Rucki, M. (Poland) Sankaranarayanasamy, K. (India) Senabre, C. (Spain) Sercer, M. (Croatia) Serpil, K. (Turkey) Sosnovič, E. (Russia) Suchánek, J. (Czech Republic) Sučić, V. (Croatia) Szalay, T. (Hungary) Šimic, M. (Slovenia) Tingle, J. (Croatia) Tisza, M. (Hungary) Tomesani L. (Italy) Udiljak, T. (Croatia) Ungureanu, N. (Romania) Varga, G. (Hungary) Valentičič, J. (Slovenia) Velay X. (Great Britain) Wilke, M. (Germany) Yashar, J. (Iran) Zivkovic, D. (Serbia)
CONTENTS
EVALUATION TO DETERMINE THE ROUGHNESS OF ADDITIVE MANUFACTURED COMPONENTS BASED ON CT DATA
M. Pendzik, D. Hofmann, S. Holtzhausen and R. Stelzer 1
NEMS RESONATOR FOR DETECTION OF CHEMICAL WARFARE AGENTS BASED ON SINGLE LAYER GRAPHENE SHEET N. Anđelić, M. Čanađija and Z. Car 5
FRICTION MODELING OF ROBOT MANIPULATOR JOINTS
N. Anđelić, I. Lorencin, V. Mrzljak and Z. Car 9
COMPARISON OF EDGE DETECTORS FOR URINARY BLADDER CANCER DIAGNOSTIC
I. Lorencin, B. Barišić, N. Anđelić, J. Španjol, Z. Car 13
TESTING OF ANTISTATICS COATINGS BASED ON WATERBORNE PAINTS
M. Zoubek, J. Kudláček, V. Kreibich, T. Jirout and Z. Car 17
STEAM RE-HEATING PROCESS INFLUENCE ON ENERGY EFFICIENCY AND LOSSES OF TWO-CYLINDER STEAM TURBINE
V. Mrzljak, H. Taletović, J. Orović and I. Poljak 21
EXERGY ANALYSIS OF HIGH-PRESSURE FEED WATER HEATING SYSTEM AT THREE POWER PLANT LOADS
V. Mrzljak, J. Orović, I. Poljak and N. Anđelić 27
THE CHANGE IN EXERGY EFFICIENCIES AND LOSSES OF LOW-POWER STEAM TURBINE WITH STEAM EXTRACTIONS AT THREE LOADS
V. Mrzljak, J. Orović, I. Poljak and I. Lorencin 33
EXPERIMENTAL VERIFICATION OF REMOVAL OF CORROSION PRODUCTS AND OLD PAINT SYSTEMS OF STEEL STRUCTURES
IN PLACES WITH DIFFICULT ACCESSIBILITY
J. Svoboda, J. Kudláček, M. Zoubek and P. Ryjáček 39
COMPARATIVE ANALYSIS OF DISCRETE WAVELET TRANSFORM AND SINGULAR SPECTRUM ANALYSIS IN SIGNAL TREND IDENTIFICATION
D. Nedeljković, B. Kokotović and Ž. Jakovljević 47
INTRODUCTION TO BUSINESS INFORMATION SYSTEM
A. Macura, E. Missoni and B. Makovic 51
DESIGN OF A PARAMETRIC KNEE IMPLANT MODEL FOR PATIENT-INDIVIDUALIZED ADAPTION BASED ON ACTIVE SHAPE MODEL OUTPUT DATA
L. Mika, P. Sembdner, S. Heerwald, C. Hübner, S. Holtzhausen and R. Stelzer 55
ADAPTIVE THRESHOLDING SCHEME FOR THE L1-NORM BASED TIME-FREQUENCY DOMAIN RECONSTRUCTION
I. Volaric and V. Sucic 59
THE USE OF ANYPLEXTM STI-7 IN THE DIAGNOSIS OF DISEASES
M. Trebuňová, M. Gdovinová, Z. Vaczy, P. Frankovský and J. Rosocha 63
SYSTEMATIC SAMPLING FOR VALIDATING A SOLENOID COMMON-RAIL INJECTOR MODEL
J.L. Perona-Navarro, E. Torres-Jiménez, O. Armas and F. Cruz-Peragón 67
VERIFICATION THE LOGISTICS FLOWS IN THE TECNOMATIX PLANT SIMULATION SOFTWARE
M. Pekarcikova, P. Trebuna and M. Kliment 71
HYDROGEN DIFFUSION INTO STEEL DUE TO TUMBLING AND PICKLING
H. Hrdinová and V. Kreibich 75
ASSEMBLY LINE DESIGN THROUGH SOFTWARE TECNOMATIX MODULE PROCESS DESIGNER
J. Trojan, P. Trebuňa, M. Mizerák and R. Duda 79
INCREASING THE EFFICIENCY OF THE MANUFACTURING PROCESS OF THE AUTOMOTIVE COMPONENT ASSEMBLY LINE BY APPLYING THE HOSHIN METHOD VERIFIED BY SIMULATION
M. Kliment, P. Trebuňa and Š. Kráľ 83
PILOT FACTORIES IN THE FRAME OF CENTRE OF EXCELLENCE IN PRODUCTION INFORMATICS AND CONTROL
M. Czampa, T. Szalay, J. Nacsa and M. Nausch 87
MODIFICATION OF WORKSTATION FEATURES OF THE ASSEMBLY LINE IN AUTOMOTIVE VERIFIED BY SIMULATION
M. Kliment, P. Trebuňa and Š. Kráľ 91
ABRASION RESISTANCE OF ORGANIC COATINGS CONTAINING Mg PARTICLES
M. Slovinec, M. Zoubek, J. Kudláček and V Neišl 95
USABILITY INVESTIGATION OF PORTABLE COORDINATE MEASURING EQUIPMENT
M. Gábriel, M. Czampa and T. Szalay 101
INFLUENCE OF FIXTURING SETUP ON QUALITY OF EDGE TRIMMED UD-CFRP
Cs. Pereszlai, N. Geier and D. Poór 105
BULK COATING OF SCREWS BY USING CATAPHORESIS PROCESS
K. Hylák, P. Drašnar, J. Kudláček, M. Pazderová and Z. Matuška 109
THE USE OF TIME SERIES FORECASTING AND MONTE CARLO SIMULATIONS IN FINANCIAL INDICATOR PREDICTION
J. Fabianova, J. Janekova and P. Michalik 113
CHARACTERIZATION PROCESS OF AN EXPERIMENTAL ROTARY DRYER: APPLICATIONS TO THE DRYING OF OLIVE STONE
F.J. Gómez-de la Cruz, J.M. Palomar-Carnicero, A. Camacho-Reyes and F. Cruz-Peragón 117
UV SPECTROSCOPY DACTYLOSCOPIC TRACES RECOGNIZING
P. Drašnar, H. Hrdinová, M. Zoubek, J. Svoboda, P. Chábera, J. Havel and P. Hlavín 121
A PILOT EXPERIMENTAL RESEARCH ON DRILLING OF CFRP UNDER TENSILE STRESS
D. Poór, N. Geier, C. Pereszlai and N. Forintos 125
UNCERTAINTY AND HEURISTICS – SUPPORT OF DECISION-MAKING PROCESS
Z. Kremljak 129
EFFECT OF NICKEL COATED OF CARBON FIBER ON DISTRIBUTION OF CARBON FIBER REINFORCED ALUMINIUM (AlSi7) FOAM COMPOSITE BY POWDER METALLURGY.
F. Damanik and G. Lange 133
TRIBOLOGICAL PROPERTIES OF MODERN COATINGS ON ALUMINIUM
P. Drašnar, M. Chvojka, J. Kuchař, Z. Hazdra and L. Marusič 137
