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HYDRAULICS BRANCH
OFFICIAL FILE COPY HYO-
FILE COPY BUREAU OF R�CLAMfaTlON HYDRAULIC Lh30r�"�EY
NOT TO BE REMOV.E;D 1·RO/vi .t1 IJ..,I<;ia
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UNITED STATES DEPARTMENT OF THE INTERIOR
BUREAU OF RECLAMATION
HYDRAULIC LABORATORY REPORT NO. 113
STUDIES TO DETERMINE SUITABLE METHODS FOR STARTING AND STOPPING THE PUMPS
IN THE GRANBY PUMPING PLANT COLORADO-BIG THOMPSON PROJECT, COLORADO
By
J. N. BRADLEY FRED LOCHER W. A. MORGAN T. F. HAMMET
Denver, Colorado June l 5, l9ij2
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.,.
UNITED �TATES DEPARTMENT OF T'-fE INTER! OR
BUREAU OF RECI.AM!t. TION
Branch of Design a.nd Construction Engineering and Geolo6ioal Control
and Research Division
Denver, Colorado
July 20, 1945
Laboratory Report No. 113 Hydraulic laboratory Compiled by1 J. N. Bradley
Fred Locher w. A. Morgan T. F. Hammett
Reviewed bys J. E. Warnook
Subjects Studies to detennine suitable methods for starting and stopping the pumps in the Granby pumping plant.
CHAPTER I - INTRODUCTION ilID SUMMARY
Introduction
le Description of Granby pumps. Four pumps Will be utilized in
the Granby pumping pla.nt to raise water from the Grl!,Ilby Reservior to
the Shadow Mountain Reservoir for diversion through the Colorado-Big
Thompson transmountain tunnel. A plan and elevation of the pumping
plant is shown in fi5ure 1-<and profile of the piping is shown on figure
2. Water will be supplied to eaoh pump through a 66-inch square suction
tunnel approximately 750 feet long. Eaoh discharge line will consist
of a. 78-inoh circular oondui t approximately 3,000 feet long. Flow
through the latter will be controlled by a hydraulically operated but
terfly valve looated in close proximity to the pump. An automatic,
electrically operated e.ir valve near the outlet of the dleohe.rge line
will break any baok-siphonio aotion developed by sudden shut-down of
a pump.
It is proposed to operate the pumps at two speeds, 300 and 327
r.p.m., the speed depending on the head to be overcome at any partic
ular time. Due to expected :fluctuations in the water surfaoe elevation
in Granby Reservoir, it will be necessary for the pumps to operate
against heads ranging from 96 to 201 feet. Eaoh pwnp, as proposed,
will discharge 240 second-feet of water at 162 feet of head at maximum
efficiency and 300 r.p.m., or 180 second-feet at 210 feet of head at
naArly maximum efficiency for a speed of 327 r.p.m. The performa.noe
curves for this pump are shown on figure 3. The pump impellers will
--measure about 88 inches in dil:lmeter and will be driven by two-speed
synohronous motors of approximately 6,000 horsepower eaoh.
2. Fur.pose of tests. Tests were made to determine whether the
undesirable oondit:i.ons experienced at simi.lar pumping inste.l latione,
when the pumps a.re started under load, oould be alleviated. These
large motors would require five times the normal running current for
starting under load at full voltage which would be sufficient to cause
dimming of lights on the oonneoted system an.1, under certain condi
tions, the rate of increase of power input required by the motors
would exceed the rate of response of the generators as limited by
penstook or turbine governor oapabili ti As. Four remedial methods -
two eleotrioal and two hydraulic • were proposed for these conditions.
In all four oases it was planned to force the water out of the
volute by admittinb compressed air. Thus on startinb, the impeller
would rotate in a.ir requiring only e. fraction of the power necessary
to start it rotatiDt; in water. In the first scheme, the impeller
would be started in ai r and broutht to rated speed by an �uxiliary
motor. With the correct speed attained, the main pump motor would be
synchronized With the line voltage and the main switoh closed. The
remainder of the starting procedure then would be to slowly exhaust
the entrapped air from the volute allowing gre.due.l submergence of the
impeller. At full submergence, the butterfly valve would automati
oe.lly begin to open slowly admitting water to the discharge line.
Thus the load would be applied progressively and the rate of increase
of power input would depend largely on the timing of the operation.
The second method of startinb a pump electrically would be as in
the first case with the exception that the auxiliary motor would be
eliminated and the pump started by applyi?\_; a fraction of the rated
voltage to the main motor to bri� it up to speed •. At rated speed,
the motor would be synchronized with the line volta&e by closing the
field switch at wh· oh time full voltage would be applied. With this
method, the shook to the electrical system would be reduced to a small
quantity sinoe the power input varies with 't,he square of tti3 voltage•
The two hydraulic methods consist of bringing the pump units to
operati:t1c speed by the use of hi6h-ve1ooity jets impinging on a bucket
2
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assembly connected to the pump shaft. The remainder of the starting
prooedure would be the same as for the other methods. The first method
would be to mount a Pelton wheel on the pump shaft in a case separate
from that of the pump impeller. With this arre.n�ement there would not
be any interference with the impeller action since the buckets would
rotate in air under normal operating conditions. The second arrange
ment would be to mount the buckets on top of the impeller behind the
seal rings but inside of the impeller oase. This report deals prima
rily with the latter :roothod of starting.
Summary
3. The starting and shut-down cycles with buckets on the impeller.
The procedure developed for ste.rtillf.; the pumps by the use of hydraulic
jets impillbing upon buckets c·1t in the topside of the impeller was sat
isfaotory as far as reducini-; the shock to the eleotrical system was oon
oerned. As shown on figures 18.A and E, the increase in power was grad
ual, and the time required for the power to increase was sufficient to
allow the generati� apparatus to respond to the increase in load. A
limited amount of control oan be exercised over this rate of power in
orease by regulating the rate at which the compressed air is released
from the pump volute. However, the buckets in the impeller created a
disturbance when the pump we.s operating under load that reduced the
over-all effioienoy about four percent. The test data showed about
two peroent decrease of disc�arge, figure 22, and a three percent in•
crease of power input, fi&ure 14, at the maximum discharge. This de
oree.se in effioienc,,r in a larg;e unit would be su fficient to make the
arrangement impractical•
In the shut-down cycle, where the power was reduoed from full load
to zero load, fi£ure 18B, the reduction in current was gradual end
there were no ob,iectionable hydraulic pressures o The fluctuations in
pressure at t�e intake, as shown by the trace of No. 3 pressure oell
(No. 3 p.c.), are characteristic of any pump, and the frequency is
related to the a.peed and the number of vanes on the impeller, The
current is not a reliable index of the power as ma:,r be seen by
3
comparing the c urrent trace of figure 18B vdth the power trace of
figure 19D. It is evident that while the current showed a gradual
reduction, the fluctuation in power was considerable due to the loca
tion of the port throuch whioh the compressed air entered the pump
volute, figure 7B.
4. !!:!_bypass and the air port. The bypass is necessary regard•
less of the auxiliary starting device tha.t may be employed. If' a de•
vioe is used whereby buckets are cut into the impeller, the bypass
diameter would be controlled by the quantity of waterJssuing from the
jets. It must be large enough to al low the je-t war.er to e soape with
out producing any considerable amount of hee� to be established in
the pump volute. If an auxiliar y Pelton wheel is used as a separate
un:-it, a drain will be necessary to remove the jet water end, in addi•
tion, a bypass must be provided from the discharge side to the pump
intake. If an auxilia�y motor or the low-voltaf;e sc�eme is used with
the regular motor, a bypass is necessary although it is desirable to
have it smaller in the latter three oases.
The location of the air-suppl:,, port directly a.ffeots the smooth
ness of operation and the form of the ;;ower curve during the shut-down
cycle. With the port located at the discharge side of the pump, there
were definite power surges, figure 19D, but with the location oha.nt;ed
to the intake, figure 7A, the power curve was smooth as shown on figure
190. From this it was evident that the air-supply port should be on
the intake side and placed to distribute the air evenly in the fluid
before it enters the impeller. The exhaust port should be located in
the system su ch that there will not be any trapped uir in the piping
when the ma.in discharge valve is opened.
5. Electrical power required a.t sta.rti� There is a decided ad
vantage, from the standpoint of the initial amount of power required,
in starting the pump with the water depressed belo-vr the impeller.
Figure 17 shows that the power required to rotate the impeller of the
test pump with air in the volute was aboot 10 percent of the full-load
value whereas, with water in the pump case and with the dis charge valve
closed, the power requ�red to drive the pump motor was about 53 peroent
4
of full load. Since it is desired to reduoe the shook to the eleotrioal
system when the motors are started, the use of compressed air will be a
material aid regardless of the method of starting.
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CHAPTER II • PUMP TES TS
Laboratory .Arrallgement of Test E4uipment
6. The teat pump. The test pump (show.n in figures 4, 5, 6, 7 1
and 8) was not oonaidered a.a a model of the proposed Granby pumps ex
cept in the sense that it was of the same general type. This, however,
was not of great importance as the experimentation centered about the
starting and stopping cyeles. Table 1 shows a oomparison of the test
pump and prototype dim&nsions giving the scale ratio for each. The
general proportions of the two pumps can be studied from figures 1 and
6 and the pumping oharaoteristios of the two are shown on figures 3 and 9.
TABLE 1 Comparison of Teat Pu.mp Dimensions with Prototype
Test Simili-Prototype
Item dimensions
Area of suction line, sq.ft ••• 30.2.5 Diameter at discharge flange, rt. ••••••••••••••••••••••••• 6.50
Diameter of impeller, rt. •••• 7.33 Depth of impeller passage at
periphery, rt. •••••••••••••• Capacity of motor, hp. ••••••• 6,000 Speed of pump, r.p.m. • ••••••• 300 and 327
Ce.pa.city of pump at maximum effieiency, see.-rt ••••••••• 240 and 180
Head developed at mexirnum effioieney, rt. •••• •••••.• ,. 162 and 210
Peripheral speed of impeller,
pump dimen-sions
0.493
0.67 1.026
0.208 15 875
tt. per sec. •••••••••••••••• 115 .2 a.nd 125.6,,.47 .o Diameter of bypass, rt. • ...•.••...•..•..........
Diameter of air--exh&ust pipe, tt. ••••·••••••••••·••··•·•••
Diameter of air-supply pipe, ft • •••••••••••••••••••••••••
Effective diameter of jet nozzles, ft. ••••••••••••••••
Velocity of jets, at 110-pound line pressure, ft. per sec • •
0.167
o.os2
0.023
0.0208
99.4
6
tude Soale ratio, relation- N
ship
Am'N". 7.84
LN
LmN PmN3•5 5.54 SmN-0•5a.so and 7.15
5.89 and 7.64
VyJI0.5 6.01 and 7.15
LmN
1mN
ImN
LmN
V. ?P .5 m
The test equipment (figure -6A) consisted of a tank reservoir, 3
feet in diameter by 12 feet high, to which was connected a tre.naparent
pyralin auction pipe and elbow (figure 6B). This in turn was oonneot•
ed to the intake of the single-suotion, eight-inch, closed-impeller.
vertical test pump. An eight-inoh tee and valve were oonneoted to the
di1oharge side of the pump. The valve corresponds to the butterfly
valve location in the prototype. An air intake, controlled by a small
:needle valve, and an air-exhaust line, controlled by a quiok-aoting
cook, were oonneoted into the top o.f the eight-inoh tee (figure 7B).
The top of the pump impeller was altered as shown in figures 5 and
8A by cutting into it thirty buokets, 1/4-inoh deep by 1.5 inohes in
diameter at an angle of 20 defrees with the horizontal. To do this, it
wa1 first neoessary to sweat on a 3/16-inch brassplate to the top of the
impeller to obtain sufficient thickness of metal to out the buckets.
The buokets were out on a milling machine using a 1/4-inoh by 1½,.1nch
keyseat cutter. The four jets which propelled the impeller oonsieted
of 3/8-inoh inside-diameter copper tubes inserted through the top cover
of the volute at an angle of 20 degrees (figure 5). Short inserts
with 1/4-inoh bore were soldered into the ends nearest the buckets to
form the jet nozzles and 3/4-inch hose oonneotora were fitted to the
opposite enda. ,Four 3/4-inoh garden hoses (figure 6B) were oonneoted
from the latter to a main header in which water preaeures from 36 to
110 p0ll1ld8 per square inch oould be developed.
A. two•inoh bypass pipe and valve were instel led between the eight
inoh tee and the transparent suction line as oan be observed in figures
6B, 7A, and '1B, the main purpose of which was to relieve pressure•
oreated in the volute by the we. ter di sohargj ng from the jets ·8'nd the
rotation of the impeller. The bypass served a secondary purpose of
allowing a s�ll amount of' circulatlon for cooling during the interTa.l
when the pump would be running under load with the butterfly valve
olosed. This circulation is very essential in the prototype.
The r emainder of the apparatus consisted of a return pipe from
the pump discharge to the tank reservoir in which was installed a. six
inch venturi meter for iooasuriD(c; the discharge (figure 6A).
7
7. Instru.mentation. Three t:h.ermomenters were installed in the
apparatus to provide an aocurate record of the temperatures throughout
a. test J one in the tank reservoir• one in the eight•inoh tee• and the
third on the pump motor.
To detect pressure fluotuations. which ooourred at various points
throughout the operating cycle, four oarbon�pile pressure oella (fig•
ure 12) were incorporated in the test equipmentJ one in the tank reser•
voir (figure 7A). a seoond in the transparent auetion line elbow (fig•
ure 6B), a. third in the eight-inoh tee. and the fourth in the discharge
line downstream from the butterfly valve (figure 7B).
The recorded pressure traoe transmitted by the eleetrioal ourrent
from the oells is based on the pressure-resistance oharaoterietios of a
series or pile of earbon disks connected by a piston to a sprirl{; brass
diaphragm which is &btuated by the actual pressures at tJ,e point in
question. This type of oell was used in two branches of a direot•
current bridge to which an oscillograph element was connected as an
indicating device. The cell was adjusted a�d oalibrated such that the
def'leotion of the osoillograph trace was a !lleasure of the pressure on
the diaphragm.
The electrical measurements on the test pump motor, were made With
an ammeter, voltmeter, W&ttmeter, watt-hour meter. and the osoillograph.
The diagram of electrical connections for the instruments is shown on
figure 13. The osoillograph was used to observe current and Toltage to
the JJ1,Qtor. and the voltage element was use� e.s e. timing W&.ve.
The indioating wattmeter gave a means of observing the rate of in
oreaae or deorease of power as air waa released from or foroed into
the pump volute. 'l'his wa.s of value since the motor power ohange on
the prototype would af£eot the governor action at the genera�ing sta
tion. Since the power faetor of the induction motor varied from 18 to
80 percent between no load and ful.l load• the eurrent wave on the
osoUlogram.s was of little value in studying power changes. The os-
oillograph as not equipped with a power element.
A watt-hour mete� and stop we.toh were used to obtain the power
where accurate values were required, sinoe the power input as shown by
the indicating wattmeter fluctuated oonsiderably. Uthough the
e
laboratory vo ltage varied continually. the power input to the motor
flu ctuated principally be cau se of the roUGhness in the pump ' s running
perfo rme.noe. Therefore, by timine; the number of revolutions of the
watt•hour zm ter over a period of a.bout two minutes, the average power
over trat period was obtai ned. The power equation for the conneoti ons
s hown on figure 13 , using the watt-hour meter and a stop wa.toh, is a.a
follows a
Watte • (Revolutions) (C.T. ra tio) (K) ( 31600) • Rev. ( l ,ZOO)
Seconds Seo.
The power to the three-phase motor was measured by one s in{, le•
phase wattmeter instead of the usual two wattmeters by aasuminf:; the
power in the three phases to be equally divided. In order to measure
the power in one phase of the three-phase motor , it was ne cessary to
use the l ine-to-ground voltage instead of the line-to-line V0 ltage ,
as shown on fi gure 1 3 .
Because of its val ue as a timer, i t was desirable to use the osoil•
lograph to determine the best place to force the e.ir into the pump
volute as far as controlling the rate of power deorease waa oonoerned.
In order to obtai n a power traoe on the osci l lograms a.a eho,vn on figure
19 , a slide wi re rheostat was mounted directly over the wat'bneter in &
position very cl ose to the wattmeter indi cator and s cale. Sin ce the
slide Wire was oonneeted to an element on the oaoillograph it was
possj_ble to manually .follow the we.ttmeter i.nd i oator w.i th the elide
wire and thereby obt ain a de fle ction of the oscillograph e lement corre
sponding to the we.ttmeter reading. It was poesible to get the desired
results by this me thod , and a fair degree of aoouraoy was obtaine d
after a little pre.otioe.
Test Procedure and Results
8. P1 rpose of bypass. It was found by tests that they bypass is
essential to successful starting and stopping of the pump for both the
electrical and hydraulic methods. In starting, by any of the four
methods, the bypass should be open previous to the admisei on of air into
the volute to all ow complete draining of the latter. If thi s is not
done, pressures are created in- the vo lute wh:l oh retard the ilapeller
8
s peed . This resul ts in an increase of power fo r sta rting the mo tors
ele otri cally or the ne ces sity for hic,her jet pre s sures in th e hydraulic
method . The bypas s i s e s sentia l in the hydraulic me thod to carry oft
the water imp...rte d to the buckets by the high-pressu re jets . The cen
trifugal pumping action tha t ooou rs when the impe ller i s revo lving
tends to throw any entrapped water toward the outer radiu s o f the volute
oe.se. If a bypa ss i s not provided , the water fl owing in from the je ts
can flow frorr. the eye of th e impell e r only after suffi ci ent pressure
ha s been develope d. to force i t out . In the a.bs en oe of a bypass , it is
obvious thet the hydraulic method of starting approache s a vicious
circle . The hi6her the pressure in the volute due to the trap ping of
water , the h i[:;he r the )res sure mus t be mai ntained on the je ts to bring
the impeller to s peed ; a.nrl a s an increase in ,je t ore ssu re is naturally
accompanied by an incr ease in di scharge , it then becomes ne cessary to
force more water out of the impe ller eye .
In the shut-down cycle , the b;1rpas s i s al so e s sentia l f or al l fb ur
methods. Without it t he admis si on of air will not force al l o f the
water from the volu te . A sm.e.1 1 portion be comes trappe d , and continue s to crea te pr essure in the air en d wu ter mixture. This in turn requires
more power to turn th e impe l ler than would be the case were the water
abs ent . Fi6ure 17 sh ows that the power required Wi. th ei ther-1 air or a
mixture of air and water in the case is 10 nnd 53 pe rcent respectively
of the full-load value . In addition . the ins tabil ity of the ai r and
water mixture produced very noticeable surges wh i ch a re refle oted in the
power re qui rement . The main purpose th roughout these te sts was to
develcp a me thod in which chang e s in pre ssures and chang e s in load would
ooour as gradu al ly e.s possible du ri� t.1-ie ste.i-tillt,; and s topping cyoles •
9. Calibration of bypas s. Convinced that the bypass is en essen
tial FB- rt of ti·.e pumpiJlG ins tallat ion , the next ste p cons is te d d: de ter
minin0 the most e conomical size . As previously stated , the bypass
consisted of a two-inch insi de-di ameter oipe with a two-inch 6 ate valve
for oontrol. Wi th t11e nump in operat i on and the main valve in the d is•
ch arge line cl osed , the velocity of flow was me asure d in the center of
the bypass pipe for each turn of the bypass valve . Th :i s was done with
10
a cylindrical pitot tube as shown in fi6ure 7A. The velocity as
measured on the center line we.s a s su med as 1 .25 tirce s that of the
average, and the di scharge c omputed accord i ngly . From th.i s information
the equ ivalent size of byf8. ss pipe was oon,_puted to c orres pond to eacll
turn of the bypass valve . This calibration, which was used through•
out the tests, is plo tted on figure 10.
10. Effect of bypass on impelle r speed. A series of tests were
ma.de to determine the minirwm size of bypass• whi oh wou ld relieve the
pressure in the volute sufficiently to not deter the speed of the im•
peller, when propelled by the water jets. With too eight-inch main
l ine valve closed ar,d the bypass valve opened completely, ten turne.
a defi nite water pressure was applied to the je ts and the impeller
speed measured. The impeller speed was then measured for nine turns •
eight turns, et o . , down to complete closure of the bypass val ve. The
above procedure was repeated fo r line pressures of 110, 70, e.n d 35
pounds per square inch , and the results are plotte d on figure 11.
It is evident from fig;ure 11 that the minimum size of bypaas to
obtain 900 r.p.m. for the jet pressu res and discharges u sed in this
model was approximately 2 inches. Jet performance is definitely the
governing factor in determining the si ze of bypasa . The size or by
pa.s s oould have been ma de somewhat smaller had it been possible to
use hiiher ' pressures with oorrespondingly lower discharges on the jets.
The aooompanyi?l€, table sh ows the magnitude of the total discharge
for the four jets, the velocity of the je ts, and the presaure on the
1/4-inch jet noz zles for three different line pressures. The jet d i••
charge s were measured through a 1-inoh orifi ce meter and the suction
elevation was held e;t; 9.0 feet above the center of the suction pipe.
The values in the table are in dependent of the size of bypass pipe.
Pressure above Jet Total dis• Pressure in oenter -1 ine Line velocity, charge of 1/4-inoh
suction pipe, pressure, feet per four je ts, nozzles, feet of we.ter lb .per sq .in. second g .p.m. feet of water
9 .0 110 99.4 61 36.7 9.0 70 81.5 50 17.3 9.0 35 57.0 35 7.7
11
11 • Effeot of buokete on pump performs.nee• The effeot cf the
impeller bu ckets on the effioienoy of the pump was determined by both
hydre.ul ic and ele otri oal IlJ9 a s urement s . In the hydraul i o method , the
dis charge delivered by the pump was measured through a six-inoh venturi
meter (figure GA.) for ea.oh turn of the eight-inch throttle valve, I
located l.IIIIOOdiately downstream from the meter , The measurement s, hT•
draulic and electrical taken simultaneously, were repeated four time a
with the buckets on the impeller { fibure 8A) and four times wi th the
buokets filled wi th Cerro Bend metal (figure SB). The readings of
ea.oh four runs were averaged and the hydraulic results plotted on fig
ure 2 2 , There is a. maximum deviation between the two curves of about
two percent in the di scharge for the larger openings of the throttle
valve. Thi s would indicate that the buckets created additional tur
bulenoe in the volute which interfered slightly with the normal funo
tioning of the pump. Thie was further evidenced by the fact that the
g age at pressure oell No. 2 (f4;ure 7B) fluctuated over a range of
about six feet of water when the buckets were incorporated in the
impeller end leas the.n a foot of water after the buckets were elimi•
nated. These fluctuations, at pressure cell No. 2, oan be observed on
the osoillograph records (fi6ure 18).
The power i nput measurements , made simultaneously with the water
disoharge measurements, indicated that the power input to the pump wa.a
inoree.eed materially by the presence of the buckets. The reading s of
four runs with the buckets and four runs without the buckets were
averaged and the results are plotted on figure 14. The data on fig
ure 14 shows that the los s in power due to the buckets amounts to from
o.s to 3 p<>roent wi th a maximum of 3 percent ocouring at maximum dis
charge. This is also the point where hydraulic measurements showed
that the buolmts caused a two i:,-e roent reduction in the dis charge.
It is apparent from the above results that the over-all effioienoy
of the pumpi� unit was reduced apprec iably by the buckets. Combining
the effeots observed by both hydraulic and eleotrioal measurements the
total loss in effioiency for the pumping unit amounted to about four
pe roent at the �imum di scharge. This loss when applied to the four
12
prototype pumps would be oonsiderable over a period of time and the
buoket installation as used on the test pump is not feasible.
Another method of determining the friotion losses due to the
buokets was to mea.sure the power input at shut-off head wi th and wi th
out the buckets• With the di scherge valve closed. power measurements
were made with sero, one . two . and three turns open on the bypass valve.
Immediately after these values W&re obtained air was admitted to the
pump volute and the power was measured. By subtra.oting this value from
the four previously obtained it was possible to separate the motor end
bearing losses from the losses due to water in the pump case for these
four positions of the bypass valve. Then, by oomparing these water
friotion losse1 with and Without the buckets. the losses due to the
bucket were obtained. The results on figure 15 show that the losses
due to the buckets amount to about 1.5 peroent.
With air in the pump oase, the power input to the motor decreased
ooneiderably during a eeries of oonseoutive tests wh ioh was probably
due to variations in the bearing and gland friotion. Although motor
and water temperatures varied, their effect was less than the errora
in observation and the change from 1,470 to 990 watts over a period of
about 2 hours, as shown on figure 16, oould not be attributed to this
source • The power input, wi th water in the case, deoreased during the
tests about the same amount ae did the input to the motor with air in
the volute. Therefore 1 the differenoe between these two quantitiee ,
whioh nipresent the losses due to the water, is fairly independent and
oonstant. To make oertain that an aoourate value of loss due to the
buckets 1'8.S · obtained, fourteen runs with the buokBts and ten runs with•
out the bucket• were me.de and the average of ea.oh plotted on figure 15.
It is believed that fairly &eoura.te determinations of power were ma.de
due to the faot that with air in the volute the power input average,
with buckets on the impeller, oheoked the power input without the
bu okets within o.a percent.
The hydra.ulio starting arrangement of housing a sma.11 Pelton wheel
in a separate unit on the same shaft does appear feasible. Provision.a
must be made to reJnOve the die oharge from the Pelton wheel and drain
13
· the cue after the ,jets &.re cl osed , thus allowing the buckets to re• volve i n ai r during normal operation of the ::n.zmp.
12. The starting oycle. In an electric motor the starting our•
rent is aeveral times th.a full•load current and wi th the larte motors
on the Granby pumps. the starting current would be sufficiently large
to momentarily reduce the ordinary line voltl¾;e • To minimize this
oond iti on some of the previously mentioned starting deviaes were used.
in oonjunction with the pn:mp motor. The laboratory sthdies chiefly
oonoerned · the method whereby the rotor we.s bro11&ht to operating speed
by the force of hydraulic jets impinging on the buckets out in t he
topside ·of the impeller.
The procedure for bring ing the pump from &. otandstill to $peed
under full load was as follows s With the dis oharge valve closed and
the bypass valve open, compreued e.ir . was a.dmi tted to the discharge
:side of the pump until the water level in the intake had depressed to
a point approximately eight inohes below tr� unpeller. Then with the
use of hydraulic jets impinging on the impe l ler buckets synchronous
speed was · att&.in@d with the impeller rotating in air. This WQ.S follow
ed by closing the motor swi'tch . olosiDil; the valves in the su pply to the
jets . and gradually releasing the air at the discharge side, thereby
allowing the we.ter to enter the .pUlll,p slowly and the pressure in the
dis oh�rge side to gre.dually build up to shut-off haQd. The discharge
valve was then opened slowly and the bypass valve cloaed . Thus the
motor operated at full load, oompleting the starting cyole.
13. The etarti3-eyole osoillo,ram. A graphic reoord, r:4sure
lSA.. shows the l'.DS.gnitude of the current , voltage • end the related hy•
draulio press ures during the. atartil)f; , cyole. It will be noted that
the rotor was brought to epeed in air by tha hydraulie jets and the
motor switch closed before the record was started. At this point in
the cycle, the current oonsumed was 20 amperes ; the head on the intake
lir\e was 9 feet of ater, whioh rem ained constant ; and the ai r priHUBure
in the volute was approximately th e same . The pres sure in the discharge
line (no . 1 pressure oell ) represent& the static head maintained by the
closed valve.
14
As the air was released from the pump volute a.nd the water enter
ed, a very rapid fluetuation in the hydraulio pres sure• occu rred at
the intake. The frequenoy oorresponded to the produot of the revolu
tions per se�ond and the number of blades of the impeller. The reduc
tion in pressure at the intake (No. 3 pressure cell) was simultaneous
with the increase in pressure at the discharge side (No. 2 pressure
oe ll) , lhe corresponding increase in pressure in the dieoharge line
was due to openin€, the di scharge valve before tte shut-off head had
attained its ms.ximum value , In the prototype , this would not oo our
bece.'JSe enough time could be al lowed between the releasing of the air
and the opening of the valve to all ow the head to stabilize , whereas
in the test pump, the capacity of the oeoillograph camera l imited the
amount of time that could be al lowed for eaoh atep in the oyole . When
the main valve we.s comple tely open, the pressure upstre&.m dropped and
then increased as the bypass was olosed. An inspe etion of the current
trace on the oscillogram shows that the increase in ourrent from 20
to 44 amperes was Sl.lff'ioiently gradual to allow the generating apparatus
to respond to the change i n l oad . Compar ing figures 180 and D , the
ordinary starting eurrent as compared to the magnetizing ourrent, whi eh
was the first current used wi th this starting deviee , was approximately
five e.nd one-h�lf times as great. This w ou ld be an appreciable reduo
tion in the prototype current where the motors wi 11 be 6,000 horse
pov1er e&oh.
Figure 18E is an osoillog ram of the motor demand duri� a starti ng cyole where the diameter of the bypass was decreased to 1.30 inches and.
the rate of air release was slower. In thi s instanoe the load inoreaa
ed more s lowly requi ring 9.1 as compared to 2.5 seoonds for the form.er.
This indicated that the size of the bypass and the rate at whioh the
air was released determined, within oertain l imits, the rate at whioh
the load was applied to the motor and we.s signified by the oorrespond�
ing inorease in power on the osoillogram.
14. The shut-down oyole , The fol lowing steps , which were talmn
to reduce the power gradual ly from full load to zero , are &ppl ioable
to the stoppint:; of any vertical pump regardless of the starting devioes
15
employed, as the shut-down oyole ii independent of the devioe us ed for
attain1?lf, synohronoua speed . The dis oharge valve was slowly olosed and
the bypass valve opened . Air was forced into the volute , oausi.Dg the
water to be depressed allowing the impeller to rotate in ai r. Thue
the power taken by the motor was redu ced to ten percent of the full
load value and the fluotuation in the line voltage was very small when
the motor switoh wa.e opened to complete the oyole .
15 . The ahutwdown-oyole osoillogram. The shut-down•oycle 01 01110-
gram, fiture 18B , 1a divided into three stepe s ( 1 ) the normal operation,
(2) closing the disoharge valve , and ( 3) for o�ng air into the volute .
At normal operation under full load , the current oonsumed was 44 am•
peres . the preasure in the dis charge l ine 2 7 .6 feet of water (No . l
pressure cell ) , the pressure at the discharge side of the pump 33 feet
of water (No . 2 pressure cell ) , the pressure at the intake 2 feet of
water (No . 3 pressure cell ) , and the head on the intake waa 9 .0 feet
of water (No . 4 pressure oell ) .
As the disoharge valve was olosed and the bypas s valve opened,
the ourrent consumed gradually decreaa•4 to 31 amperes when the die
oharge ve.lve we.a completely elosed, then it remained constant until
air was forced into the volute . In the meantime , the hydraulio pres
sure at the dis charge valve inoreased to 42 .5 feet of water, the pree•
sure in the line became negative for 0 .6 of a seoond, then increased to the static head. of 6 .6 feet of water . The pressure at the intake
inoreased to its stati c value of a .o feet of water , m d the head on
the intake line remained oonstant . When the oompreued air entered
the die oharge side and depressed the water, the presaure at the int&lm
fluctuated with the frequenoy of the impeller vanes and for an instant
reached a maximum value of 16 feet of water• Aa the air oontinued to
enter the volute , the water level gradual ly lowered , the shut-off hea4
decreased to the ste.ti o pressure at the dis charge s ide , and the current
consumption dropped to a mini1Tllm value of 20 amperes for the impeller
rotating in a1 r •
16 . The relati on of the bypaas to the shut-down oyole. During
the oourae of the studies it was found that the diameter of the bypae1
16
- affected the power curve durint; the shut-down oyole. For instanoe, a
b�rpass with a large d iameter caused �he power to decrease muoh more
rapidly tha.n did a smaller bypass (figure 19 ) . Without a bypass the
power consumed with the impeller rotating in an ai r and water mucture
was 50 to 60 percent of the full-load value, whereas with a bypass it
was only 10 percent of the full-load value . Without a bypass, the air
did not force the water out of the dis charge si de and a mixture of air
and water remained trapped around the outside of the impeller and in
the line upstream from the di scharge valve. As a result, there was
sufficient trapped water to oa-1se the pump to create approximately 60
percent of the shut-off head . When a small-diameter bypass was pro•
vided , from the di B charge side to the intake the trapped water and air
flowed slowly out of the discharge side and the oorrespondj ng decrease
in hee.d and power were 1:. radua l. If the diameter of the bypass was
large the water left the pump quickly and the corresponding decrease
in power was rapid . The rate of decrease in power i s shown on fig ure
19 for the bypass diameters of 1 .30 inches and 0.67 inch. The curves
also show the results obtained wi th different looatione of the air
ports, which are discussed in tre followi.n.b paragraph.
17. The location of the air-supply ports. The location of the
air-supply ports affe cted the rate at v.hi ch the load de oreased and the
manner in whi ch the power decreased . This can be seen by comparing
the power-time �Jrves of fi6ures 19A and C with fi&ures 19B and D. The
form.er curves show the decrease in power related to time for bypass
diameters of 1.30 inches and o.67 inch with the air-supply port located
at the intake (fi6ure 7A) whereas the latter curves show the results ob•
tained with the port on the di. s charge s ide ( figure 7B ) • In figure 19B
the drop in power was quite rapid, 1.8 seconds, with the air•eupply
port at the di scharge side of the pump, an d it was mu ch slower, 6.2
seoonds, and more gradual wi th the port located in the intake, figure
19A . The difference in the results for the two locations beoame more
pronounced as the diameter of the bypass was made smaller (figures 19C
and D). The total time required for the power to deorea.se 4,500 watts
and becow.e steady at 1,500 watts was in both oases satiafaotory, 33 .9
17
seoonds for the former and 2 8 . 6 se conds for the latter, but wt,en the port was looated on the d i s char�e side , the de crease in power was not
gradual and would cause undesi rable power surges in the prototype. In
the test pump , these fluctuati ons in power, whi ch had a definite period,
were gradu ally damped to a steady demand at 1 1 500 watts·. 1'his was due
to the f'e.ct that the air and water did not mix when the compressed eir
was supplied to the di scha rge side . As a res ult, large concentrations
of air esoaped intermittently through the bypass or impelle r and sudden•
ly relieved the shut-off head whi ch again built u p to some lower value
than previously obtained . The process continued until all of the water
was drai ne d from the pump . This fluctuat ion in pressure oaused the
oorrosponding fluctu ati on in power shown graphi cally on figure 1 9D .
With the a.ir•supply port at the pump inttl.ke . a. s shown in fig; ure
7A, the power de crea sed steadily and the total t ime for the reduotion
to o oaur increased . This impro·vement was due to the thorough mixing
of the air and water bY' the impeller before it entered the discharge
side and cir oub.ted baok through the bypass , thus n o large oonoentra•
tions of air could es oape rapidly and cause the head to fluotuate .
As a result of this chti.nge , it was evident that the mos t desirable
location for the air port was somewhere on the intake si de so another
test was rnade Wi th the compres sed ai r entering at the center of the im•
peller hub . The da ta obtaine d showed no appreciable difference be-
tween the power time curve s as oomp ... red to those of the previous arrange• ment . Howeve r, from visual observati ons , it appeared that the mixing
of the air e..nd water wa s more uniform and there was little or no vibra
tion of the pump due to the mixi� . 'l'hi s indicated that the ai r was
d ispersed throughout the fluid , me.kint,; the mas s oore 1.1nif'orm when it
entered the impeller . If thi s l o cation of the air port presents meohan•
ieal difficulties , the s eme smoothness ' of operat ion can be obtained by
looating several ports on equal s paoes around- the periphery of t he in•
take . A summary of the data for the three conditions is shown on fig •
ure 20 .
18
The exhaust port should be located as near the dlsoharge valve
as possible or i n a place such that there w ill not be air trapped in
the s ystem when the main valve, is opened. The rate at wh ich the load
is applied to the motor depends upon the opening of the exhaust valw
and the diameter of the bypass . For the small•di a.rneter bypas s , 0 .67
in ch , the rate at which the air is released seems to have little e ffe ct ,
but with the 2-inch d ie..'Ileter bypass there is an e.ppre oiable di fference .
A summa ry of the data i s shown on figure 2 1 .
19
CHAPTER I II - c .. i:T CLliSIONS
18 • Summary. (a) If the startint; device is jet-propelled wi th buckets on the im•
peller , the size of the bypass is boverned by the disoharge from the
jets. The buckets reduce the efficien cy of the pump approximately four
percent.
(b) If the starting devioe is e.n auxiliary motor, a Pelton wheel
housed in a separate case, or the low-voltage scheme in connection with
the regular motor, the diameter of the bypass need not be larger than
is necessary to circulate the coolinb water.
(o ) The power required to drive the impeller at rated speed in ai r
is about 10 percen t o f the full-load demand, whereas with water in the
volute it amounts to about 53 percent.
(d) The startin,. and shut-down cycles, as proposed in chapter' I I ,
sections 12 and 14, reduoe the shock to the electrical s ystem suffi
cien tly to make the method practical .
(e) The compressed-air-supply port to the pump should be located
on the intake side whereas the air-exhaust port should be on the dis•
charge side at a point where all of the air in the system oe.n be ex
hausted .
(f) The rate at whi ch the air is exhausted from the pump during
the startil\:, cycle is a major factor in controlling the rate at whi oh
the load is applied to the motor.
(g ) The rate at which the air enters the pump , and the dirureter of
the bypass control the rate at whl. ch the load on the motor reduces
durirlf, the shut-down cycle.
(h) The test data indicated that the di ameter of the bypass waa the
most important factor controlling the rate at whi. oh the power decreased
durirl(; the shut-down cycle.
20
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C A P A C I T Y I N C U B I C F E E T P E R S E CO N D
G R A N B Y DA M P U M P I N G P L A N T
P R O P O S E D P RO TO T Y P E P U M P C H A R A C TE R I S TI C S
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f Bross p late s weated to impeller-·' ..___ __________ _
DEPA R TM E N T OF THE I N TERIOR B U R E A U O F RECLA M A T I O N
COLOR A DO - BIG TH O M P S O N PROJECT - C O LO.
G R A N B Y P U M P I N G P L A N T REMODEL ED BINGHAM S - JNCH VER TICAL
C LO S E COUPLED PUMP SIDE VIE W OF IMPE L L E R
T Y PE SV - 1 5 H. P. - 9 00 R. P. M.
A S U S E O FOR M OD E L P U M P '(E S T S
DRAWN _____ J. N_B _ _____ SUBMITTED ___ _
TRACED ____ C F. F. ___ ___ .RECOMMENDED •• _ ___ _ _ ______ _
C1-4ECKEO •• _ _ _ ___________ A PP ROVED ______ -- _ _ ___ --- _ _ _ -
1ornvrn, COL ORA DO APR1L 1, 1902 I 245 -0- 1 7 2 1
FIGURE 6
A. TEsr ARRANGEMENI'.
B. PUMP SHOWING TRANSPARENI' SUCTION PIPE AND ELBOW.
GRANBY PUMP TEST .ARRANGEMENI'
FIGURE 7
A. PUMP SHOWING BY-PASS AND PITOI' TUBE .
B , PUMP SHOWING BY-PASS , AIR SUPPLY AND EXHAUST CONNEOI'IONS,
DETAILS OF GRANBY PUMP TES!' EQ.UIPMENI'
FIGURE 8
A. TOP OF REMODELED PUMP IMPELLER WITH THIRTY BUCKETS.
B . PUMP IMPELLER WITH BUCKETS FILLED.
GRANBY TEST PUMP IMPELLER
4
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G A L L O N S PER M I N U T E 2500
T YPE S V - S I Z E 8 " - R. P M . 9 00
C HA RA C TER I S TI C CURV E SHEE T - B I N G H A M P U M P
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B Y - P A SS C A L I B R A T I O N
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1
1'. _ _ J �o*�e1ssure � .� /f "' � /' c I
I Q = 40 G. P M. ":'I t Q - 50 G PM. y I /
I - - : � j - ! / -- __.,/\,
/�o_* Pressure I I ! l I � ,)<-'l�
I Q - 6/ G. PM. I
1- - 1-- '. - - r J---::::-,---. +- --+-------+----+----
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i t-�- i-- -�----·- - i -- - _ l - -----· --- -----+--�-�-�-�-�--�--+-----<
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, - - - - - - - -,-,-Terminals for the c onne c ting
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diaphragm
SECTION THRU CELL G ENERAL VIE W OF C ELL
D E TA ILS OF CARB ON - PIL E PRESS URE CELL US E D IN G RA N B Y P U MP MODEL TE S TS
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3 Phase
1 '
G R A N B Y P U M P M O D E L T E S T S D I A G R A M O F E L E C T R I C A L C O N N EC T I O N S
F O R T H E I N S TR U M E N TS
1 -.---------------------� 1
', -'2 o 8 Vo I ts I i n e to I i n e
, ' 1! 20 Vo l ts I in e to n e u tra I power � _..._ ______________ -+-----41
sou r c e
C.T.
(Curre n t ) Sh u n t - - ,
A mmeter- , - , , , - - Vo l tm e ter I c---->---1-,
' --_,..,,. Osc i l lograph ,' e l e m e n ts
( Vo l t a g e )
Wa t t m e te r - - - _ , ' - - Wa tth our m e ter
M O TO R - - - - /5 H. P , 9 00 R. P. M . , 220 / 4 4 0 Vo l t s , 3 ph a s e .
M o to r
C . T. - - - - - B00/600/!00/ 50/20/10/5 R a t i o c urre n t t r a n s fo r mer , G . E . No. 6 3 9 6 5 5 0 .
A M M E TE R - - 5 A m p. , A . G . , 2 5 0 A mp. s c a l e , Th o m s on No. 3 0 3 6 9 8 . VO LTM E T E R - 1 5 0/300 Vo l t ra n g e , We s to n No. 5 9 4 9
WATT M E TER - 5 A mp. , 1 50 vo l t , 1 ¢ , W e s to n No. 3 700
WA T T H O U R} M E TER - t/5 Amp. , 150 vol t, 1 ¢ , K = t /3 wA T TJRE v. , Sangomo No. 216 8 925
S H U N T- - - - 3 Fe e t of No. 14 A .W. G. so lid c opp e r w i r e
W. A . M. 3 - 42
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z -I-I-<1. 3:
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r l � U K t. I �
G R A N B Y P U M P M O D E L TE S T S
M EASUREM E N T OF PO WER INPU T TO P U M P M O TO R
A S TH E D I S CHA R G E VA L VE POS I TI O N I S VA R I E D
UNDER CONDI TI O NS OF WI TH A NO WITHOUT BUC KETS
1 4 r--------,----------.-------r--------r-----,-------,
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10
6
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-:.::..
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L I N E WA TTS DISCHA RGE W I T H
VA L V E B U CK ETS
8 turns 1 2, 200 7 turns I 1 , 805 G tums I I, 5 70 5 tu rns 1 1 , 035 4 turns 10 ,370 J tums
I 9 245
I
b u c k ets
I _ ____ , D A T A
I N PU T P E R BUCKET LOSS W I TH C EN T I N PER CEN T
OF FULL LOA D O U T CHA NGE B U C K E TS M O TOR I NPU T
1 1, 830 3 . 1 3 2_ 9 6 I I , 650 1 . 33 I . 2 4 1 1, 3 90 1 . 58 I . 44 10, 930 0. 96 0 . 8 4 10, 2 05 / . 62 I . 32 9 / 8 0 0 . 7 1 0 . 5 2
O �---�3-----4-----5�---�6----�7 -----'8
T U R N S
M A I N L I N E D I S C H A R G E VA L V E
W. A . M. 3 - 4 2
r I O V n L I ....,-
G R A N B Y P U M P M O D E L T E S T S
M EA S UR EM EN T OF LOSS ES D U E TO WA TER FRI CT I ON
W I TH D ISCH A R G E VA L V E C L O S E D WI TH
C O N D I Tl O N
Total wa tts with wa te r in p u m p c a s e
Watts w i t h a i r i n p u m p c a s e
Watts loss d u e to wa t e r tri c -ti o n ( From a bo ve readings )
6
0 (f) I- 0 W Z
4
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A N O WITH O U T B U C KE T S
D A T A
B Y WA T TS I NPU T P E R BUCKET LOS S PASS W I T H C E N T I N PER CEN T
W I T H O F FUL L L OA D VA L VE O U T CHA NGE B U CK ETS BUCKETS M OTOR INPUT
3 turns 6, 554 6 , 40 7 2 . 3 0 I . 2 6 2 turns 6, 384 6
)202 2 . 94 I . 54
t turn 6)292 6 , 1 1 6 2 . 88 1 . 4 9
Closed 6 296 6 1 2 4 2 . 73 I . 4 2
Air I 2 5 5 I 2 6 5 0. 79 0 . 08
3 turns 5, 299 5 , 1 42 3 . 0 6 I . 2 6 2 turns 5, 1 2 9 4
) 93 7 3 . 8 9 / . 5 4 I turn 5, 03 7 4 , 8 5 1 3 . 4 4 I . 4 9 Closed 5, 041 4, 8 64 3 . 64 / . 4 2
- Wi th . I
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_ ___ L I -
M O D E L T E S TS
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I 2 3 4 5 6 7 8 9 10 1 1 12 1 3 1 4 1 5 1 6 1 7 1 8 1 9 20 2 1 22 23 24 25 26 27
R U N S M A D E M A R C H 2 5 , 1 9 4 2 W. A . M . 3 - 42
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I I i I I I I I I By - pa s s v a l v e c lo s e d, I w a ter in p u m p ca s e
I I
J I I I i
By - p o ss v a l v e c l o s e d , a ir let l i n to case w h ile motor run n i n g .
( Ste ady p o w e r condi t i on ) I
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m o t o r, ru n n in g . ( Ste a dy po wer con di tion )
C)
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By - p cis s v a l v e o p e n , w a te r in p u m p ca se
I __ I
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C) 1"17 :::0 a :o .;;;: G) < � n, ::0 C) h (/) h ; � -, < - ni a a < U'J < co ti) --<: ti) --< ::r: ti) -I � -0 -, ::c c:: C: n, -, � C) � ::r: " ;; a n, C) -, :::0 3: a ni a - :::0 r-< h CJ -, .,, -, ri, ::r: a � rn, :::0 n, ti) -, --; n, ::r: h ri,
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r
Zero for Na 3 P.C.-. , . k--Air exhausted and scroll cos;,u,i of -water Oischarg�alve wide open- -- --:i-----=--=-=--By- po;;;;ve beingd�d---------�,.,. -- :--·Normol operation of full discharge- - -- - -- ---Impeller running in air- --- - - ----- ------ ---- - - - - - ---'t'- Air leovi� scroll case ond wot�c_ entering- -- -
, _ _ _ _ _ ____ of - - - -- Discharge valve being opened- - - - - - - -- ---- -- - -�- - - - - -.. By-poss closed···>-'
,' ,r-i ( / + +
By poss volve open I ' l rPC. No.1· 31. B ft IMClter
II I 11• 1• 11111 1t,l"" "·• · ·-I . ...... ... . , . .. ,. -· · .. . � ..... . . .,- .. ..,,.,..,"''""" I I / . ''" ,,, ......... _ ·•t J .. :1!�11i,1'1!U' \ • ·1"'1l1 ::ill!. ,'L�I . �. ' .. • I I . .. . . " , ..... 1 1 PC. No. 2 - 32. B ff. of woter-,, }' �1 ;- '.., . '!; · ; '; ,· ' ·· · 't· -J,Hl,I ·\ i ' , voltage : i '. L 1•: .... �!'· , • · � ... •., ·
I
' Zero tor Na 4 P. C. 9.0 ft. water -,. Na 4 P.<;._-·· ! I Nb. I P C
8 9 110
11,,J,.,,,,ff!flll,IIIII·
Current
A . S T A R,T I N· cr C Y C LE M O T O R B R O U G H T TO S P E E D BY H Y D R A U LI C J ETS
Normal operation a t full discharge-- - ----+--- - --- - - - - - - - - - - -- - - --Discharge valve closing--- - -- - - - - - - - ------------ - -�--- - - -- ----- - - -- --- - - --�--:�-- -- -· - ----- --- - - - - - -- - - - - ---- -- -Air entering and water leav1n g-- -- - - - ------- - ---- - ------- ------- - -----===-=-=-- --=- ==-i-
.--Zero No3 P C. , No. 1 By -poss valve open L.,-- - - - -- - - - - - --- - ---- - - -Air entering at discharge s,de of pump------ - ·---------------- - - -- ------ A1r travelin g back wards through Impeller-- - ----- - - - - - - - - ----.,
� zero No 4 P.C /2 Water 3 P.C.
t Discharge valve closed· ·"1 , 42 5• Water at No 2 P. C. I Impeller running in air - - · . ,..,
I ' " ' ' I ,, !I tlf•tlll't I � ,,, • • ,, I II .. "'* I I I ,· j I' ' 1 1 1 1 1 I , ' " " I � , ,. • .. ,._ '
�-- , •I fl 11 1 1 ,11111 t , I . • I "'
· Voltage I
+ ' . I - • I + _.27. 5 Water No. I P. C. I 1 1 �. . .: •.•. L � I
33 ' Wofe,-No 2 P. C.· o I i 2 . --Time In sec.- - -- 3
'''"1111111k111�1,,,,11f1111 1p1�111"!11111,1t1�11,1111J,n'"r�1111p1 1l,1t"''II' ,,.. t:�,1�1111�1111r1l1,,,,,,_, 1,,l;:,�1 + I
--r-·-·-_-... !zero No.I P.C. L .. , Current f. I '
-----Zero No. 2 P.c I \ .. .L,j j j , \ ..
I I<,
' · 4 4 A mperes
l \ ,f T .. 10. 2 Water No. 3 P C. 'a.J..1,.,,_,l----/66 Amperes
11,1, . ,, 11',1111111if1Wlll�h_e_9t�.?!
C. M O TO R S T A R T I N G C U R R E N T I M P E LLE R NOT R O TA T I N G W H E N S W I T C H W A S CLOS E D
Impeller running ,n air discharge valve closed
I � -I I< - - - -- - - - - - - ---- - - - -- - -' I -
---
t500 Watts
= ill, • 3000 Watts
8 S H U T - D O W N C Y C L E
leaving scroll case and water entering - - - - - · -
-� . .. . ....... .. --.... . ..
- 9. 1 seconds - - - - - - - - - - - - - - - - - - - - -
-- -. ......... ---- ,-· ·Power
t6' Water No. 3 P. c_,-
-
Vol t o g e
;+- --v. second - --...J I � I Y:zta -:r: --�77F1iir22 - -
• 1 _ _ .-30 AITJ)f'r'lls 1 l , 1'li11�1111111111 llllltfl 11111 tflll!Tr,Tl 11111111111111111111111111H �-- . ,.._ i1,11111111 11 1 1 1 1 11 11,11111111 11111u1t11.11111,111111111111111u 11uu .,y_ 20 Amperes - . _ ,.
0. MAG N E TI Z I N G C U R R E NT ( Z E R O POW E R l
M OTOR R U N N I N G AT SY NCHRO N O U S SPEED W H E N S W I T C H CLO S E D --,------
-- - - -.---- - --- - -- -../ Impeller running : in water -- - ----- - --- - - - - - - -� I
I I .
-
1 500 Watts -----------
6000 WoHs
' I
� :�
__,, "'"' . .i ...
G R A N B Y D A M P U M P T E S T S O S C I LLOG R A M S FO R STA R T ! N G A N D
A,r exhaust valve wide open ,,.,, ... ��··�ri ,,..,�,.,""�"°'1� S H UT D O W N C Y C LE S
E. PO W E R - T I M E C U R V E S T A RT I N G C Y C L E BY - P A S S D I A M E T E R 1 . 3 0 "
, - - - - - -· - -- - - ------� --- ----- -- · · I -'4t �----· ·- - - · -- - -- - -- · - - - -- --- - - ---- -- - · - --- - - --- --- - - --- -· - -- -- · - . .• • . .
J
��r- - - - - - - - - - - - - - - - - - - - - - - - -- - - -- - -- - - - - - - - - A, r enter i ng scroll cose and water leavi ng - - - -- - - - - - - - - - --- - - - - - - -- - -- - - - Scroll .cas e fi l led with ai; _ _ I
- - ---- - - - -- - - - - - - 1 1 seconds - - - - - -- - - - - - - - - - - --- - - - - - - - - - - - - - - - - - - - - - - - ------
_ __ _ _ _ _ _
_ _ _ __ _ _ _ _ -------- ----�- -J ' :,._ _ _ _ _ _ _ _ _ Imp eller running In water !'4 · · · ·· --- - - - - - - --- - Air entering scroll c as e a nd water leavin g - - - - - - - - - - - - - - - - -- --.../ ·
blscharge valved closed - - - -- -->1 · Impel/er running In alr--.J. f->-_ -- . - - - - - - - - - - - - - - - - - - - - - 1 -- -- -!l./ seconds - - - - - - - - - -- --- - - - - - - - - - - - -- - - - - - --..l
ed - - -� -1500 Watts
3000 Watti;
4500 Watts ·- - · · ·Po wer
6 000 Watts
7500 Watts ., __ _ _
A. A ir e n terin g at side of i n t a ke a · be low impel /er - By -pass dia. 1. 30"
. I r;-.. �-- , . . '"''"" ..... ,m, .. _ .. ,. ' ' I I
I I .
1500 Watts
300 0 watts
4500 Watts
, ;, ,-,'l'•n·,<1•-•··"· ,.,,.,,,.,. , , -m1,1•1",lf! .,.�,.., . . . , . ,, , ,. , . ,
1<,-- - :-:--- -1.8 seconds -- - ---- ·""! ............,._ · ,
B.,' AJr e ntering at dis charge side of pump - By - pass dia. • I. 30 • '"' "\t! . . ,, ,,r,,,, . . ,,,-, .. �,, - ,,. · •:·::•/!• ' . ,
1 -·
c- - - - _ _ _ _ _ • _ _ _ _ _ _ - · - • . - :-1'[':C���� ;��1n:;�l�s =�t
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I >-CD LL 0
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1 . 50
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-
0. 5 0 0
· F. L . 4 -9 - 4 2
I I I I I
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7
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G R A N B Y PUM P TES TS
I S H U T - D O WN C YCLE i I R A T £ OF D EC REA S E I N P O W ER
REL A TED TO THE B Y- PA S S DIA M E T E R -- - - r
I
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A ir e n tering through s ide o f
-
i n take 8 " belo w impel / er.
- ·- � A ir e n ter ing at
discharge
"' �
" "' �
A ir e n tering in ta k e at ,,. / center of impel ler. - /
--- - - ----- -
----
16 �
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