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Rebuilding 120" Niles Boring Mill HYDROELECTRIC SITES: Anasagunticook Lake Dam Replacement- C.Fay & W.Fay Appleton Wisconsin Anniversary Senor Bonifettis' sites in Chile Turners Falls Generator Rewind USEFUL ENGINEERING: Admitting Air to Turbine Runners Improves Efficiency, S. Logan Kerr Air Admission to Hydro Runners, David Cox, USCOE, Kerr Dam The Banki Water Turbine Mockmoore and Merryfield Bishops Method- STABGM Program Blade Pitting- Boving LTD 1930 Cavitation- Accelerated Research, Allis Chalmers Research Cavitation & Vibration of a Draft Tube Cavitation- Prevention & Reduction, Allis Chalmers Research Causes & Effects of Cavitation in Hydraulic Turbines Chain Turbine by: Nguyen Minh Duy Chain Turbine Mechanics- Discussions with Duy Characteristics of Modern Hydraulic Turbines-Chester Larner Comparative Tests On Experimental Draft Tubes- C M Allen & I A Winter 1923 Design of an Overshot Waterwheel (by Carl Weidner) Design of Small Water Turbines for Farm and Small Communities Design of the runner of a Kaplan turbine for small hydroelectric power plants: Timo Flaspöhler Draft Tubes of Hydro-Electric Stations by M. F. Gubin Ejection into Tailraces of Hydropower Plants: S. M. Slisskii Erection & Alignment of Vertical Waterwheel Generator Units-R.O. Standing Evolution of Hydraulic Prime Movers-Byron McCoy Fall Increaser Herschel Venturi Tube Fall Increaser Moody Ejector Turbine Fall Increaser Hydraulic Jump Apron Generator Shaft Design Calculation- Olav Hodtvedt Governor Theory for the Plant Operator Graphics of Water Wheels- William Fox Hydraulic Motors- M. Bresse & F. A. Mahan 1869 Hydraulic Turbine and Governor Field Erection Information Hydraulic Turbines- Robert Long Daugherty Hydraulic Turbines by Arnold Pfau Hydraulic Turbines Gelpke & Van Cleve Hydrokinetic Energy in Massachusetts, William D. B. Fay Impulse Turbines by Ely Hutchinson Interference fitting a large runner shaft Kaplan Blade Design NACA Air Foil- Report No. 460 Kaplan Blade Design NACA Air Foil- Report No. 628 Kaplan Design Marko Kogovsek.xls A Laboratory Study to Improve the Efficiency of Crossflow Turbines- N. Aziz & V. Desai Low Head Hydroplants, Emil Mosonyi Meggering Earth Resistance Motors as Generators for Microhydro, Nigel Smith Operation & Maintenance of Hydro-Generators Out Gassing of Cross Flow Turbines Parallel Operation of Turbines Analysis Powerhouse Design- Miniwatt Hydro Rack Design-Chicopee-Olav Hotvedt Rack Design- Hydraulic Institue of Munich Rack Design-Flow Induced Vibrations Selecting Hydraulic Reaction Turbines BUREC Snows Improved Water Wheel Governor Standard for Hydraulic Turbine and Generator Shaft Couplings and Shaft Runout Tolerances Stoplog Structure Design Calculation Stress Analysis of Hydraulic Turbine Parts, BUREC- F.O. Ruud Some Fluid Flow Characteristics of a Cross Flow Type Hydraulic Turbine- Durgin & Fay Tenth Census of the US, 1880, Water Power of the US, Part I- Professor Trowbridge Tenth Census of the US, 1880, Water Power of the US, Part II- Professor Trowbridge Tests on a Kaplan Hydraulic Turbine Theoretical Conditions Related to an Open Channel Flow Linear Turbine- Ishida & Service Theory of Turbines- De Volson Wood Treatise relative to the Testing of Water-Wheels and Machinery, James Emerson 1879 Trash Rack Differential Equations 2L/3 Trashrack Differential Equations General Solution f(x) Turbine Water-Wheel Tests- Robert Horton Turgo, A High Speed Impulse Turbine- Paul Wilson Water Hammer-Lorenzo Allievi-Text Water Hammer-Lorenzo Allievi-Figures Water Hammer-ASME Symposium 1933 Waterpower Engineering-Daniel Webster Mead Water Turbines Contributions to Their Study, Computation and Design-S.J. Zowski TRADE CATALOUGES: Bradway Turbine (progressive gate) Christiana Machine (register gate) Electric Machinery Company (EM) Head Gate Hoists- S. Morgan Smith J & W Jolly (cylinder gate) Lombard Direct-Connected Oil Pressure Governors Bulletin N0. 113 October 1st, 1912 Lombard Governor Company Type T Instruction Book Lombard Governors for Waterwheels and Steam Engines-1902 Lombard Water Wheel Governors Catalouge 26 Ridgway Perfection Water-Wheel Vertical Shaft Water Wheel Driven Generators- General Electric Westinghouse Small Vertical Waterwheel-Driven A-C Generators, July 1944
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Small Turbine Manufacturers Websites: www.waterturbine.com | Chain Turbine Mechanics- Discussions with Duy Chain Turbine Mechanics- Discussions with Duy!!!
How are you? Now I am in Vietnam. And try to write English - Vietnamese Hydroelectric Power Dictionary. I only have a vacation in Vietnam for 1 month. After that I go back Taiwan. Have a nice day! Duy On 6/3/07, Nguyen Minh Duy <duyspar@gmail.com> wrote:
----- Original Message ----- From: Nguyen Minh Duy Sent: Tuesday, June 05, 2007 10:59 PM Subject: Chain turbine
Dear William K. Fay,
Do you have this paper? "Schneider, D. J., et al., 1979, Schneider Lift Translator System, Low Head Hydro Feasibility Study Final Report, Schneider Lift Translator Co., NTIS No. DOE/RA/01693-T1. " Can you send for me a copy of this paper? I cannot buy it, I need this paper to do my final report! I don't have any experience about chain turbine. So It is very difficult. Thank you so much! Duy
Dear Duy: I will try to get a copy of the paper. My son and I have been discussing the design parameters of your turbine. We considered the following:
1) It is a gravity machine. It is also a water motor. The power output is still KW=( efficiency*Q*deltaH)/11.81 2) The speed of the machine can be determined by the average velocity that one bucket volume of water reaches, as it passes from the top of the machine, from where it is filled, to the bottom of the machine, were it empties. Of course this would translate directly into the average velocity of the chain to which the buckets are attached. This is independent of the mass of the object per Sir Isaac Newton. 3) The upper limit of the power of the machine is dictated by P=eff*Q*H. This will be true, if the buckets are large enough to catch all the water passing into the machine. If the buckets are too small, a volumetric inefficiency will result. 4) The gross head across the machine will have to be adjusted. The performance of this type of machine is dramatically effected by the buckets impinging the tailwater (this is called "wading"). In order to not have the buckets drag in the tailwater, you need to have them discharge at a distance above the tailwater. This distance results in a loss of gross head and is an inefficiency of the machine. 5) The velocity of the water entering the buckets should be minimized. It would be best if the water entered from the headrace through a sluiceway or weir. It would be difficult, with the shape of the proposed buckets, to recover much of the intake velocity head. 6) Another inefficiency is the water lost between the filling of each bucket. If the buckets are not closely spaced on the chain, water will be lost between bucket charging. This will probably happen to some extent even with closely spaced bucket and some type of shrouding. This is another type of volumetric inefficiency. As memory serves me: v= dx/dt, a= dv/dt or a= v* dv/dx integrating from vo to v and from 0 to t we have: v= vo+at also vdv=adx, integrating we obtain: v^2=v0^2+2*a*(x-x0) now for your gravity machine, a=g= acceleration of gravity. When you first fill the bucket the machine is at rest so v0=0. The height the buckets drop is deltaX= X-X0= delta H= H so the equation reduces to Vterminal= square root(2*g*H) This is the maximum speed of rotation. The average speed of descent is Vavg= 1/2 Vt In all turbo machines, you can apply a dynamometer to their shaft and measure the torque and rpm. Torque times rpm is power. If you plot the graph of horsepower versus rpm, you will obtain a parabola, that goes to zero power, on either end. This makes sense. If you stall the machine, you have maximum torque but zero rpm and zero rpm*max torque=0 On the other end, the speed of the machine is being countered by the friction in the bearings, which is very small. You have maximum speed but negligible torque and again Maximum speed * minimal torque=0 Now, it is true that this parabola has a maximum and it is in the middle of the parabola. This is the point of maximum horsepower and also the point of maximum machine efficiency. So to obtain your operational speed, to size your pulleys for your motor, take V terminal and divide by 2 again. So, Voperational= 1/4*(2*g*H)^0.5 The RPM of the sprocket would be : revolution/second=Voperational/(phi*d) where V is in meters/second and d=diameter is in meters. I am sure you have already considered a similar analysis. This is a very preliminary and simplified one. You could check these equations on your operational machine. I hope this has been of some help. Sincerely, Bill Fay Thorndike, MA ---- Original Message -----
Dear Duy: In addition, to determine the number of buckets and their volume, one would need to consider the velocity of the chain and the volumetric flowrate entering the machine. If the water is entering at one cubic meter per second and the chain was descending at one meterpersecond and the head was ten meters you would need ten, one cubic meter buckets, on the descending chain, to catch all the water. In order to prevent spillage, I would make the volume of the buckets 20 percent larger. Best regards and have a nice day. Sincerely, Bill Fay ----- Original Message -----
----- Original Message ----- From: Nguyen Minh Duy To: Celeste Fay Sent: Wednesday, June 06, 2007 9:37 PM Subject: Re: Chain turbine Dear Bill Fay: Thank you very much! I try to solve it. After that I will send the result for you! Best Regards, Duy
----- Original Message ----- From: Nguyen Minh Duy To: Celeste Fay Sent: Friday, June 08, 2007 9:51 AM Subject: Re: Chain turbine
Dear Mr. Bill Fay, How are you? I receive both of your email. They are very useful. Thank you! I calculate the chain turbine with flow rate (Q=1 cubic meter /sec) and Head (H = 20 m). The capacity of this plant about 120kW (I assume the efficiency of this system about 0.6). Hope to co-operation more. The end of July, I finish my reports. I am going to co-operation with you to write a Vietnamese-English dictionary. Thank you very much! Duy
----- Original Message ----- From: Celeste Fay To: Nguyen Minh Duy Sent: Thursday, June 07, 2007 7:13 PM Subject: Re: Chain turbine
Dear Duy: Did you receive both of my recent e-mails regarding the machine? I just want to make sure. The first was about the poweroutput and speed of the chain. The second was about the number and sizing of the buckets. They were sent within minutes of each other. The first has more information and I wanted to make sure you received both e-mails. If not I will resend them. Best Regards, Bill Fay
Duy: Xin Chao!!! Cam on for your friendship!! Tam Biet!!! Bill Fay Original Message ----- From: Nguyen Minh Duy To: Celeste Fay Sent: Sunday, June 17, 2007 1:54 PM Subject: Re: Chain turbine again Dear Mr. Bill Fay, Can I ask you again about chain turbine? I send you an my attached file. I solve the design parameters of chain turbine. Could you correct it for me? Last email, you sent me your idea about this turbine with the average speed of descent is Vavg=1/2Vt, but I query, this is only a velocity when water from the jet act on bucket. How about the velocity follow the force of buckets full of water? (have figure in attached file). Could you explain more? About my English, My English is still very poor! Hope you teach me more. I never go to American or countries using the English. Nowadays, Vietnamese can speak English very well. Thank you very much! Best Regards Duy
Dear Duy: Vt is the terminal velocity of the falling bucket if it starts from rest. It is no different from dropping a ball off the roof of a building and calculating how fast it will reach when it hits the ground. The average speed is (Vt^2-V0^2)/2= (Vt^2-0)/2= Vt/^22. This would be the average velocity of the chain if you let the system run away without extracting any power. It is the speed the device would reach if it "ran away" ie: the runaway speed at the far end of the parabola. To find the speed that would be most powerful and most efficient, we would divide that speed in 1/2 again to determine the mid point of the parabola and the best speed of rotation for the system ie: Vt^2/4. I am 53 years old and I come from an old system of engineering that still plaques my country. We think in terms of rpm or revolutions per minute. You are expressing the rotational speed in radians per second. Both notions are correct. I think my analysis is correct. Your pdf file is wonderful. The logic seems accurate and the drawing is beautiful. Did you understand my distinction between the chain turbine being installed on the same head as the height of the chain turbine without it being necessary to recover velocity head versus installing it at the end of a high velocity penstock where it would be necessary to shape the buckets to recover the velocity head. In the first case you have a strict momentum machine. In the second case you would have an impulse machine. Please provide me with a shipping address. I have a 90 year old textbook on hydraulic turbine design by an American engineer called Daugherty that I would like to send to you as a gift. Sincerely, Bill Fay
Dear Duy: We are confused about the head H. Is it approximately the height of the machine like an overshot waterwheel or is it a much higher head with a very large exit velocity for the jet/nozzle. Your analysis is correct and very similiar to a Pelton Wheel analysis if the available head is much more then the height of the machine. If the machine is approximately the height of the dam from headwater to tailwater then my analysis is more correct. If the head is much higher then the height of the machine, the water is going to splash out of the buckets, the energy regained will be from a momentum transfer and the useful work gained from the weight of the water will be minimal. In this case, a Pelton Wheel is much easier to design, build and has less moving parts then your chain drive machine. I need to know more about how you intend to apply/install these machines. I thought that if the distance between the axles was ten meters then you had 11 meters of head. Then the analysis is more like a gravity waterwheel. If the height of the machine is 10 meters and you are operating on 50 meters, then the machine needs to recover the velocity head. You need to turn the jet 180 degrees around in the bucket to recover the head. I need more information! Cam On!!! Tam Biet!!!!
Dear Duy:
It is nice to hear from you. Did you give your presentation on the turbine design? I have spent the last five weeks in Sebec, Maine working on the Sebec Lake Hydro. When I come home on the weekends, Will and I have been replacing a 10' by 10' oak, flood gate at Winchendon. The stems weighed 1400 pounds apiece and we had to drag them across a tiny bridge over the tailrace with a rope, pulleys and my ford truck. The FERC inspector is coming next Monday for the every four year inspection so the kids are frantically cleaning and polishing!!! The message is ready to be sent with the following file or link attachments:
----- Original Message ----- From: Nguyen Minh Duy To: Celeste Fay Sent: Sunday, September 02, 2007 9:17 AM Subject: Fwd: Emailing: final - Report Hydroelectric power plant
Dear Mr. Celeste Fay: How are you? I finished to report my presentation. I send you my presentation. Hope you like it! Duy
Dear Duy: Please see our website with your presentation available to the world!!! Bill Fay
Chain Turbine Design- Link<<<Click here This is a powerpoint presentation and takes a while to download. Please wait. It is worth it!!
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