Design of Turbine Screw Model for Pico-Hydro

American Journal of Engineering Researc (AJER) e-issn: 2320-0847 p-issn : 2320-0936 Volume-6, Issue-9, pp-130-140 www.ajer.org Researc Paper Design of Turbine Screw Model for Pico-Hydro Yulianto 1 *, A.Komarudin 2, B. Priyadi 3, Subiyantoro 4, Fatoni 5 1,2,3,4,5 (Electronic Engineering, Polytecnic State of Malang, Indonesia Corresponding Autor: Yulianto Open Access ABSTRACT: Te total availability of small-scale of potential water resources is enormous and ave different caracteristics. Te rivers in te lowlands are mostly low altitudes but large flow and very long so te total ig is very large, maybe dry or flooded, and maybe clear or contains garbage. Vice versa for mountain areas. To increase te added value, water energy needs to be converted into electrical energy using turbines and generators. Commonly used turbines are waterweels, open flume propeller turbines, and oters. Tese turbines wen applied will ave disadvantages, namely: certain waterfall elevations, not flood resistance, expensive, and lower efficiency. One alternative solution is te use of turbine screw models. In tis turbine a flat flow of water is collected and drained in a rapid pipe in wic tere is a screw-saped rotor. Te purpose of tis researc is to design a screw turbine for pico-ydro wic are resistant to flood, dirty water, can work at low waterfall elevation and ave ig efficiency, Te metod used is teoretical design and test on stream flow. Te design results are tested on te river to obtain te real caracteristics of te turbine. Te results of te data analysis sow tat te screw turbine design results ave an efficiency of up to 80%. Keywords: design, river, turbine screw, pico-ydro ------------------------------------------------------------------------------------------------------------------------ --------------- Date of Submission: 01-09-2017 Date of acceptance: 13-09-2017 ----------------------------------------------------------------------------------------------------------------------------- ---------- I. INTRODUCTION In time, te renewable energy will replace te energy of te fossil. Consideration in te selection of renewable energy tat is availability, environmentally friendly, easy, ceap, and reliable. One of te most renewable energy sources tat is currently concerned is te potential energy of water, because of its availability and environmentally friendly. Te use of small-scale water potential energy began to be developed. Altoug small scale but te number of so muc tat te total energy available exceeds large-scale water potential. Potential water energy sources ave a variety of caracteristics, including varying eigts and discarges, water conditions, and excessive water discarges for a moment Rivers wit an altitude of upstream to downstream can reac undreds of tousands of meters wit discarge up to tens of cubic meters per second, representing an enormous potential energy accumulation. But tis potential energy of water is scattered along te rive. Tis condition provides inspiration for designing compatible turbines for stream flow caracteristics. Te commonly used turbine is a waterweel. Discarge and excessive water levels can damage te waterweel. Te oter type is a floating turbine, altoug it can cope wit water level fluctuations and is suitable for low waterfall elevations, but tis turbine is less tan optimal in energy conversion. Te turbine selected in tis design work is a screw turbine, a turbine wit a screw-saped rotor / blade inserted on te stator of a rapid pipe fitted wit flow guide on te inlet side and nozzle on te outlet side so tat te turbine can be mounted at an elevation close to 0o and drowned. Tis model is resistant to diversified waterfall levels and can be used in low flow velocity of large debit, flood resistance, dirty water (except sand deposits), and no loss of waterfall eigt. Wit careful design, we can suppress te loss of energy caused by turbulent flow, friction losses, and air bubbles. Infrastructure support for te installation of screw turbines is very simple and ceap. Provision of weirs can provide feedback to improve stability of rotation. Screw model turbine development including new model turbines developed by existing bolt turbine development models. In [6] a tresold turbine elevation study was conducted as a variable to te flow of water. Also examine te comparison of pitc distance to rotation. In [7] researc is done wit te empasis of various outer sectional forms (cannels) on treaded turbines. Here it is concluded tat te maximum velocity occurs at te surface of te stream as big as te minimum velocity occurs on te basis of te cannel. In [4] te researc variables are discarge, water flow velocity, turbine rotation, te resulting torque, te magnitude of te efficiency of te w w w. a j e r. o r g Page 130

available potential and te power generated.of te several studies sown above all use a treaded turbine wit a monotonic sape or a perfect tread. No oter innovations.. II. MATERIAL AND METHODS 2.1 Various Kinds of Turbines Based on te fluid momentum cange, te turbine is divided into: 1) impulse turbine by principle generating impulse spin troug decreasing kinetic energy of fluid flow, and 2) reaction turbine wit potential water energy principle converted to kinetic energy. Types of turbines: 1) Te propeller turbine as a blade tat resembles a sip's propeller, mounted on te end of a fast pipe. Turbine propellers wit adjustable blades are called kaplan turbines. 2) Te Turgo turbine is an impulse turbine, te working principle is te jet from te nozzle it te blade at an angle of 20o wit ig rotation speed, 3) Francis turbine wit te working principle, wen water enters te rotor, some ig energy drops water converted into water velocity, te remaining ig energy fall water is utilized using suction pipe to enable ig energy to fall to work in te blade of te road wit te maximum. All te blades are immersed in water. Incoming water is flowed troug a screw-saped ouse. Te turbine generated power is adjusted by canging te opening position of te guide blade. ) Turbine type pelton is a impulse turbine, energy coming into te blade is a kinetic energy. Usually large, ig pressure and momentum canges at te blades are very large. Nozzles are used to regulate te incoming water capacity of te turbine and at te same time convert te pressure energy into kinetic. Pelton turbine ave low power, discarge can be adjusted by sifting te position of te blade needle. Te sape is a rim wit a number of ellipsoidal elbow blades in te seamelline. 5) Oter, te weel is a weel rotated by te water flow. Tis is considered to be te most effective type. Te advantages are ceap, simple, easy to build and ave little impact on te environment. But te efficiency is low, only good used at te speed rate and te water debit is quite eavy. Tread turbineis a turbine type wit treaded blades inserted in te pipe (figure 1) [1]. 2.2 Turbine Analysis Teory Figure 1. Tread Turbine. Figure 2. Difference Pressure of Inlet and Outlet in Vessel Water produces gravity. Heavy force produces ydrostatic pressure (figure 2). Te pressure at te bottom of te vessel due to te fluid as ig as becomes p = ρg. Potential power [2][3] generated by te flow rate and water flow eigt can be formulated (1): P = ρ.q.g. 1 Were: P : water power (Watt) g : gravity (m/s2) ρ : water density (kg/m 3 ) : waterfall eigt (m) Q : water flow discarge (m 3 /s) Wile te pressure difference on te pipe relates te pipe cross section at bot ends tat flows wit velocity v on a pipe expressed by. Bernoulli's Law [4] according to te equation: 1 P ρv 1+ 2 1 2 1 + ρg 1 = P ρv 2+ 2 2 2 + ρg 2 2 w w w. a j e r. o r g Page 131

Figure 3. Flow of Fluid Using Pressure Te flow properties in pipes can be determined by calculating te Reynolds number: R e = DVρ μ Were: R e = Reynolds number D = pipe diameter μ = fluid viscosity vρ = mass flow rate 3 2.3 Power Analysis on Turbine Input power is te sum of losses wit output power. Te total losses incurred in te turbine can be measured in te manner sown in figure. 4. Figure 4. Energy Equations 2.4 Analyze Rotary Speed Turbine Treads Designed wit various treaded densities to obtain turbine rotation speed. Figure 6 sows: 1) 4 treads/meter, 2) 3 treads/meter, and 3) 2 treads/meters. Te closer te number of treads will be obtained te faster te turbine rotation but wit te lower torque. If it is considered tat water flows straigt ten turbine rotary speed is maximum. Turbine Rotation Speed is formulated in equation 4: n max = 60. G treads. V 4 Weres: n max : maximum rotation (rpm) g treads : te number of treads per mete V : speed of water flow (m/s) g ulir = 4 ulir g ulir = 3 ulir g ulir = 2 ulir Figure 5. Definition of Number of Treads Per Meter Wile te resulting torque depends on te diameter of te turbine. Particular construction to consider is te rotor diameter and te pipe diameter of te turbine wit te same cross-sectional area. Here is an example illustration. Figure 6.a) as a large diameter, but wit te same marking area as te figure 6.b) small diameter. To obtain optimal work required a value of comparison between te number of treads and te diameter of te w w w. a j e r. o r g Page 132

turbine rotor. Figure 7 sows te prediction of turbine design values wit a certain dimensional ratio to obtain optimum output power wit mecanical energy values. Te circular cross-sectional area is πr 2 L0, wereas te area of te circular penamapang between te radius of R D to R L is: πr 2 L - πr 2 D, tus: Torque: r L = r L0 2 + r D 2 5 r τ = π P L r 2 dr 6 r D Figure 6. Comparison of Rotor Diameter On te Same Effective Cross-sectional Area Figure 7. Torque and Turbine Rotation Speed Figure 7 is a curve of teoretical analysis of te cange of torque to te rotor diameter canges of tree turbines wit different discarge capacities. Te dased line sows te limits of te curve linearity. 2.5 Flow Analysis on Rapid Pipes Rapid pipe or also called a nozzle on turbine screw as an excessive lengt of lengt compared to oter types of turbines. Incorrect lengts and elevations of turbine installation can cause turbine work to be less effective ie at te turbine tail may be empty air space, as sown in Figure 8. Altoug turbines can still work, but te presence of empty space indicates tat te turbine not working maximally or sowing te lack of waterfall in eiter water discarge or ydrostatic pressure. To overcome tis incident a turbine model wit a cone sape is decoded, as sown in Figure 9. But, te speed of water in te pipe is not te same. Figure 8. Empty Space on te Back of te Turbine w w w. a j e r. o r g Page 133

Figure 9. Tread Turbine Wit Pipe Conical Model III. BASIC DESIGN 3.1 Construction and Design Variables Treaded turbine and arcimedes screws are well suited for propulsion in ydropower wit low waterfall and large discarge. Variable design of treaded/screw turbine is pitc, cylinder pipe radius (R0), tread lengt (L), and tread slope (K), treaded saft diameter (Ri), number of blades (N), water discarge per cycle tread. Wit a good design, efficiency can be acieved between 79 to 84%. Figure 10 sows te construction of a screw turbine wit a unique sape. Tis form is designed for a variety of reasons. Figure 10. Turbine Screw Te installation of te turbine is orizontally submerged so tat no air enters into te turbine. Te tip of te rotor is made taper wit a widened pipe widened in order tat tere is no wirlpool tat can draw air into te turbine. Te front-side tread as a wider pitc over te inner edge used to condition te flow of water and is designed according to te local water velocity. On te back side wit a uniform pitc inside a fast pipe tat resembles a nozzle to obtain steady speed and stability. Figure 11. Level of River Water and Turbine a) Sectional Area of Te Front Side of Te Turbine and Area of Te River, b) Simple Weir Te design of te fast pipe diameter adjusted wit te available water discarge. Calculated from te cross-sectional area of river water is equal to or greater tan te area of te pipe cross section to keep te turbine always submerged in water. Tis can be done wit te addition of a simple weir as sown in figures 11.a and 11.b. Te speed of te water flow can be used to calculate te speed of te turbine. Te design of te number of blades per unit lengt adjusted to te need for turbine rotational speed. Te calculation of effective water ead (s) is equal to te difference between te river water level in front of te weir wit te water level beind te weir. If te cross-sectional area of te river flow is 0.15 m 2, ten te pipe diameter of te front side is: π w w w. a j e r. o r g Page 134

(r Doutside ) 2 = 0.22 meters wit te front rotor diameter is considered zero. Te diameter of te back side quick pipe is set at 0.38 meters wit te inner side rotor diameter of 0.10 meters, so te comparison of front and rear side cross-sectional area is: A ratio = ((r 2 Doutside r 2 Dinner)/(r 2 Boutside-r 2 Binner). =((0,22 2 0)/(0,18 2-0,1 2 ))= 2,16 If te river water velocity is 0.5 m/s and is considered equal to te velocity of te water in te front side pipe, ten te flow rate of water in te back pipe is 1.08 m/s. Tis speed as a stable tendency because if te water flow rate decreases ten te water level will rise and increase te ydrostatic pressure bigger, vice versa. If te expected turbine speed is 300 rpm or 5 rps, ten te number of blades per meter is: N blade = N rotation /V water = 5/1 = 5 blade/meter Tis is te minimum blade amount, due to slip, friction, and load causing te rotation to drop by 50%, maybe, so te amount of blade required is 10 blade/meter or wit a 10 cm pitc. In te same way te blade distance of te front side of te pitc is 22 cm. Figure 12 sows te number of blades and pitces required 80 cm FLOW DIRECTION 19 cm 15cm 12 cm 10 cm 10cm Figure 12. Blade Structure Based on Pitc Figure 13 sows te results of te screw turbine production according to te design results. Te connecting gear to te generator is mounted on te depat side due to te low water flow rate. On anoter occasion, te generator will be installed inside te rotor saft. Figure 13. Screw Turbine Production Results 3.2 Calculation of Power Availability For calculation of power availability, it is necessary to define te waterfall eigt (). In accordance wit image 2 ten te so-called waterfall eigt is te difference in te eigt of te water level of te front and rear of te turbine. Figure 14. Determination of Altitude and Zero Point Wile water velocity is calculated witout friction, is V (t) = 2g and te result is sown in figure 15. w w w. a j e r. o r g Page 135

Figure 15. Waterfall Speed Various Altitude Te turbine's turning speed is very ig by te airfall. Wile turbine rotational speed can be calculated using te equation nmax = 60. η. Gblade. V, and te results in figure. 16 Figure 16. Turbine Rotation Rate at Waterfall Heigt Minimum ydrostatic pressure occurs wen te eigt of s = r2doutside r2boutside = 0.44-0.36 = 0.08 meters. In tis condition te entire turbine is submerged in water and no air enters te turbine. If te water level is less tan 0.48 meters above te base of te turbine ten tere are some turbine blades tat are not subjected to pressure so tat te turbine is not working optimally. Te stresses are: P = ρg = 0.784 N/m2. Te flow of water flow along te pipe is te same. If te velocity of te uniform flow in one of te cross-sectional areas, ten te water discarge Q is te multiplication of te velocity of water flow wit te cross-sectional area of water, ie Q = AV. For D = 0.44 meters wit V = 0.5 m / s, ten Q = 0.076 m3 / s. Te potential power generated by te discarge and flow eigt of water is P = ρ.q.g. = 0.06 watts. Te result of power output analysis as a function of altitude is presented in table 1 Note: Tabel 1. Daya Output Turbin Fungsi Ketinggian No. KETINGGIAN s (meter) ALIRAN *) V D_aliranr (m/s) DEBIT AIR Q (m 3 /s) DAYA OUTPUT P (kw) **) 1. 2. 3. 4. 5. 6. 7. 8. 9. 10 0,1 0,2 0,3 0,4 0,5 0,6 0,7 0,8 0,9 1,0 3.0240 4.2766 5.2377 6.0480 6.7619 7.4073 8.0008 8.5532 9.0720 9.5627 0.4026 0.5694 0.6973 0.8052 0.9002 0.9862 1.0652 1.1387 1.2078 1.2731 0,395 1,116 2,050 3,156 4,411 5,799 7,307 8,928 10,653 12,477 *) Using te free fall equation wit Vo = 0 m / s **) Turbine output power wit efficiency is assumed 100% 3.3 Discussion of Design Results Tere are two ways of turbine in te field, namely a) using a simple weir to obtain potential energy of water (Figure 12.a), b) direct installation (figure 12.b). To keep te effective ead maximally utilized, te installation of te turbine is recommended as sown in Figure 17.a. Tis will also ave better speed stability. w w w. a j e r. o r g Page 136

Figure 17.b sows a mounting model wic prioritizes kinetic energy to be converted to mecanical energy by te turbine. Tis metod as a tendency to ave a unstable rotation, lose ead because te friction also becomes larger. (a) (b) Figure 17. Turbine Installation(a) Models of Simple Bend Usage, (b) Direct Installation Mode Figure 18 sows one problem: te contour of te river is widened so tat it is not suitable for te implementation of te turbine type of te design result, due to te still large number of unused water discarge in te energy conversion process. Increased efficiency is done by using a lot of tubin altoug it is still less effective Figure 18. No Compatible River Flow Figure 19. Alternative Installation of Turbines at Te Waterfall(a) Vertically, (b)horizontally Te waterfall as a large enoug potential/kinetic energy. Figure 19 sows two ways of mounting a turbine on a field tat as a waterfall. Te mounting metod sown in Figure 19.a as many disadvantages: muc water does not pass troug te inside of te turbine, air can enter te turbine, te majority of wic is only kinetic energy converted to mecanical energy, and unstable turbine spinning. All tese losses will decrease te efficiency of energy conversion, besides tat turbines are not designed for suc treatment. It is terefore recommended tat te mounting procedure as sown in figure 19.b be treated according to te design of te turbine in terms of rotational stability and energy conversion ie te conversion of potential energy. 3.4 Data retrieval Metod Figure 20 sows te data retrieval metod. Te measurement of te waterfall eigt is measured by te refres of te water level puddle on te back side of te turbine. Te speed of te flow of water in te turbine at te cross-sectional position terein is considered uniform, altougt te top or bottom side because te turbine as been designed so. More accurate data retrieval will be obtained if it is done wit a eigt of more tan one meter so tat all ripples (less tan 10 cm) tat occur can be ignored. But tis is not done because all te equipment is less meet te safety standards w w w. a j e r. o r g Page 137

Gambar 20. Metoda Pengambilan Data Te results of turbine design and manufacture are tested under actual conditions. Ten take te data as follows: 1) Te water falling eigt canges wit zero turbine spin, ten recorded te torque. 2) Te eigt of te water fall turns and te turbine spins free to get turbine rotary speed wit no load 3) Turbine is loaded (retaining) ten measured retention and rotation speed IV. DATA AND DATA ANALYSIS 4.1 Data Testing Results Te efficiency (η s ) of te turbine rotation is te difference in te velocity of water flow to turbine rotation rate. If te flow of water moves straigt is not affected by te turbine spin ten it is defined η s = 1. Tis event can ardly occur because te beavior of water is very easy to move in all directions. Table 2 sows te turbine rotation rate values teoretically by using te free fall equation. Tis approac is done because it is still difficult to find a reference to analyze te case. For ease of observation ten it is presented for rotation efficiency value from 0.5 to 0.9. If te power (P) is in kilowatts and te rotational speed (N) in rpm, teoretically te torque generated by te turbine can be calculated using te equation: τ = (975 x P) / N and te result is sown in table 2. Hig Waterfall (cm) 0,1 0,2 0,3 0,4 0,5 0,6 0,7 0,8 0,9 1,0 Table 2. Teoretical Torque and Rotate Rate Teoretical Rotation Rate (rpm) Teoretical Torque Generated (Nm) η s =0,5 η s =0,6 η s =0,7 η s =0,8 η s =0,9 η s =0,5 η s =0,6 η s =0,7 η s =0,8 η s =0,9 210 252 294 336 378 4.39 3.66 3.14 2.74 2.44 296 356 415 475 534 8.78 7.32 6.27 5.49 4.88 363 436 509 582 654 13.17 10.98 9.41 8.23 7.32 420 504 588 672 756 17.56 14.63 12.54 10.98 9.76 469 563 657 751 845 21.95 18.29 15.68 13.72 12.20 514 617 720 823 925 26.34 21.95 18.82 16.46 14.63 555 666 777 889 1000 30.73 25.61 21.95 19.21 17.07 593 712 831 950 1069 35.12 29.27 25.09 21.01 19.51 630 756 882 1008 1134 39.51 32.93 28.22 24.70 21.95 664 796 929 1062 1195 43.90 36.59 31.36 27.44 24.39 In table 3 sown data measurement results bot conditions, witout load or burden. N = 0 means tat te data obtained is static torque, and τ = 0 means tat te measurement is carried out under no-load conditions and te turbine is allowed to run free. In taking tis data tere are some variables tat are difficult to observe, namely: initial velocity of inlet, flow velocity in turbine, and final velocity of discarge stream. At larger speeds will also increase turbulence on te front and rear of te turbine, but inside te turbine does not occur te process of cavitation. Te measured variables are te average flow rate in te turbine, te resulting torque, and te rotational speed, respectively in some conditions. No 1. 2. 3. 4. 5. 0,30 0,40 0,50 0,60 0,70 Table 3. Result Measurement Data of Torque, Rotation Speed Versus Head N = 0 τ = 0 τ (N-cm) Q (%) V(m/s) V N (rpm) 19 70 THE THE 126 46 90 DIFFERENCES DIFFERENCES 208 86 100 OF SPEED IS OF SPEED IS 231 132 100 HARD TO BE HARD TO BE 272 170 100 KNOWLEDGE KNOWLEDGE 311 w w w. a j e r. o r g Page 138

Weres: τ N V : waterfall eigt (cm) : torque (Nm) : speed of rotation (rpm) : flow rate (m/s) Observation of te loading on te turbine, in fact, if te turbine is loaded so tat te measured torque to live 9 N-cm turned out to decrease te speed to 96 rpm. Te problem wit tis measurement is te difficulty of determining te constant load (te load always canges) so tat its appointment at te torque meter is also always on te move, tis cange is less visible on te rotation. Tis occurs wen te measurement is a cycle count, wereas te cange in te occurrence of cycles occurs in eac cycle, so tat counts remain te number of cycles per minute 4.2 Analisa Data In te design of tis turbine te flow of water on te inlet side is considered calm and as no speed wit unlimited volume and constant level. In fact, te flow of water as ad speed before entering te turbine, tis is an advantage. Te speed will accelerate and accelerate wen it enters te turbine caused by te ydrostatic pressure of te water itself and te suction power of te turbine blades If it is said tat te rotational speed of te turbine of te screw arcimedes is not affected by te operating conditions [7] it must be treated by te ideal conditions approac. But in reality in lapanggan will be very different and te condition is no longer ideal as it as been done in te laboratory. Some difficulty factor factors sould be considered specifically for turbines to work optimally, even increasing turbine efficiency, or optimizing available waterfall energy. In order to acieve maximum power, it sould be noted tat te mounting elevation, in addition to te turbine as been designed to ave a certain elevation still needs to be rearranged in its installation by increasing te slope of te turbine slope to about 10 degrees. Te front side of te turbine is made wit a slope of 80 degrees, so it resembles an aerodynamic sape. Te addition of a turbine slope tat is not too large can increase te performance of te engine because te flow of water does not veer sarply. Tis Kimiringan as been linked in its design and manufacture. Te addition of a suction pipe on te back side may also be required depending on te field conditions. Te caracteristics of tis turbine are very good and suitable for river rivers wit low slope and waterfall. Tis type of turbine rotation does not ave a meaningful oversot, it also as good stability at certain loading limits, but te condition will be worse if te load increases in excess because it can cause direct rotational speed will decrease drastically. In non-rotating conditions will lose considerable torque compared to spinning conditions. Precisely wit te addition of flyweel wit a moment of great inertia will increase oversot. Terefore, it is preferable tat turbines be loaded wic may cause a reduction of turbine rotary speed not more tan 10% to rotation at zero load (considered maximum rotational speed). In tis area will ave optimal output power wit good stability. Altoug te 10% rotation range and efficiency rates of up to 80% in tis study are not perfect and less accurate, tis is important information for te continuation of subsequent researc. Tese accurate figures do not appear in te measurement data, but te numbers are close to te trut. Oter numbers tat can be utilized from te results of tis study is te comparison of te maximum turbine rotor rotational speed (as if te water goes straigt / does not follow te turbine flow) to te reality round is between 0.5 to 0.7 and tis does not mean tat te value in te middle- te middle of wic is 0.6 is te most correct value. Te data is suitable for te design turbine wit a 10 cm uniform pitc wit a treaded amount of 3 pieces positioned in a fast pipe / nozzle and 4 screw pieces wit a distance of a series of diameter conical wit position inside te collecting pipe. Designed turbine as te following disadvantages: 1) less precision wic can lead to te formation of a wide intercept between te blade wit a fast pipe resulting in wasted stream and can cause waste or oter objects to be spilled witin te sidelines between te blade and te wall rapid pipe, 2) incomplete ratio of front and rear side diameter ratios causing te front side turbulence and turbulence on te back, and 3) te occurrence of loss of falling water altitude caused by incorrectly installed turbine elevation. If te back side is depressed it will reduce te nozzle effect, but if not drown will lose te eigt of falling water as ig as te pipe diameter of te back side. Suc conditions can be overcome by te addition of suction pipe on te back side. V. CONCLUSION 1) To avoid te occurrence of abnormal flow sould be used rapid pipe construction in two parts, namely te nozzle and collector/conditioning side wit te distance of te blade on te rotor (pitc) is not te same but te measuring row adjust te position in te pipe rapidly. 2) Te speed of turbine rotation is influenced by te number of treads per unit lengt wose value is limited by flow velocity and form factor along wit oter friction on te turbine. Te value of te ratio between te w w w. a j e r. o r g Page 139

maximum speed of te rotor rotation (teoretical rotation of te flow of water straigtly/does not follow te turbine blade flow) of te reality cycle is 0.5 to 0.7. 3) Te ratio of te area of te inlet and out side turbine sections sould be greater tan 2 times, and te installation of turbines wit a 10 degree slope to improve turbine performance and reduce turbulence on te turbine discarge side. 4) Turbine will work optimally if te torque and speed of rotary turbine output is selected comparison between fast pipe diameter/nozzle and turbine rotor diameter (turbine saft) wose value is limited from te availability of waterfall energy Implications It is necessary to design a turbine wit easily modifiable construction to adjust te waterfall availability beavior and facilitate te setting of necessary parameters in order to obtain te most optimal level of efficiency. Tank-you note Acknowledgments submitted to te Directorate of Researc and Community Service Directorate General Strengtening Researc and Development Kemenristek and Higer Education troug te Institute of Researc and Community Service Polytecnic State of Malang wo as provided financial aid and trust REFERENCES [1] A Nurul Suraya, N M M Ammar, and J Ummu Kultum,, Te Effect of Substantive Parameters on Te Efficiency of Arcimedes Screw Microydro Power, 3rd International Conference of Mecanical Engineering Researc (ICMER 2015), IOP Conf. Series: Materials Science and Engineering, 2015 [2] B. Andersson, R. Andersson, L. Hakansson, M. Mortensen, R. Sudiyo, B. van Wacem, L. Hellstrom, 2012, Computational fluid dynamics (CFD), Cambridge University, Press, First Edition. [3] Erino Fiardi,, Preliminary Design of Arcimedean Screw Turbine Prototype for Remote Area Power Supply, Journal of Ocean, Mecanical and Aerospace, Science and Engineering-, Vol.5, 2014, 30-33. [4] Muliadi, Erna Wijayanti Raayu, 2016, Te design of a Very Low Head Tturbine as a Microydro Power Plant, Media Bina Ilmia, Vol. 10 No. 4, page 64-68. [5] Murray Lyons, William David Lubitz, Arcimedes Screws for Microydro Power Generation, Proceedings of te ASME 2013 7t International Conference on Energy Sustainability & 11t Fuel Cell Science, Engineering and Tecnology Conference ESFuel Cell 2013. Canada,. 1-7. [6] Nur Kamdi, Amnur Akyan, 2014, Effect of Pitc on Turnover On Screw 3 Wind Turbine, Journal of Electrical and Computer Engineering, Vol. 2, No. 2, 2014, 181-188, [7] Zulkiffli Sale, M. Fauzan Syafitra, Power Comparative Analysis of Carrier Cannels for Arcimedes Tread Turbine Supply, Simposium Nasional Teknologi Terapan (SNTT) 4, Palembang,2016, * Yulianto Design of Turbine Screw Model for Pico-Hydro American Journal of Engineering Researc (AJER), vol. 6, no. 9, 2017, pp. 130-140 w w w. a j e r. o r g Page 140