DESIGN OF BACKWARD SWEPT TURBINE WHEEL FOR CRYOGENIC TURBOEXPANDER

Size: px
Start display at page:

Download "DESIGN OF BACKWARD SWEPT TURBINE WHEEL FOR CRYOGENIC TURBOEXPANDER"

Transcription

1 Journal of Engineering Science and Technology Vol. 9, No. 4 (014) School of Engineering, Taylor Univerity DESIGN OF BACKWARD SWEPT TURBINE WHEEL FOR CRYOGENIC TURBOEXPANDER BALAJI K. CHOUDHURY *, RANJIT K. SAHOO, SUNIL K. SARANGI Department of Mechanical Engineering, NIT Rourkela , Odiha, India *Correponding Author: balajichoudhury@gmail.com Abtract With upport from the Department of Atomic Energy, our intitute ha initiated a programme on development and tudy of a low capacity (0 liter/hr.) turboexpander baed Nitrogen liquefier. Hence a proce deign wa carried out and a turboexpander wa deigned to meet the requirement of the liquefier. The turboexpander i ued for lowering the temperature of the proce ga (Nitrogen) by the ienthalpic expanion. The efficiency of the turboexpander mainly depend on the pecific peed and pecific diameter of the turbine wheel. The paper explain a general methodology for the deign of any type of turbine wheel (radial, backward wept and forward wept) for any preure ratio with different proce gae. The deign of turbine wheel include the determination of dimenion, blade profile and velocity triangle at inlet and outlet of the turbine wheel. Generally radial turbine wheel are ued but in thi cae to achieve the high efficiency at deired peed, backward curved blade are ued to maintain the Mach number of the proce ga at the nozzle exit, cloe to unity. If the velocity of fluid exceed the peed of ound, the flow get choked leading to the creation of hock wave and flow at the exit of the nozzle will be non-ientropic. Keyword: Turboexpander, Turbine wheel, Backward wept blade. 1. Introduction The performance of all cryogenic refrigeration and liquefaction plant mainly depend on the efficiency of turboexpander. The turboexpander i an expanion device where the proce ga i expanded by lowering it temperature at turbine ide and imultaneouly rejecting heat at the brake compreor ide. Hence the dimenion of turbine and it blade profile play a vital role in expanding the proce ga and lowering the temperature of the ga. The turboexpander conit 43

2 44 B. K. Choudhury et al. Nomenclature b Height (nozzle, impeller blade), m C Abolute velocity of fluid tream, m/ C o Spouting velocity, m/ C Velocity of ound, m/ D Diameter, m d Specific diameter, dimenionle h Enthalpy, kj/kg k 1 Preure recovery factor k Temperature and denity recovery factor M Mach number m& Ma of nitrogen flow through turboexpander, kg/ N Rotational peed, rpm n Specific peed P Power output of the turbine, W p Preure, N/m Q Volumetric flow rate, m 3 / Specific entropy, kj/kg K T Temperature, K t Blade thickne, m U Blade velocity (in tangential direction), m/ Z Number of blade Greek Symbol α Abolute velocity angle, radian α Inlet flow angle, radian 0 α Throat angle, radian t α Ma fraction of nitrogen diverted through turboexpander tr β Relative velocity angle, radian η Ientropic efficiency λ Hub diameter to tip diameter ratio tr ρ Denity, kg/m 3 ξ Inlet turbine impeller diameter to exit tip diameter ratio ω Rotational peed, rad/ Subcript o Stagnation condition hub Hub of turbine impeller at exit m Meridional direction max Maximum mean Average of tip and hub min Minimum r Radial direction Ientropic t Throat tip Tip of turbine impeller at exit θ Tangential direction Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

3 Deign of Backward Swept Turbine Wheel for Cryogenic Turboexpander 45 of a turbine impeller and a brake compreor at the two end of a vertically placed haft. The haft i upported by two number of tilting pad journal bearing and two number of aerotatic thrut bearing. The whole component are place inide a bearing houing. At the lower end of bearing houing, cold end houing i attached. The cold end houing conit of nozzle and diffuer. At the top of bearing houing, warm end houing preent. It conit of nozzle to the brake compreor. The ectional view of the turboexpander i hown in Fig. 1 and the deign input parameter are hown in Table 1. Fig. 1. Sectional View of Turboexpander Aembly. Table 1. Deign Input Parameter. Working fluid Turbine inlet temperature, T in Turbine inlet preure, Dicharge preure, Ma flow rate, m& p ex p in Nitrogen 14 K 7.97 bar 1. bar kg/ Working of Turboexpander The proce ga enter from the bottom end and get expanded by paing through the nozzle and turbine impeller and come out from the diffuer. The tate point at nozzle, turbine impeller and diffuer are hown in Fig.. Due to the Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

4 46 B. K. Choudhury et al. ienthalpic expanion of the proce ga the temperature decreae along with the preure. Preure recovery occur due to the preence of diffuer. The T- diagram of the turboexpander expanion proce i hown in Fig. 3. The deign of turboexpander need a fixed tate of proce tream parameter or deign point. The deign point i fixed a per the proce deign done for turboexpander baed Nitrogen liquefier [1]. The literature of deign method for turboexpander [-5] are available for low expanion ratio with purely radial turbine. But the required deign point have high expanion ratio (i.e., 6.64). The high expanion ratio i achieved by uing backward curved vane [6] which increae the tangential force on the blade thereby increaing the turbine peed for higher efficiency. The preent deign procedure ha following characteritic: Deign for any expanion ratio. Deign of radial, backward or forward turbine. Fig.. State Point at Nozzle, Turbine Impeller and Diffuer. Fig. 3. T- Diagram of Turboexpander. Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

5 Deign of Backward Swept Turbine Wheel for Cryogenic Turboexpander 47. Deign of Turbine Wheel The major dimenion of the turbine wheel and it inlet and exit velocity triangle are uniquely determined by the two dimenionle parameter [7], i.e., pecific peed and pecific diameter. The pecific peed and pecific diameter are expreed by the following equation n d Specific peed, = ω Q 3 3/ 4 ( h ) in 3, Specific diameter, ( h ) 1/ 4 D in 3, = () Q3 where Q 3 i the volumetric flow rate at the exit of the turbine impeller and h in-3, i the ientropic enthalpy drop from inlet to the turbine exit. The value of pecific peed and pecific diameter are choen o that Mach number of the fluid at the nozzle exit i maintained at or cloe to unity. If the velocity of fluid exceed the peed of ound, the flow get choked leading to the creation of hock wave and flow at the exit of the nozzle will be non-ientropic. To achieve the maximum poible efficiency within the ubonic zone the pecific peed and pecific diameter are choen o a and repectively. At known inlet input preure and temperature all the ret thermodynamic propertie can be calculated uing property package ALLPROPS [8]. Conidering reaonable turboexpander efficiency of 75%, enthalpy at exit, hex i calculated by following equation, h = h η( h h ) (3) ex in in ex, Power produced, ( ) P = m& h in h ex (4) Q ex and volume flow rate at diffuer exit, = m& / ρ (5) ex The tate at the inlet and exit of the turboexpander are known. But tate at turbine exit are not known. There i the difference between the tate 3 and ex caued by preure recovery and conequent rie in temperature and denity in the diffuer. The two factor k 1 and k are taken in account, where k1 = Q3 Qex (6) and k = ( h h ) h h (7) in 3 in ex, The value of 1 k i aumed to be 1.11 a taken by Ghoh [] and k value i taken a 1.03 from the uggetion of Kun and Sentz [5]. Subtituting the value of (1) Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

6 48 B. K. Choudhury et al. k 1 and k in Eq. (6) and (7) repectively we get, ientropic enthalpy drop from turbine hin 3, and volumetric flow rate at exit of turbine impeller Q 3. Putting the value of hin 3, and Q 3 into Eq. (1) and () give the peed and diameter of the turbine. The velocity ratio i calculated from the ratio of blade velocity to pouting velocity, where pouting velocity, C o 1 h ex, = ( h ) (8) A all radial turbine are found to produce maximum efficiencie over the range of velocity ratio 0.65 to 0.70 [9], the current deign i limit to within limiting value. Rohlik [10] precribe that; ξ the ratio of eye tip diameter to inlet diameter hould be limited to a maximum value of 0.7 to avoid exceive hroud curvature. The value of ξ i taken a 0.6, correponding to the maximum efficiency within the ubonic zone and for obtaining longer blade paage. Again from Reference [10], the exit hub to tip diameter ratio hould be limited to a minimum value of 0.4 to avoid exceive hub blade blockage and energy lo. Kun and Sentz [5] have taken the ratio a 0.35 while Ino et al. [6] have choen a value of For current deign the value of λ i taken a Table give the etimated value of turbine impeller. Table. Etimated Value of Turbine Impeller. Inlet diameter 9.6 mm Rotational peed rpm Eye tip diameter 17.8 mm Hub diameter 8.9 mm Power output 85.3 W Velocity ratio Turbine exit velocitie For mall turbine, the number of blade depend on the hub circumference at exit and availability of diameter of milling cutter. So number of blade i taken Z = 10 []. Conidering uniform thickne of blade i 0.6 mm []. Auming abolute meridian velocity, C m3 and exit angle, α3 a 95 o [6] other velocity component are calculated along with mean blade angle at exit uing following equation. Abolute velocity at turbine exit, C m 3 C3 = (9) inα 3 Abolute tangential component, C = C co( 3 ) (10) θ 3 3 α Relative velocity at turbine exit, W = C + U C U co( α ) (11) Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

7 Deign of Backward Swept Turbine Wheel for Cryogenic Turboexpander 49 β 3, mean = tan C in( α ) U C co( α ) 3, mean 3 3 (1) Flow through turbine ( 3, 3, ) π Zt D D Q3 = C3 in( α3) ( D3, tip D3, hub ) 4 in β tr tip hub 3, mean (13) Comparing the value of Q3 in Eq. Error! Reference ource not found. with the previouly calculated value from Eq. (5), if they are not equal then change the value of C m3 until both the value are equal... Turbine inlet velocitie Aume incidence angle, α a 6 o [3]. The amount of work can be extracted from a turbine i calculated from change in momentum of the fluid in it paage through the turbine impeller. So implifying the energy conervation equation for turbo machine [9], abolute velocity i calculated a C C 1000( h h ) + U C co( α ) = (14) U co( α ) And ret of the velocitie etimated a follow. = C co( α ) (15) θ C = C in( α ) (16) m W = Cm + ( U C θ ) (17) β = tan 1 C m ( U ) C ϑ (18) It can be een from Fig. 4 that the turbine impeller ha backward wept blade. The blade profile ha been worked out uing the technique of Haelgruber [11], which ha been modified for the backward curved vane. Fig. 4. Velocity Triangle at Inlet ant Exit of the Turbine Impeller. Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

8 430 B. K. Choudhury et al. Figure 5 how the different type blade profile. In backward curved blade, u > C coα give a the blade are inclined away from the direction of motion ( ) higher value of blade velocity, u for the given pouting velocity, C0 and nozzle angle. Or, in other word, the ame blade velocity give a lower value of jet velocity compared to other type of blade. Thi permit more preure drop in the nozzle, thu permitting the ue of high expanion ratio within the ubonic zone. Fig. 5. Different Type of Blade..3. Thermodynamic tate at dicharge (tate at 3) Neglecting loe in the diffuer, Stagnation enthalpy at turbine exit, h03 i equal to Stagnation enthalpy at diffuer exit h 04. From the tagnation enthalpy at turbine exit, tatic enthalpy at turbine exit i calculated. The denity wa found out by knowing the value of ma flow and volume flow at turbine exit by following equation ρ 3 = m& / Q 3 (19) From h 3 and ρ 3, all the other propertie at the turbine outlet are calculated from fluid property calculation oftware ALLPROPS [8]..4. Thermodynamic tate at inlet (tate at ) For computing the thermodynamic propertie at impeller inlet (tate ), the efficiency of the expanion proce till tate i aumed. Auming ientropic expanion in the vane le pace, the efficiency of the nozzle along with the vane le pace i defined a h ηn = h in in h h From Eq. (0), taking the nozzle efficiency η n a 93% [5, 6, and 1], the ientropic enthalpy at turbine inlet i calculated. Alo due to ientropic at inlet to nozzle i equal to inlet to turbine, i.e., in = 1 =. Knowing h and, the other propertie at turbine inlet are calculated along with the velocity of ound. Then abolute Mach number at the exit from the nozzle or inlet to the turbine impeller i calculated from the following equation which i to be le than 1 (i.e., ) (0) Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

9 Deign of Backward Swept Turbine Wheel for Cryogenic Turboexpander 431 M = C C (1) / From continuity equation, the blade height at entrance to the impeller i computed from Eq. () a mm. b = m& ( πd Z trttr ) ρ Cm () 3. Concluion The requirement of turboexpander to operate at high preure ratio and with high velocitie for better efficiency a backward curved turbine impeller i deigned. It maintain the Mach number at inlet to the turbine and take care of the velocity ratio (i.e., ratio of blade velocity to the pouting velocity) which i about Reference 1. Alur, S.A.; Choudhury, B.K.; Sahoo, R.K.; and Sarangi, S.K. (010). Simulation of turboexpander baed nitrogen liquefier. Proceeding of the 0 th National and 9th International ISHMT-ASME Heat and Ma Tranfer Conference, January 4-6, Mumbai, India.. Ghoh, P. (00). Analytical and experimental tudie on cryogenic turboexpander. Ph.D. Thei, Indian Intitute of Technology Kharagpur, India. 3. Ghoh, S.K. (008). Experimental and computational tudie on cryogenic turboexpander. Ph.D. Thei. National Intitute of Technology Rourkela, India. 4. Kun, L.C. (1988). Expanion turbine and refrigeration for ga eparation and liquefaction. Advance in Cryogenic Engineering, 33, Kun, L.C.; and Sentz, R.N. (1985). High efficiency expanion turbine in air eparation and liquefaction plant. Proc. International Conference on Production and Purification of Coal Ga & Separation of Air, Ino, N.; Machida, A.; Ttugawa, K.; and Arai, Y. (199). Development of high expanion ratio Helium turbo expander. Advance in Cryogenic Engineering, 37B, Balje, O.E. (1981). Turbomachine. John Wiley and Son. 8. Lemmon, E.W.; Jacoben, R.T.; Penoncello, S.G.; and Beyerlein, S.W. (1995). ALLPROPS 4. Computer program for calculating thermodynamic propertie of fluid of engineering interet. Centre for Applied Thermodynamic Studie, Univerity of Idaho. 9. Blackford, J.E.; Halford P.; and Tantam, D.H. (1971). Expander and pump in G.G. Haelden (Ed.) Cryogenic Fundamental. Academic Pre London, RohliK, H.E. (1968). Analytical determination of radial inflow turbine geometry for maximum efficiency. NASA TN D Haelgruber, H. (1958). Stromunggerechte getaltung der laufrader von radialkompreoren mit axialem laufradeintrict Kontruction (in German). 10(1), Sixmith, H.; and Swift W.L. (1986). Cryogenic turbine and pump in Hand. Cryogenic Engineering Academic Pre, Journal of Engineering Science and Technology Augut 014, Vol. 9(4)

Preliminary Design of Turbine Wheel for High-Speed Cryogenic Turboexpander for Helium Liquefier

Preliminary Design of Turbine Wheel for High-Speed Cryogenic Turboexpander for Helium Liquefier Preliminary Design of Turbine Wheel for High-Speed Cryogenic Turboexpander for Helium Liquefier Mr. Prabeen Kumar Pattnayak Department of Mechanical Engineering Defence Institute of Advanced Technology

More information

The research of simplified method of calculating wind and rain loads and its validation

The research of simplified method of calculating wind and rain loads and its validation The reearch of implified method of calculating wind and rain load and it validation Xing FU 1) and Hong-Nan LI 2) 1), 2) Faculty of Infratructure Engineering, Dalian Univerity of Technology, Dalian 116024,

More information

Alpha College of Engineering

Alpha College of Engineering Alpha College of Engineering Department of Mechanical Engineering TURBO MACHINE (10ME56) QUESTION BANK PART-A UNIT-1 1. Define a turbomahcine. Write a schematic diagram showing principal parts of a turbo

More information

Effectiveness and Exergy Destruction Analysis of Evaporator in Organic Rankine Cycle

Effectiveness and Exergy Destruction Analysis of Evaporator in Organic Rankine Cycle Effectivene and Exergy Detruction Analyi of Evaporator in Organic Rankine Cycle Kyoung Hoon Kim, and Chul Ho Han Abtract---Thi paper carrie out a performance analyi baed on the firt and econd law of thermodynamic

More information

Kalina & Organic Rankine Cycles: How to Choose the Best Expansion Turbine?

Kalina & Organic Rankine Cycles: How to Choose the Best Expansion Turbine? Kalina & Organic Rankine Cycles: How to Choose the Best Expansion Turbine? Dr Frédéric Marcuccilli, Senior Process Engineer Hervé Mathiasin, Sales Engineer Electricity generation from Enhanced Geothermal

More information

[4163] T.E. (Mechanical) TURBO MACHINES (2008 Pattern) (Common to Mech. S/W) (Sem. - II)

[4163] T.E. (Mechanical) TURBO MACHINES (2008 Pattern) (Common to Mech. S/W) (Sem. - II) Total No. of Questions : 12] P1061 SEAT No. : [Total No. of Pages : 7 [4163] - 218 T.E. (Mechanical) TURBO MACHINES (2008 Pattern) (Common to Mech. S/W) (Sem. - II) Time : 3 Hours] [Max. Marks :100 Instructions

More information

T.E. (Mech., Mech. S/W) (Semester II) Examination, 2011 TURBOMACHINES (New) (2008 Pattern)

T.E. (Mech., Mech. S/W) (Semester II) Examination, 2011 TURBOMACHINES (New) (2008 Pattern) *4063218* [4063] 218 T.E. (Mech., Mech. S/W) (Semester II) Examination, 2011 TURBOMACHINES (New) (2008 Pattern) Time : 3 Hours Marks : 100 Instructions : 1) Answer any three questions from each Section.

More information

Minimization of exergy losses in combustion processes with an illustration of a membrane combustion

Minimization of exergy losses in combustion processes with an illustration of a membrane combustion Minimization of exergy loe in combution procee with an illutration of a membrane combution Markku J. Lampinen*, Ralf Wikten, Arto Sarvi, Kari Saari and Marjut Penttinen Aalto Univerity, Department of Energy

More information

CENTRIFUGAL PUMPS e-notes: Dr.N.Balasubramanya Professor, Department of Civil Engineering M.S.Ramaiah Institute of Technology, Bangalore

CENTRIFUGAL PUMPS e-notes: Dr.N.Balasubramanya Professor, Department of Civil Engineering M.S.Ramaiah Institute of Technology, Bangalore CENTRIFUGAL PUMPS e-note: Dr.N.Balaubramanya Profeor, Department of Civil Engineering M.S.Ramaiah Intitute of Technology, Bangalore-5654 A pump i a hydraulic machine which convert mechanical energy into

More information

Exergy Analysis of Organic Rankine Cycle with Internal Heat Exchanger

Exergy Analysis of Organic Rankine Cycle with Internal Heat Exchanger International Journal of Material, Mechanic and Manufacturing, Vol. 1, No. 1, February 21 Exergy Analyi of Organic Rankine Cycle with Internal Heat Exchanger Kyoung Hoon Kim, Hyung Jong Ko, and Se Woong

More information

Notes on the GoldSim Plume Function

Notes on the GoldSim Plume Function NAC-0036_R1 Note on the GoldSim Plume Function Augut 014 Prepared by John auxe NEPUNE AND COMPANY, INC. 1505 15 th St, Suite B, o Alamo, NM 87544 itle: Decription: hi document calculation detail of the

More information

KNOWN: Separate streams of air and water flow through a compressor and heat exchanger arrangement.

KNOWN: Separate streams of air and water flow through a compressor and heat exchanger arrangement. .00 Separate tream of air and water flow through the compreor and heat exchanger arrangement hown in Fig. P.00. Steady-tate operating data are provided on the figure. Heat tranfer with the urrounding can

More information

Principles of. Turbomachinery. Seppo A. Korpela. The Ohio State University WILEY A JOHN WILEY & SONS, INC., PUBLICATION

Principles of. Turbomachinery. Seppo A. Korpela. The Ohio State University WILEY A JOHN WILEY & SONS, INC., PUBLICATION Principles of Turbomachinery Seppo A. Korpela The Ohio State University WILEY A JOHN WILEY & SONS, INC., PUBLICATION CONTENTS Foreword xiii Acknowledgments xv 1 Introduction 1 1.1 Energy and fluid machines

More information

(a) the inlet and exit vane angles, (b) work done (c) Efficiency of the system. [16]

(a) the inlet and exit vane angles, (b) work done (c) Efficiency of the system. [16] Code No: R05310302 Set No. 1 III B.Tech I Semester Regular Examinations, November 2007 HYDRAULIC MACHINERY AND SYSTEMS ( Common to Mechanical Engineering and Automobile Engineering) Time: 3 hours Max Marks:

More information

Evaluating Performance of Steam Turbine using CFD

Evaluating Performance of Steam Turbine using CFD Evaluating Performance of Steam Turbine using CFD Sivakumar Pennaturu Department of Mechanical Engineering KL University, Vaddeswaram, Guntur,AP, India Dr P Issac prasad Department of Mechanical Engineering

More information

Gas Processing Expander

Gas Processing Expander Expander Operated Ga Proceing April, 2015 Ga Proceing Expander Colder Proce Temperature and Maximized Compreor Uptime with Helidyne Expander Skid. Specification: Flowrate 1-10 mmcfd Max. Preure 1,440 pi

More information

The Benefit of Variable-Speed Turbine Operation for Low Temperature Thermal Energy Power Recovery

The Benefit of Variable-Speed Turbine Operation for Low Temperature Thermal Energy Power Recovery Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2014 The Benefit of Variable-Speed Turbine Operation for Low Temperature Thermal Energy

More information

THEORETICAL STUDY OF THERMALLY DRIVEN HEAT PUMPS BASED ON DOUBLE ORGANIC RANKINE CYCLE: WORKING FLUID COMPARISON AND OFF-DESIGN SIMULATION

THEORETICAL STUDY OF THERMALLY DRIVEN HEAT PUMPS BASED ON DOUBLE ORGANIC RANKINE CYCLE: WORKING FLUID COMPARISON AND OFF-DESIGN SIMULATION - 1 - THEORETICAL STUDY OF THERMALLY DRIVEN HEAT PUMPS BASED ON DOUBLE ORGANIC RANKINE CYCLE: WORKING FLUID COMPARISON AND OFF-DESIGN SIMULATION Jonathan Demierre, PhD student, Industrial Energy Systems

More information

SHRI RAMSWAROOP MEMORIAL COLLEGE OF ENGG. & MANAGEMENT

SHRI RAMSWAROOP MEMORIAL COLLEGE OF ENGG. & MANAGEMENT B.Tech. [SEM VI(ME-61,62,63 & 64)] QUIZ TEST-1 Q-1). A jet strikes a smooth curved vane moving in the same direction as the jet and the jet get reversed in the direction. Show that the maximum efficiency

More information

Computational Fluid Flow analysis in Cryogenic Turbo expander

Computational Fluid Flow analysis in Cryogenic Turbo expander Computational Fluid Flow analysis in Cryogenic Turbo expander A Thesis Submitted in Partial Fulfilment of the Requirements for the Award of the Degree of Bachelor of Technology in Mechanical Engineering

More information

Equilibrium Sediment Transport and Evolution Trend Simulation of the Lower Yellow River

Equilibrium Sediment Transport and Evolution Trend Simulation of the Lower Yellow River Senor & Tranducer, Vol. 21, Special Iue, May 213, pp. 135-141 Senor & Tranducer 213 by IFSA http://www.enorportal.com Equilibrium Sediment Tranport and Evolution Trend Simulation of the Lower Yellow River

More information

ANALYSIS OF DIFFERENT TYPES OF REGULATION AND ITS EFFICIENCY IN STEAM POWER CYCLES MASTER THESIS

ANALYSIS OF DIFFERENT TYPES OF REGULATION AND ITS EFFICIENCY IN STEAM POWER CYCLES MASTER THESIS ANALYSIS OF DIFFERENT TYPES OF REGULATION AND ITS EFFICIENCY IN STEAM POWER CYCLES MASTER THESIS Author: Ricardo Sánchez Pereiro Advisor: Piotr Krzyslak Poznan University of Technology 11/06/2012 INDEX

More information

TD 1 BASIC CONCEPTS AND ENERGY ANALYSIS

TD 1 BASIC CONCEPTS AND ENERGY ANALYSIS TD 1 BASIC CONCEPTS AND ENERGY ANALYSIS TD 1.1 Denity of liquid water i r = _ 1008 - T 2 i / m with T in c C. If the temperature increae 10c C, how much will be the change in per meter depth of water?

More information

ORCHID Turbine. Fluid-dynamic design and characterization of a mini-orc turbine for laboratory experiments

ORCHID Turbine. Fluid-dynamic design and characterization of a mini-orc turbine for laboratory experiments Prof. ORCHID Turbine Fluid-dynamic design and characterization of a mini-orc turbine for laboratory experiments M. Pini, C. De Servi, M. Burigana, S. Bahamonde, A. Rubino, S. Vitale, P. Colonna ORC2017-14/09/2017

More information

Code No: RR Set No. 1

Code No: RR Set No. 1 Code No: RR310303 Set No. 1 III B.Tech I Semester Regular Examinations, November 2006 THERMAL ENGINEERING-II (Mechanical Engineering) Time: 3 hours Max Marks: 80 Answer any FIVE Questions All Questions

More information

Radial Turbine Preliminary Design and Modelling

Radial Turbine Preliminary Design and Modelling Radial Turbine Preliminary Design and Modelling Shadreck M. Situmbeko University of Botswana, Gaborone, Botswana; University of KwaZulu-Natal, Durban, RSA; Freddie L. Inambao University of KwaZulu-Natal,

More information

Experimental Investigation of Sediment Trap Efficiency in Reservoirs

Experimental Investigation of Sediment Trap Efficiency in Reservoirs ENGINEER - Vol. XLVII, No. 0, pp. [1-8], 014 The Intitution of Engineer, Sri Lanka Experimental Invetigation of Sediment Trap Efficiency in Reervoir N.M.T.K. Revel, L.P.G.R. Ranairi, R.M.C.R.K. Rathnayake

More information

IS YOUR RADIAL TURBOMACHINERY OPERATING AT OPTIMUM?

IS YOUR RADIAL TURBOMACHINERY OPERATING AT OPTIMUM? IS YOUR RADIAL TURBOMACHINERY OPERATING AT OPTIMUM? Charles C. Solvason and Barry Burr Bryan Research & Engineering, Inc. Bryan, Texas, United States ABSTRACT Bryan Research and Engineering, Inc. (BRE)

More information

Code No: R Set No. 1

Code No: R Set No. 1 Code No: R05310302 Set No. 1 III B.Tech I Semester Regular Examinations, November 2008 HYDRAULIC MACHINERY AND SYSTEMS ( Common to Mechanical Engineering and Automobile Engineering) Time: 3 hours Max Marks:

More information

Thermodynamic Considerations for Large Steam Turbine Upgrades and Retrofits

Thermodynamic Considerations for Large Steam Turbine Upgrades and Retrofits POWER-GEN Asia 2011 Kuala-Lumpur, Malaysia September 27-29, 2011 Thermodynamic Considerations for Large Steam Turbine Upgrades and Retrofits Leonid Moroz, Kirill Grebennik 15 New England Executive Park,

More information

Performance of an Open Ducted Type Very Low Head Cross- Flow Turbine

Performance of an Open Ducted Type Very Low Head Cross- Flow Turbine Performance of an Open Ducted Type Very Low Head Cross- Flow Turbine Zhenmu Chen, Van Thanh Tien Nguyen, Morihito Inagaki, and Young-Do Choi * Abstract Cross Flow Turbine (CFT) known as a Banki turbine

More information

Testing of a 1 kw-class Cryogenic Turboalternator

Testing of a 1 kw-class Cryogenic Turboalternator 426 Brayton Cryocooler Developments 1 Testing of a 1 kw-class Cryogenic Turboalternator D. Deserranno, A. Niblick, M. Zagarola Creare Hanover, NH 03755, USA ABSTRACT Future NASA missions will require hydrogen

More information

Power Recovery in LNG Regasification Plants

Power Recovery in LNG Regasification Plants Power Recovery in LNG Regasification Plants Harry K. Clever Director of Sales hclever@ebaraintl.com Hans E. Kimmel Executive Director R&D hkimmel@ebaraintl.com Ebara International Corporation Sparks, Nevada,

More information

A model for grain growth based on the novel description of dendrite shape

A model for grain growth based on the novel description of dendrite shape ARCHIVES of FOUNDRY ENGINEERING Publihed quarterly a the organ of the Foundry Commiion of the Polih Academy of Science ISSN (1897-3310) Volume 7 Iue 4/2007 183 188 36/4 A model for grain growth baed on

More information

INSTITUTE OF AERONAUTICAL ENGINEERING (Autonomous) Dundigal, Hyderabad

INSTITUTE OF AERONAUTICAL ENGINEERING (Autonomous) Dundigal, Hyderabad INSTITUTE OF AERONAUTICAL ENGINEERING (Autonomous) Dundigal, Hyderabad -500 043 MECHANICAL ENGINEERING ASSIGNMENT Course Name : THERMAL ENGINEERING II Course Code : A50518 Class : III B. Tech I Semester

More information

Challenges of Developing ISO Sampling Standards

Challenges of Developing ISO Sampling Standards Challenge of Developing ISO Sampling Standard Ralph Holme CSIRO Mineral Down Under Flaghip Chair ISO/TC 10/SC 1 Sampling Iron Ore Chair ISO/TC 7/SC 4 Sampling Coal and Coke Convenor ISO/TC 183/WG 9 Sampling

More information

R13 SET - 1 '' ''' '' ' '''' Code No: RT31035

R13 SET - 1 '' ''' '' ' '''' Code No: RT31035 R13 SET - 1 III B. Tech I Semester Regular/Supplementary Examinations, October/November - 2016 THERMAL ENGINEERING II (Mechanical Engineering) Time: 3 hours Max. Marks: 70 Note: 1. Question Paper consists

More information

CERTIFICATES OF COMPETENCY IN THE MERCHANT NAVY MARINE ENGINEER OFFICER

CERTIFICATES OF COMPETENCY IN THE MERCHANT NAVY MARINE ENGINEER OFFICER CERTIFICATES OF COMPETENCY IN THE MERCHANT NAVY MARINE ENGINEER OFFICER EXAMINATIONS ADMINISTERED BY THE SCOTTISH QUALIFICATIONS AUTHORITY ON BEHALF OF THE MARITIME AND COASTGUARD AGENCY STCW 95 CHIEF

More information

Computational Fluid Flow Analysis of Turbine Used in OTEC System

Computational Fluid Flow Analysis of Turbine Used in OTEC System Computational Fluid Flow Analysis of Turbine Used in OTEC System Sonam Nagar 1, H C Thakur 2, Roma singh 3 P.G. Student, Department of Mechanical Engineering, Gautam Buddha University, greater noida, UP,

More information

3.4 BUTT FUSION WELDING

3.4 BUTT FUSION WELDING 3.4 BUTT FUSION 3.4.1 INTRODUCTION The butt welding proce conit of the joining of two component (pipe and/or fitting) of equal diameter and thickne in which the urface to be welded are heated until melting

More information

A Study on the Reduction of Throttling Losses in Automotive Air Conditioning Systems Through Expansion Work Recovery

A Study on the Reduction of Throttling Losses in Automotive Air Conditioning Systems Through Expansion Work Recovery Purdue Univerity Purdue e-pub International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2008 A Study on the Reduction of Throttling Loe in Automotive Air Conditioning

More information

00046 Term-End Examination June, 2015

00046 Term-End Examination June, 2015 No. of Printed Pages : 5 BIME-013 B.Tech. - VIEP - MECHANICAL ENGINEERING (BTMEVI) 00046 Term-End Examination June, 2015 BIME-013 : TURBO MACHINES Time : 3 hours Maximum Marks : 70 Note : Answer any five

More information

Design of a Centrifugal Compressor with Low Specific Speed for Automotive Fuel Cell

Design of a Centrifugal Compressor with Low Specific Speed for Automotive Fuel Cell Proceedings of ASME Turbo Expo 2008: Power for Land, Sea and Air GT2008 June 9-3, 2008, Berlin, Germany GT2008-50468 Design of a Centrifugal Compressor with Low Specific Speed for Automotive Fuel Cell

More information

Level control of small intake reservoir in hydraulic system with long and complex penstock - Implemented level control at Toro 3 HPP

Level control of small intake reservoir in hydraulic system with long and complex penstock - Implemented level control at Toro 3 HPP September 013 Page 1 Level control of mall intake reervoir in hydraulic ytem with long and complex pentock - Implemented level control at Toro 3 PP Damir Dolenc, Mitja Klopčar, Jernej Mazij Litotroj Power,

More information

Up or Out? Economic-Engineering Theory of Flood Levee Height and Setback

Up or Out? Economic-Engineering Theory of Flood Levee Height and Setback Up or Out? Economic-Engineering Theory of Flood Levee Height and Setback Tingju Zhu 1 and Jay R. Lund 2 Abtract: Levee etback location and height are important iue in flood levee ytem deign and modification.

More information

Study of a Supercritical CO 2 Turbine with TIT of 1350 K for Brayton Cycle with 100 MW Class Output: Aerodynamic Analysis of Stage 1 Vane

Study of a Supercritical CO 2 Turbine with TIT of 1350 K for Brayton Cycle with 100 MW Class Output: Aerodynamic Analysis of Stage 1 Vane Study of a Supercritical CO 2 Turbine with TIT of 1350 K for Brayton Cycle with 100 MW Class Output: Aerodynamic Analysis of Stage 1 Vane Joshua Schmitt, Rachel Willis, David Amos, Jay Kapat Center for

More information

semester + ME6404 THERMAL ENGINEERING UNIT III NOZZLES, TURBINES & STEAM POWER CYCLES UNIT-III

semester + ME6404 THERMAL ENGINEERING UNIT III NOZZLES, TURBINES & STEAM POWER CYCLES UNIT-III ME6404 THERMAL ENGINEERING UNIT III NOZZLES, TURBINES & STEAM POWER CYCLES UNIT-III 3. 1 CONTENTS 3.1 Flow of steam through nozzles: 3.2 Continuity and steady flow energy equations 3.3 Types of Nozzles

More information

Research Article Effect of Er +3 Concentration on the Small Signal Gain Coefficient and the Gain in the Erbium Doped Fiber Amplifier

Research Article Effect of Er +3 Concentration on the Small Signal Gain Coefficient and the Gain in the Erbium Doped Fiber Amplifier Reearch Journal of Applied Science, Engineering and Technology (): -, DOI:.9/rjaet.. ISSN: -9; e-issn: - Maxwell Scientific Publication Corp. Submitted: October, Accepted: November, Publihed: April 9,

More information

Deoxidation of Liquid Steel with Molten Slag by Using Electrochemical Method

Deoxidation of Liquid Steel with Molten Slag by Using Electrochemical Method SJ nternational, Vol. 5 (0), No., pp. 767 77 Deoxidation of Liquid Steel with Molten Slag y Uing Electrochemical Method Guo-Hua ZHANG,,) * Kuo-Chih CHU,) and Fu-Shen L,) ) State Key Laoratory of Advanced

More information

Performance of Non-Condensing Steam Turbine by Using Energy and Energy Analysis

Performance of Non-Condensing Steam Turbine by Using Energy and Energy Analysis Performance of Non-Condening Steam Turbine by Uing Energy and Energy Analyi Mr. K.Lavanya, M.Tech Aitant Profeor, Department of Mechanical Engineering, Sanketika Vidya Parihad Engineering College, P.M.Palem,

More information

Eutectic Gallium-Indium (EGaIn): A Liquid Metal Alloy for the Formation of Stable Structures in Microchannels at Room Temperature

Eutectic Gallium-Indium (EGaIn): A Liquid Metal Alloy for the Formation of Stable Structures in Microchannels at Room Temperature Advanced Functional Material Supporting Information for: Eutectic Gallium-Indium (EGaIn): A Liquid Metal Alloy for the Formation of Stable Structure in Microchannel at Room Temperature Michael D. Dickey,

More information

PAPER-I (Conventional)

PAPER-I (Conventional) 1. a. PAPER-I (Conventional) 10 kg of pure ice at 10 ºC is separated from 6 kg of pure water at +10 O C in an adiabatic chamber using a thin adiabatic membrane. Upon rupture of the membrane, ice and water

More information

2. (a) How do you classify water turbines? (b) Define and explain different efficiencies of a water turbine. [8+8]

2. (a) How do you classify water turbines? (b) Define and explain different efficiencies of a water turbine. [8+8] Code No: RR310302 Set No. 1 III B.Tech I Semester Supplementary Examinations, February 2007 HYDRAULIC MACHINERY AND SYSTEMS ( Common to Mechanical Engineering and Automobile Engineering) Time: 3 hours

More information

1.5 DEVELOPMENT OF THE DEPTH AVERAGED GOVERNING EQUATIONS

1.5 DEVELOPMENT OF THE DEPTH AVERAGED GOVERNING EQUATIONS CE 344 - Topic.5 - Spring 2003 - Revied Feruary 3, 2003 3:20 pm.5 DEVELOPMENT OF THE DEPTH AVERAGED GOVERNING EQUATIONS General Conideration We are developing a hierarchy of equation averaged over variou

More information

Reactive Power Management of a Wind Farm to Prevent Voltage Collapse of an Electric Power System

Reactive Power Management of a Wind Farm to Prevent Voltage Collapse of an Electric Power System Reactive Power Management of a Wind Farm to Prevent Voltage Collape of an Electric Power Sytem R. M. Monteiro Pereira Intituto Superior Engenharia de Coimbra, Portugal rmfm@iec.pt C. M. Machado Ferreira

More information

Permanent City Research Online URL:

Permanent City Research Online URL: Read, M. G., Smith, I. K. & Stosic, N. (2015). Comparison of Organic Rankine Cycle Under Varying Conditions Using Turbine and Twin-Screw Expanders. Paper presented at the 3rd International Seminar on ORC

More information

INVESTIGATION OF THERMOSTAT-SET CONTROL AS A NEW DIRECT LOAD CONTROL METHOD

INVESTIGATION OF THERMOSTAT-SET CONTROL AS A NEW DIRECT LOAD CONTROL METHOD INVESTIGATION OF THERMOSTAT-SET CONTROL AS A NEW DIRECT LOAD CONTROL METHOD Canbolat Uçak canbolat@elk.itu.edu.tr Gökçe Dokuyucu gokce776@uperonline.com Department of Electrical Engineering Electrical

More information

SCHOOL OF COMPUTING, ENGINEERING AND MATHEMATICS SEMESTER 1 EXAMINATIONS 2014/2015 ME257. Fluid Dynamics. Answer FOUR out of SIX questions

SCHOOL OF COMPUTING, ENGINEERING AND MATHEMATICS SEMESTER 1 EXAMINATIONS 2014/2015 ME257. Fluid Dynamics. Answer FOUR out of SIX questions s SCHOOL OF COMPUTING, ENGINEERING AND MATHEMATICS SEMESTER 1 EXAMINATIONS 2014/2015 ME257 Fluid Dynamics Time allowed: TWO hours Answer: Answer FOUR out of SIX questions Items permitted: Any approved

More information

Advanced Gas Turbine Concept, Design and Evaluation Methodology. Preliminary Design of Highly Loaded Low Pressure Gas Turbine of Aircraft Engine

Advanced Gas Turbine Concept, Design and Evaluation Methodology. Preliminary Design of Highly Loaded Low Pressure Gas Turbine of Aircraft Engine Proceedings of the International Gas Turbine Congress 2007 Tokyo December 3-7, 2007 IGTC2007 Tokyo TS-058 Advanced Gas Turbine Concept, Design and Evaluation Methodology. Preliminary Design of Highly Loaded

More information

International Journal of Mathematical Archive-8(6), 2017, Available online through ISSN

International Journal of Mathematical Archive-8(6), 2017, Available online through   ISSN International Journal of Mathematical Archive-8(6), 27, 33-38 Available online through www.ijma.info ISSN 2229 546 BAYESIAN SPECIAL TYPE DOUBLE SAMPLING PLAN WITH BETA PRIOR DISTRIBTUTION Dr. S. JEYABHARATHI*

More information

COMBUSTION HEAT RELEASE RATE CALCULATIONS

COMBUSTION HEAT RELEASE RATE CALCULATIONS computation of Net Heat Releae Rate analyi i the combution preure crank angle hitory in the combution chamber. COMBUSION HEA RELEASE RAE CALCULAIONS CHAPER-III HEA RELEASE RAE CACULAIONS Preure crank angle

More information

P _扉_ストレーナー :30 PM ページ 1 Strainer 139 資料-00

P _扉_ストレーナー :30 PM ページ 1 Strainer 139 資料-00 139 Selection 1.0 1.3 2.0 3.0 220 1 220 260 220 220 1 260 260 3 1.0 60 80 152 154 154 156 156 162 1 149 153 153 151 151 162 162 162 163 152 162 158 158 161 161 158 163 160 163 160 157 157 163 1 162 162

More information

Available online at ScienceDirect. Energy Procedia 48 (2014 )

Available online at   ScienceDirect. Energy Procedia 48 (2014 ) Available online at www.ciencedirect.com ScienceDirect Energy Procedia 48 (2014 ) 806 812 SHC 2013, International Conference on Solar Heating and Cooling for Building and Indutry September 23-25, 2013,

More information

Improving Efficiency of Submersible Pump Impeller of Mixed Flow Type by Design Modification through CFD Analysis

Improving Efficiency of Submersible Pump Impeller of Mixed Flow Type by Design Modification through CFD Analysis Improving Efficiency of Submersible Pump Impeller of Mixed Flow Type by Design Modification through CFD Analysis Naveen Nagalinga Lohar 1, Prof. S A Janawade 2. 1Department of Mechanical Engineering (M.Tech

More information

Introduction. Objective

Introduction. Objective Introduction Pelton Wheel Turbine is an impulse or a constant pressure water turbine. In this case water head is very high. Pelton wheel consists of a wheel called rotor. The rotor of the turbine consists

More information

Releasing Compounds Presses Lubrication Grooves Sealing

Releasing Compounds Presses Lubrication Grooves Sealing Acceorie Acceorie Releaing Compound Pree Lubrication Groove Sealing E2.00 29 Acceorie Releaing Compound Releaing Compound SKC C 15 Releaing Compound The releaing compound SKC 15 i a diperion of waxe in

More information

Radial Inflow Gas Turbine Flow Path Design

Radial Inflow Gas Turbine Flow Path Design International Journal of Engineering Research and Development e-issn: 2278-067X, p-issn : 2278-800X, www.ijerd.com Volume 5, Issue 9 (January 2013), PP. 41-45 Radial Inflow Gas Turbine Flow Path Design

More information

International Journal of Advance Engineering and Research Development

International Journal of Advance Engineering and Research Development Scientific Journal of Impact Factor(SJIF): 3.134 International Journal of Advance Engineering and Research Development Volume 2,Issue 6, June -2015 e-issn(o): 2348-4470 p-issn(p): 2348-6406 DESIGN AND

More information

DEVELOPMENT OF A 300 kw e INTEGRATED AXIAL TURBINE AND GENERATOR FOR ORC APPLICATIONS

DEVELOPMENT OF A 300 kw e INTEGRATED AXIAL TURBINE AND GENERATOR FOR ORC APPLICATIONS DEVELOPMENT OF A 300 kw e INTEGRATED AXIAL TURBINE AND GENERATOR FOR ORC APPLICATIONS 2 nd International Seminar on ORC Power Systems: Turbo Expanders II De Doelen, Rotterdam, The Netherlands David Japikse,

More information

Modal Response of Hydraulic Turbine Runners

Modal Response of Hydraulic Turbine Runners 1 (9) Modal Repone o Hydraulic Turbine Runner Q.W. LIANG Center o Indutrial Diagnotic and Fluid Dynamic (CDIF), Technical Univerity o Catalonia, Barcelona, Spain, quanwei@m.upc.edu C. G. RODRIGUEZ Center

More information

Study on Mechanical Behavior of Thin-walled Member during Precision Straightening Process

Study on Mechanical Behavior of Thin-walled Member during Precision Straightening Process 2014 by IFSA Publihing, S. L. http://www.enorportal.com Study on Mechanical Behavior of Thin-walled Member during Preciion Straightening Proce Ben Guan, Yong Zang, Diping Wu, Qin Qin School of Mechanical

More information

Modeling and Simulation of A Laser Deposition Process

Modeling and Simulation of A Laser Deposition Process Modeling and Simulation of A Laer Depoition Proce rank Liou*, Zhiqiang an*, Heng Pan*, Kevin Slattery**, Mary Kinella+, Joeph Newkirk*, and Hin-Nan Chou** *Univerity of Miouri Rolla, Rolla, MO, 65409 **

More information

Value intensity of water used for electrical energy generation in the Western U.S.; an application of embedded resource accounting

Value intensity of water used for electrical energy generation in the Western U.S.; an application of embedded resource accounting Value intenity of water ued for electrical energy generation in the Wetern U.S.; an application of embedded reource accounting Elizabeth A. Martin and Benjamin L. Ruddell Abtract Thi tudy evaluate the

More information

Hydraulic Machines, K. Subramanya

Hydraulic Machines, K. Subramanya Hydraulic Machines power point presentation Slides has been adapted from Hydraulic Machines, K. Subramanya 2016-2017 Prepared by Dr. Assim Al-Daraje 1 Chapter (1 Part 1) Prepared by Dr. Assim Al-Daraje

More information

Mapping of the Range of Operational Conditions for Cu-, Fe-, and Nibased Oxygen Carriers in Chemical-Looping Combustion

Mapping of the Range of Operational Conditions for Cu-, Fe-, and Nibased Oxygen Carriers in Chemical-Looping Combustion Submitted, accepted and publihed by: Chemical Engineering Science 62 (2007) 533 549 Mapping of the Range of Operational Condition for Cu-, Fe-, and Nibaed Oxygen Carrier in Chemical-Looping Combution Alberto

More information

Exergy analysis of a flat plate solar collector

Exergy analysis of a flat plate solar collector Exergy analysis of a flat plate solar collector Sunil Chamoli GRDIMT Dehradun, Uttarakhand, India Abstract In this study, exergetic performance analysis of flat plate solar collector has been carried out

More information

Simulation of the Effect of Bucket Tip Angle on Bucket Splitter of a Pelton Turbine

Simulation of the Effect of Bucket Tip Angle on Bucket Splitter of a Pelton Turbine Research Paper American Journal of Engineering Research (AJER) e-issn : 2320-0847 p-issn : 2320-0936 Volume-03, Issue-11, pp-85-92 www.ajer.org Open Access Simulation of the Effect of Bucket Tip Angle

More information

Advanced Gas Turbine Concept, Design and Evaluation Methodology. Preliminary Design of Highly Loaded Low Pressure Gas Turbine of Aircraft Engine

Advanced Gas Turbine Concept, Design and Evaluation Methodology. Preliminary Design of Highly Loaded Low Pressure Gas Turbine of Aircraft Engine International Journal of Gas Turbine, Propulsion and Power Systems December 2008, Volume 2, Number 1 Advanced Gas Turbine Concept, Design and Evaluation Methodology. Preliminary Design of Highly Loaded

More information

Hydrogen oxygen steam generator integrating with renewable energy resource for electricity generation

Hydrogen oxygen steam generator integrating with renewable energy resource for electricity generation Available online at www.sciencedirect.com Energy Procedia 29 (2012 ) 12 20 World Hydrogen Energy Conference 2012 Hydrogen oxygen steam generator integrating with renewable energy resource for electricity

More information

International Journal of Scientific and Research Publications, Volume 8, Issue 8, August ISSN

International Journal of Scientific and Research Publications, Volume 8, Issue 8, August ISSN International Journal of Scientific and Research Publications, Volume 8, Issue 8, August 2018 314 Flow Analysis of Turgo Impulse Turbine for Low Head Power Plant Hnin Hnin Ei *, Myat Myat Soe ** * Department

More information

Experimental Investigation of Twisted Bladed Savonius Wind Turbine Rotor

Experimental Investigation of Twisted Bladed Savonius Wind Turbine Rotor International Energy Journal: Vol. 5, No. 1, June 2004 1 Experimental Investigation of Twisted Bladed Savonius Wind Turbine Rotor A. S. Grinspan, U. K. Saha and P. Mahanta Department of Mechanical Engineering

More information

UNIT I: UNIFORM FLOW PART B

UNIT I: UNIFORM FLOW PART B UNIT I: UNIFORM FLOW PART-A 1 Define open channel flow with example BT-1-1 2 Distinguish between open channel flow and pipe flow. BT-4-1 3 Compute the hydraulic mean depth of a small channel 1m wide, 0.5m

More information

SHRI RAMSWAROOP MEMORIAL COLLEGE OF ENGG. & MANAGEMENT B.Tech. [SEM IV (ME-41, 42,43 & 44)] QUIZ TEST-1 (Session: )

SHRI RAMSWAROOP MEMORIAL COLLEGE OF ENGG. & MANAGEMENT B.Tech. [SEM IV (ME-41, 42,43 & 44)] QUIZ TEST-1 (Session: ) QUIZ TEST-1 Q.1. In a stage of an impulse turbine provided with a single row wheel, the mean diameter of the blade ring is 80cm and the speed of the rotation is 3000rpm. The steam issues from the nozzle

More information

NUMERICAL SIMULATION AND OPTIMIZATION OF SOLID-LIQUID TWO-PHASE FLOW IN A BACK-SWEPT AXIAL FLOW PUMP

NUMERICAL SIMULATION AND OPTIMIZATION OF SOLID-LIQUID TWO-PHASE FLOW IN A BACK-SWEPT AXIAL FLOW PUMP THERMAL SCIENCE, Year 2017, Vol. 21, No. 4, pp. 1751-1757 1751 NUMERICAL SIMULATION AND OPTIMIZATION OF SOLID-LIQUID TWO-PHASE FLOW IN A BACK-SWEPT AXIAL FLOW PUMP by De-Sheng ZHANG *, Qiang PAN, Hu ZHANG,

More information

Modeling Liquid Phase Sintering of Hard metal powder compacts

Modeling Liquid Phase Sintering of Hard metal powder compacts ing Liquid Phae Sintering of Hard metal powder compact Shama Shamaundar *, Maheha Siddegowda*, Pavanachand Chigurupati**, Rengarajan Raghavan***, Rameh Rao. S. *** * ProSIM AFTC # 326, 8th Main, III Stage,

More information

INCOMPRESSIBLE FLOW TURBOMACHINES Design, Selection, Applications,

INCOMPRESSIBLE FLOW TURBOMACHINES Design, Selection, Applications, INCOMPRESSIBLE FLOW TURBOMACHINES Design, Selection, Applications, George F. Round Professor Emeritus McMaster University Hamilton, Ontario Canada ELSEVIER BUTTERWORTH HEINEMANN Amsterdam Boston Heidelberg

More information

Characteristics of Organic Rankine Cycles with Zeotropic Mixture for Heat Recovery of Exhaust Gas of Boiler

Characteristics of Organic Rankine Cycles with Zeotropic Mixture for Heat Recovery of Exhaust Gas of Boiler Available online at www.ciencedirect.com ScienceDirect Energy Procedia 75 (2015 ) 1093 1101 The 7 th International Conference on Applied Energy ICAE2015 Characteritic of Organic Rankine Cycle with Zeotropic

More information

SCHOOL OF COMPUTING, ENGINEERING AND MATHEMATICS SEMESTER 1 EXAMINATIONS 2015/2016 ME257. Fluid Dynamics

SCHOOL OF COMPUTING, ENGINEERING AND MATHEMATICS SEMESTER 1 EXAMINATIONS 2015/2016 ME257. Fluid Dynamics s SCHOOL OF COMPUTING, ENGINEERING AND MATHEMATICS SEMESTER 1 EXAMINATIONS 2015/2016 ME257 Fluid Dynamics Time allowed: TWO hours Answer: Answer TWO from THREE questions in section A and TWO from THREE

More information

Pumps, Turbines, and Pipe Networks, part 2. Ch 11 Young

Pumps, Turbines, and Pipe Networks, part 2. Ch 11 Young Pumps, Turbines, and Pipe Networks, part 2 Ch 11 Young Pump and Turbine Dimensional Analysis (11.5 Young) Say we want to replace turbines on the Hoover Dam Want to have a good design Essentially impossible

More information

CE2253 APPLIED HYDRAULIC ENGINEERING (FOR IV - SEMESTER)

CE2253 APPLIED HYDRAULIC ENGINEERING (FOR IV - SEMESTER) CE2253 APPLIED HYDRAULIC ENGINEERING (FOR IV - SEMESTER) UNIT I to V QUESTION BANK Prepared by, M.SUGANYA. B.E., LECTURER / CIVIL DEPARTMENT OF CIVIL ENGINEERING CE2253 APPLIED HYDRAULIC ENGINEERING UNIT

More information

= Guide angle = angle between direction of jet and direction of motion of vane/bucket.

= Guide angle = angle between direction of jet and direction of motion of vane/bucket. GEC223: FLUID MECHANICS MODULE 4: HYDROPOWER SYSTEMS TOPIC: IMPULSE TURBINES-PELTON WHEEL DEPARTMENT OF CIVIL ENGINEERING, LANDMARK UNIVERSITY, KWARA STATE, NIGERIA CONSTRUCTION AND WORKING OF A PELTON

More information

VALLIAMMAI ENGINEERING COLLEGE DEPARTMENT OF MECHANICAL ENGINEERING CE6451-FLUID MECHANICS AND MACHINERY UNIT- I: FLUID PROPERTIES AND FLOW CHARACTERISTICS PART-A 1. Find the surface tension in a soap

More information

ENVE 301 Environmental Engineering Unit Operations. CHAPTER: 5 Aeration

ENVE 301 Environmental Engineering Unit Operations. CHAPTER: 5 Aeration ENVE 301 Environmental Engineering Unit Operation CHAPTER: 5 Aeration Ait. Prof. Bilge Alpalan Kocamemi Marmara Univerity Department of Environmental Engineering Itanbul, Turkey 1 Aeration Primary application

More information

Download From:

Download From: Fluid Mechanics 1. A single acting reciprocating pump, running at 60 r.p.m, delivers 0.01 m2/sec of water. The area of the piston is0.05m2 and stroke length is 40 cm. Then theoretical discharge of the

More information

"Leveraging Cross-Industry Know-How for Thermodynamic Cycles & Turbomachinery Component Innovation"

Leveraging Cross-Industry Know-How for Thermodynamic Cycles & Turbomachinery Component Innovation "Leveraging Cross-Industry Know-How for Thermodynamic Cycles & Turbomachinery Component Innovation" Wednesday, June 17, 2015 Stage Presentation ASME TURBOEXPO 2015 1 About SoftInWay Founded in 1999, we

More information

Derivation of Global Parametric Performance of Mixed Flow Hydraulic Turbine Using CFD. Ruchi Khare, Vishnu Prasad and Sushil Kumar

Derivation of Global Parametric Performance of Mixed Flow Hydraulic Turbine Using CFD. Ruchi Khare, Vishnu Prasad and Sushil Kumar Derivation of Global Parametric Performance of Mixed Flow Hydraulic Turbine Using CFD Ruchi Khare, Vishnu Prasad and Sushil Kumar Ruchi Khare Vishnu Prasad Sushil Kumar Abstract: The testing of physical

More information

Design of Radial Turbo-Expanders for Small Organic Rankine Cycle System

Design of Radial Turbo-Expanders for Small Organic Rankine Cycle System IOP Conference Series: Materials Science and Engineering PAPER OPEN ACCESS Design of Radial Turbo-Expanders for Small Organic Rankine Cycle System To cite this article: M Arifin and A D Pasek 2015 IOP

More information

CH 6.docx CH 1.docx CH 2.docx CH 3.docx CH 4.docx CH 5.docx

CH 6.docx CH 1.docx CH 2.docx CH 3.docx CH 4.docx CH 5.docx CH 6.docx CH 1.docx CH 2.docx CH 3.docx CH 4.docx CH 5.docx CH 6 MISCELLANEOUS MACHINES THEORY (1) With neat sketch explain construction and working of hydraulic torque Convertor [643] (2) Write short

More information

UNIT 5 HYDRAULIC MACHINES. Lecture-01

UNIT 5 HYDRAULIC MACHINES. Lecture-01 1 UNIT 5 HYDRAULIC MACHINES Lecture-01 Turbines Hydraulic machines which convert hydraulic energy into mechanical energy. This mechanical energy is used to run electric generator which is directly coupled

More information

Code No: R31034 R10 Set No: 1

Code No: R31034 R10 Set No: 1 Code No: R31034 R10 Set No: 1 JNT University Kakinada III B.Tech. I Semester Regular/Supplementary Examinations, Dec - 2014/Jan -2015 THERMAL ENGINEERING-II (Com. to Mechanical Engineering and Automobile

More information