It is also expected to change the pressure drop of the and the well-known Cordier diagram [18] the speed of machine by modifying the rotational speed of the rotor. Therefore, the simulation model can be used as an. The calculated speed of rotation is factor will result in very low energy gain.
A reason for that, except the very low head, can be the fact that Cordier diagram, which has been the statistical result of various commercial turbines, is not able to describe the operation of the specific application.
Therefore, a higher rotational speed, at the BEP, will be assumed and fixed. Hydraulic machine selection The selection of the type of the hydraulic machine Fig. Duration of lock process red and energy depends on many criteria, all of which are directly linked to recuperation blue for different values of the turbine the application under consideration.
In the specific case, to overall resistance coefficient predefine the machine type, several quantitative available head, flow rate, rotational speed, cost and qualitative 3.
Best efficiency point BEP factors degree of intervention in the facility, portability, From the results of the simple modelling, a first location must be considered [19].
The main characteristic estimation of the best efficient point BEP or design point of the turbine under design is the very low head. It is a of the turbine can be done for any value of the loss common practice in such applications to use axial reaction coefficient.
The best efficient point is determined by the turbines and more precisely a propeller or Kaplan turbine. As mentioned before, the impeller speed of rotation can to the variation of the flow rate and hydraulic head. At that then be rather easily deduced using the Cordier diagram phase of the study, the transient speed of rotation is which cannot be applied satisfactorily in the case under following the similarity law of Eq.
Therefore, the consideration or a pre-defined fixed value can be used for turbines will always operate at the best efficient point the best efficient point.
However, it will be clear afterwards resulting in high and constant efficiency during the lock that the final selection of the rotational speed will depend on process. The detailed design of the turbines revealed a slight Controlling, thus, the speed with the electrical machine will different filling time, comparing with the results of the result in controlling the flow evolution on the system.
The Additionally, the specific machine is being required evolution of the flow and gross head together with the to be installed with the minimum intervention on the facility, corresponding evolution of the potential power and the meaning no civil works must be required, to be submerged mechanical power are given on Fig. And, of course, economical aspects must be considered in the early phase of the machines selection.
Based on the above criteria a simple non-regulated axial propeller was chosen to be designed for the case under consideration. Detailed design of the turbine 3. The simplest approach to the analysis and design of a hydraulic turbine is to assume that the flow conditions at the mean radius represent the flow at all radii. This two-dimensional analysis can provide a reasonable approximation of the actual flow, if the ratio of blade height to mean radius is small.
The total energy produced is The amount calculated with the and hub was taken equal to 1 m and 0. The efficiency is being calculated by Eq. On the contrary, a rotational speed could be found above which the 3. The rotational speed at design point was always 50 rpm, and the hub and tip radius 0. The best hydraulic efficiency of the turbine be expressed as a function of the speed of rotation and the obtained in Fig. Dividing the mechanical and the recent numerical simulation concerning very low head hydraulic power, an equation for the efficiency can also be turbines and a little bit higher than the efficiencies produced.
This speed can be found by taking the maximum of the power output. The below equation can be used as a tool Fig. Turbine characteristics curves for different flow rates: a power output, b turbine hydraulic head, c torque, d efficiency Fig.
The total energy produced was Therefore, the characteristic curves can these two components. As The converter 2, placed between the DC bus and the introduced above, the turbine will be installed at the inlet or electrical grid, leads to controlling the DC bus voltage at a outlet of the side conduits in order to avoid any civil constant value and the reactive power on the grid with engineering modification and its rotation speed during the sinusoidal current absorption.
The control of the DC bus operation will not be constant. Therefore, whatever the voltage leads to having the electrical grid power equal to the chosen generator and the purpose of the conversion, static power generated by the electrical machine.
Thus, the architecture of 4. Permanent magnet Vernier generator the electromechanical conversion device is similar to those Following the design of the turbine, the chosen used in wind turbines or more specifically in tidal turbines at generator has obviously to fulfil some specifications and variable speed [].
The main differences are relative to constraints. Indeed, its rated speed has to be low in order to the generator to be used and to the most appropriate control avoid any mechanical gearbox and its volume must be for the application studied, due to the atypical character of enough small in order to be housed in the available interior flow of water as a function of time.
These two constraints cannot be In the following sections, the overall scheme of the satisfied at the same time by a classical direct driven electromechanical conversion is first described. Then, the Permanent Magnet Synchronous Machine PMSM as it designed and sized electrical generator is introduced as well requires large pole pair number to satisfy a rated low speed as the control principle adopted. Finally, the models of the different mechanical and Therefore, to reach a high torque at low speed operation electrical parts are coupled and the whole system is while ensuring frequency of the electrical variables at simulated by applying the used control with the aim of standard value, a PM Vernier Generator Machine PMVM extracting the maximum power using variable speed turbine- is designed, which has a simple structure comparing with generator.
The designed prototype is illustrated in Fig. It is an inner stator outer rotor which 4. Electromechanical system provides the possibility to integrate the turbine blades into The whole electromechanical system is illustrated in the latter.
It constitutes of an electrical generator driven by the turbine and two static converters, i. Permanent magnet vernier machine In PMVM, the electromagnetic energy conversion is based on the interaction of armature magnetic field with the Fig. Electrical system illustration one of the rotating magnets which is modulated by the air gap permeance due to the open stator slots. Thus, to reach a In this system, the generator can be either immersed continuous energy conversion at a synchronous speed, a integrated with the turbine or out of water with its shaft special relationship among the rotor PM pole pair number pr, mechanically coupled to the turbine through different the stator winding pole pair number, ps, and the stator slots devices.
In our case, the first solution is chosen for reasons number, Ns, should be satisfied to obtain constant torque of compactness and simplifications of mechanical parts. The extracted power of the turbine With the specifications of the studied application, an varies with flow rate and turbine rotational speed.
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April 16, No Comments. Tags: generator , hydroelectric. Leave a Reply Cancel reply Your email address will not be published. Diy Wedding Card Ideas. Is Giftly A Safe Website. How To Grade Against House. Diy Fume Hood Design. A new nozzle design methodology for high efficiency crossflow hydro turbines Energy for Sustainable Development. RC Adhikari. A short summary of this paper. A new nozzle design methodology for high efficiency crossflow hydro turbines.
Adhikari, D. The predictive capability of the computational model was assessed by comparing the computational and experimental results for the power over a range of operating conditions on both turbines. Published by Elsevier Inc.
All rights reserved. The primary obstacles to the A systematic study was conducted using a two-dimensional 2-D further adoption of such systems are cost and long-term sustainabil- analytical model for the nozzle design and three-dimensional RANS ity. As shown in Fig. The turbine power output was not reported. Since the outer blade angle, b1b , is likely to be close of the two used in this study.
This turbine will be described in the to b1 , only the blade inner angle, b2b , can be chosen to maximize Computational methodology section. These matters will be addressed in a The main nozzle design parameters are the nozzle width, throat subsequent paper on runner design. They continue to do so. Nakase et al. Recent computational studies include Choi et al.
This is the key step in addressing the design problem. None of these studies addresses the need to convert the head into kinetic energy before the runner entry. Choi et al. The remainder of this paper is organized as follows. New nozzle design section presents the new nozzle design methodology, Computational methodology section describes the computational simulations by which we analyze existing nozzle and runner design to establish the accuracy and then analyze the impact of the new nozzle design methodology.
New nozzle design The aim is to determine optimum nozzle dimensions using ana- Integration of Eq. The general- variation out of the page in Figs. The constant nozzle width ized equation for R h with an arbitrary nozzle orientation shown in in that direction, W, is also the width of the runner.
This equation allows the design of a nozzle with arbitrary orientation, and will be used in this study for analyzing which can be written as 1 A curve of the form of Eq. It is noted that this is the same tip speed ratio for optimizing the Pelton turbine when losses in the jet and elsewhere are ignored.
Previous studies have reported satisfactory predic- previous section. For tangential entry, continuity at the nozzle throat h0 and Eq. The gives important geometrical features of these turbines are shown in Figs. Thus the conditions that give the best nozzle performance also give essential information for the runner design. Kerr, P. Responsible for power- house support systems such as intake gates, cranes, service piping, drainage, and fish diversion equipment.
Koepnick, P. Responsible for mechanical engineering and procurement activities for specification and installation of 12 new replacement hydro turbine runners over the past five years.
Responsible for hydrodynamic engineering on research and development of hydro turbines especially Pelton, Francis, Kaplan, and bulb turbines based on year career in Fuji Electric Co. Reese W. S, sales representative Owner of RW.
May Associates with clients in small hydro and nuclear waste management. Charles A. McKee, P. Author, co-author of numerous technical papers and publications. Miller, P. Steve C. Peabody, P. Responsible for hydro generator component assessment and uprate evaluations in the U. Assists customers with technical issues for ongoing and new ABB hydro generator projects. Stanislav Pejovic, P.
Visiting Professor National University of Singapore. Design of three test rigs and 14 hydropower plants, pumped-storage plants, and pumping systems. Hydraulic transient and vibration analysis of 28 hydraulic machines and systems. Model acceptance tests of nine turbomachines. Field tests of 12 and acceptance tests of six power plants. Chief Engincer of final field tests.
Author and co-author of 15 books, technical papers, and six computer programs. Peter, P. Responsible for designs, drawings, and specifications for procurement and instal- lation of large structural steel wheel- and roller-mounted gates and radial gates over a year career. John Pocher, P-E. Responsible for mechan- ical technical services relating to the design and maintenance of projects and pro- grams for hydroclectric generation stations within Power Supply of B.
Hydro with a total capacity of 9, MW. Authored and presented technical papers on heavy mechanical equipment. David N. Raffel, P-E. Furnished practical engineering for hydroelectric and pumping plants, from small hydro to the 10,MW Guri plant, built in 37 states of the U.
Best known for plan- ning power plants and utility systems, and all aspects of selecting, specifying, erecting, testing, and operating the principal machinery. As chief executive, he managed engineering consulting firms in Argentina and in El Paso, Texas, train- ing many engineers. Ritchie, P. Responsible for the Operation and Maintenance of nine hydroelectric developments in the Hudson Valley region of upstate New York.
Co-author of a paper that was awarded Honorable Mention at the Waterpower Conference. Russell, P. Has over 15 years of experience in the hydropower field. Previously, Mr. Russell was involved with standardized turbine product development as an Hydraulic Engineer and was a project manager for the supply and installation of several water-to-wire turbine, generator, and control packages. Seifarth, P. Graduate in mechanical engineering from the University of Maryland.
Registered Professional Engincer in Pennsylvania.
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