Let V., V, be the velocities of the wheel at the inlet and l This angle can, if necessary, be corrected to allow for the thickness
outlet surfaces,

vt, v., the velocities of the water, ut, ua the velocities of How,

vf¢, v, ,, the relative velocities, ht, h., the pressures, measured in feet of water, rt, r., the radii of the wheel,

at the angular velocity of the wheel. At any point in the path of a portion of water, at radius r, the velocity 21 of the water may be resolved into a component V=a.r equal to the velocity at that point of the wheel, and a relative component ur. Hence the motion of the water maybe considered to consist of two parts:-(a) a motion identical with that in a forced vortex of constant angular velocity a.; (b) a flow along curves parallel to the wheel vane curves. Taking the latter first, 'and using Bernoulli's theorem, the change of pressure due to How through the wheel passages is given by the equation h't +1'ft”/2g = h'., +v~»'/23;

hli h, o = (vroz "7-lri2)/2g°

The variation of pressure due to rotation in a forced vortex is h". -h"., = (Viz -VJ)/2g.

Consequently the 'whole difference of pressure at the inlet and outlet surfaces of the wheel is

hi -h., =h'¢-!-h”, -h', ,—h".,

= (Viz"'Va2)l/2g+(vro2“Uri2)/2g-Case 1. Axial Flow Turbines.~V¢ =V, ; and the first term on the right, in equation 17, disappears. Adding, however, the work of gravity due to a fall of d ft. in passing through the wheel, ht -ht. = (11.02-mf)/2g-d. (170)

Case 2. Outward Flow Turbines.—The inlet radius is less than the outlet radius, and (Viz -V, ,*)/2g is negative. The centrifugal head diminishes the pressure at the inlet surface, and increases the velocity with which the water enters the wheel. Thisvsomewhat increases the frictional loss of head. Further, if the wheel varies in velocity from variations in the useful work done, the quantity (VE-V., ')/2g increases when the turbine speed increases, and vice versa. Consequently the flow into the tur ine increases when the speed increases, and diminishes when the speed diminishes, and this again augments the variation of speed. The action of the centrifugal head in an outward flow turbine is therefore prejudicial to steadiness of motion. For this reason r, ,:r; is made small, generall about 5:4. Even then a governor is sometimes' required to regulate the speed cf the turbine.

Case 3. Inward Flow Turbines.-The inlet radius is greater than the outlet radius, and the centrifugal head diminishes the velocity of flow into the turbine. This tends to diminish the frictional losses, but it has a more important influence in securing steadiness of motion. Any increase of speed diminishes the flow into the turbine, and vice versa. Hence the variation of speed is less than the variation of resistance overcome. In the so-called centre vent wheels in America, the ratio fi: r, , is about 5: 4, and then the influence of the centrifugal head is not very important. Professor James Thomson first pointed out the advantage of a much greater difference of radii. By making fi2Tg=21I, the centrifugal head balances about half the head in the supply chamber. Then the velocity through the guide-blades does not exceed the velocity due to half the fall, and the action of the centrifugal head in securing steadiness of speed is considerable. Since the total head producing flow through the turbine is H-b, and of this h, -h., is expended in overcoming the pressure in the wheel, the velocity of flow i11to the wheel is v, =c, /{2g(l-I-b-(VF-V02/2g+(v, ,,2-vraz)/2g)}, (18) where ov may be taken 0-96.

From (1441),

of the guide-blades. .

§ 195. Condition determining the Angle of the Vanes at the Inlet Surface of the Wheel.-The single condition necessary to be satisfied at the inlet surface of

the wheel is that the

water should enter the

wheel without shock. - -~ -'- 7- » s Y This condition is satis- 9.

fied if the direction of -'

relative motion of the

water and wheel is

parallel to the first

element of the wheel

vanes.

Let A (fig. 196) be a

point on the inlet surace

of the wheel, and

let 1/5 represent in

magnitude and direction

the velocity of the water entering the wheel, and V; the velocity of the wheel. Completing the parallelogram, vrt is the direction of relative motion. Hence the angle between 21,4 and Vt is the angle 0 which the vanes should make with the inlet surface of the wheel. § 196. Example of the Method of designing a Turbine. Professor James Thomsorfs Inward Flow Turbine:- Let H =the available fall after deducting loss of head in pipes and channels from the gross fall;

Q=the supply of water in cubic feet per second; and 1; =the efficiency of the turbine. The Work done per second is 'qGQH, and the horse-power of the turbine is h.p. =1;GQH/550. If 1; is taken at o-75, an allowance will be made for the frictional losses in the turbine, the leakage and the friction of the turbine shaft. Then h.p. =0-o85QH. The velocity of How through the turbine (uncorrected for the space occupied by the vanes and guide-blades) may be taken uf =u»=o~125/ 2gH,

in which case about, ,14th of the energy of the fall is carried away by the water discharged.

The areas of the outlet and inlet surface of the wheel are then Ztffado =2'lI'fadt =Q/0' 1251/ (2ZH)-If we take r., , so that the axial velocity of discharge from the central orifices of the wheel is equal to u., , we get To (Q//V H)1

do = 7'9-

lf, to obtain considerable steadying action of the centrifugal head, rt =2r, ,, then di =%d, ,.

Speed of the Wheel.-Let Vi =o-66/ 2gH, or the speed due to half the fall nearly. Then the number of rotations of the turbine per "

I7 '~ A

s —

0| OG-i 1

FIG. 196.

second is

N =Vi/27ffg = I'O579/ (Hxf H/Q);

also Va =Vtr../rt =0~33~/ 2,25-Angle of Vanes with Outlet Surface.

Tan ¢ =ua/V.. =o~ 125/o-33 = -3788; ¢> =2I ° nearly.

If this value is revised for the vane thickness it will ordinarily become about 25°.

Velocity with which the Water enters the Wheel.-The head producing the velocity is,

H - (VF/2g)(1 +1402/VF) +1¢-1”/22

=H{1 — I.t1356(1-l-o-o358)+-o156}

=o~5646

Then the velocity is

U.. =v.~/ <1 +u.2/ve). Yf = ~96~/ 2S<'S646H> =°'721~/ HHlt will be shown immediately that Angle of Guide-Blades v~;=utcosec0; " I Sin-y=u¢/°v¢=o~125/o~721=o-173; or, as thisfis olnly a small term, and 0 is on the average 90°, we 'y=IO° nearly. t - f .= . .

may a e, or the present purpose, if., u, nearly. nserting these values, and remembering that for an axial How turbine Vi =V., , l) =o, and the fall d in the wheel is to be added, l.

For an outward flow turbine, E

s si

For an inward flow turbine,

< an

§ 194. Anfle which the Guide-Blades make .with the Circumference of the Whee .—At the moment the water enters the wheel, the radial component of the velocity is ut, and the velocity is vg. Hence, fh'y is the angle between the guide-blades and a tangent to the w ee

1 =Sir1"(ut/vt)-Tangential

Velocity of Water entering Wheel.

wg évfcos 'y =o~7101/El.

Angle of Vanes at Inlet Surface.

Cot 0 =(wt-Vt)/u;=(~7101 -~66)/-125 = -4008; 0 =68° nearly. »

Hydraulic Ejiciency of Wheel.

-q=wtVa/gH==-7I0IX'66X2

=0'9373-

This, however, neglects the friction of wheel covers and leakage. The efficiency from experiment has been found to be 0-75 to o~8o. Impulse and Partial Admission T urbines. § 197. The principal defect of most turbines with complete admission is the imperfection of the arrangements for working with less than the normal supply. With many forms of reaction

turbine the efficiency is considerably reduced when the regulating