AWWA E 101 (Vertical Turbine Pumps).pdf

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AWWA El01 88 I 783358 U O O Z 743 3 W

P

American Water Works Association

(Revision of ANSVAWWA E101-77 [R82])

ANSVAWWA E lO 1-88

AWWA

STANDARD

FOR

VERTICAL

TURBINE PUMPS-LINE

SHAFT

A N D SUBMERSIBLE TYPES

Effectiue date: Aug.

1,

1988.

First edition approved by AVCrWA Board of Directors May 11, 1955.

This edition approved Jan . 24,

1988.

Approved by American National Standards Inst i tute, . M a y 31,1988.

AMERICAN WATER WORKS ASSOCIATION

6666 West Quincy Avenue, Denver,

Colorado

80235

merican Water Works ssociationYRIGHT American Water Works Associationensed by Information Handling Services


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A W A Standard

This document is an American Water Works Association (AWWA) standard. I t is not a specification.

AWWA standards describe minimum requirements and do not contain all of the engineering and

administrative information normally contained in specifications. The AWWA standards usually con-

tain options that mus t be evaluated by the user of the standard. Until each optional feature is

specified by the user, the product o r service is not fully defined. AWWA publication of a standard

does not constitute endorsementof any product o r product type, nor does AWWA test, certify, or ap-

prove any product. The use ofAWWA standards is entirely voluntary. AWWA standards are in-

tended t o representa consensus of the water supply industl y hat he product described will

provide satisfactory service. When AWWA revises or withdraws this standard, an official notice of

action will be placed on the firs t page of the classified advertising section of

Journal

AWWA. The

action becomes effective on the first day of the month following the month of

Journal

AWWA publi-

cation of the official notice.

Am erican National Sta nd ard

An American National Standard implies a consensus of those substantiallyconcerned with its scope

and provisions.An American National Standard is ntended as a guide to aid the manufacturer, the

consumer, and the general public. The existence of an American National S tanda rd does not in any

respect precludeanyone, whetherhe has approved thestandard or not, from manufacturing,

marketing, purchasing, or using products, processes, o r procedures not conforming to the standard.

American National Standards are subject

to

periodic review, and users are cautioned t o obtain the

latest editions. Producers of goods made in conformity with an American National Standard are en-

couraged to sta te on thei r own responsibility in advertising and promotional materials or on tags or

labels that thegoods are produced in conformity with part icular American National Standards.

CAUTIONNOTICE: The American National Standards Inst itute (ANSI) approval date on the front

cover of this s tandard indicates completion of the ANSI approval process. This American National

Standard may be revised or withdrawn a t any time. ANSI procedures require that action be taken

t o reaffirm, revise, or withdraw this standard no late r than five years from the date of publication.

Purchasers

of

American National Standards may receive current information on all standards by

calling or writing the American National Standards Institute, Inc., 1430 Broadway, New York, NY

10018 (212)354-3300.

Copyright

O

1988 by American Water Works Association

Printed in USA

11



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Co m m ittee Personnel

The Subcommittee on Revision ofANSUAWWA E101, which developed this

standard, had theollowing personnel at the time:

Chester

A.

Green,

Ch a i r m a n

Dale D. Curtis

Denis L. Maher

Jr.

Walter N. Moline

Chi-Seng Yang

The AWWA Standards Committee on Vertical Turbine Pumps, which reviewed

and approved this standard, had theollowing personnel at the time of approval:

Chester A. Green, Ch a i r m a n

Consumer Members

George Bryant, City of Montgomery, Montgomery, Ala.

R.H. Hohenstein, Board of Water and Light, Lansing, Mich.

R.E. Pillow, Baton Rouge Water Works Company, Baton Rouge, La.

F.E. Withrow Jr., Production & Pumping, Wichita, Kan.

General Interest Members

Manuel Carreno, CHBM Hill Southeast, Inc., Gainesville, Fla.

B.R. Elms,* Standards Engineer Liaison, AWWA, Denver,

Colo.

C.A. Green, Parkhill, Smith & Cooper, Inc., Lubbock, Texas

W.R. Inhoffer, Passaic Valley Water Commission, Clifton, N.J.

W.A. Kelley, MichiganDepartment of Public Health, Lansing, Mich.

D.L. Maher

Jr.,

The Maher Corporation, North Reading, Mass.

C.S. Mansfield Jr .,? Amory Engineers, Duxbury, Mass.

S.C. McLendon, Holzmacher, McLendon& Murrell, Melville, N.Y.

J.F. Schultes, A.C. Schultes & Sons, Inc., Woodbury, N.J.

Charles Stauffer, Stauffer

&

Associates, Inc., Overland Park, Kan.

T.J. Stolinski Jr., Black

&

Veatch, Kansas City, Mo.

A.F. Vondrick, Arthur Beard Engineering, Phoenix,

Ariz.

Producer Members

Merrill Berman, Layne& Bowler, Inc., Memphis, Tenn.

D.D. Curtis, Crane Company, Columbus,Ohio

H.A.J. Greutink, Johnston Pump Company, Glendora, Cam.

W.N. Moline, Byron Jackson Pumps, nc., Los Angeles, Calif.

Chi-Seng Yang, GouldsPumps, Inc., Lubbock, Texas

*Liaison, nonvoting

?Alternate

...

111



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Contents

SEC PAGE

Foreword

I

History of Standard

......................... vi

II Information Regarding Use

of

This Standard ................................

vi

III

Majorevisions

.............................. vi

Par t A-Line-Shaft Vertical Turbine

Pumps

A-1

A-2

A-3

A-3.1

A-3.2

A-3.3

A-3.4

A-3.5

A-4

A-4.1

A-4.2

A-4.3

A-5

A-5.1

A-5.2

A-5.3

A-5.4

A-5.5

A-6

A-6.1

A-6.2

A-6.3

Scope and Purpose ........................ 1

Definitions

.......................................

1

General

Standard Nomenclature .................... 5

Order Form

........................................ 5

Inspection and Certification by

Manufacturer

.................................. 5

Information

t o Be

Supplied by

Bidder

.............................................. 5

Sanitary Codes

................................... 5

Specifications

Pump Components............................. 5

Water-Lubricated Pump

Oil-Lubricated Pump Column

........

16

Column

..........................................

17

Engineering Data

Discharge Column Pipe

................... 18

Column-Friction

Loss ...................... 18

Discharge Head Loss.......................

18

Mechanical Friction

.........................

20

Line-Shaft Selection

........................

23

Factory Inspection and Tests

Tests

.................................................

24

Running Test

...................................

24

Typical Laboratory Test

Arrangement ................................. 24

SEC PAGE

A-6.4 Capacity Measurement

...................

24

A-6.5 Head Measurement

.........................

25

A-6.6VelocityHead

...................................

26

A-6.7Horsepower Input

...........................

26

A-6.8 Measurement of Speed.................... 26

A-6.9Large-Pump Tests ........................... 27

A-6.10 Hydrostatic Tests

............................

27

A-6.11 Recording and Computation of

Test Results

...................................

27

A-6.12 Other Tests

......................................

30

Part B-Submersible Vertical Turbine

Pumps

B-1

ScopeandPurpose

...................... 31

B-2 Definitions .....................................

31

B-3 General

B-3.1 Standard Nomenclature

..................

32

B-3.2 Order Form

......................................

32

B-3.3 Inspection and Certification by

Manufacturer

................................

32

B-3.4 Information

t o

Be Supplied by

Bidder

............................................

32

B-3.5 Sanitary Codes ................................ 32

B-4 Specifications

B-4.1 Submersible Motor

..........................

33

B-4.2 Submersible Cable

........................... 33

B-4.3 Surface Plate

...................................

41

B-4.4 Strainer ............................................ 41

B-4.6 Pump

Bowls .....................................

42

B-4.8 Pump MotorCoupling ..................... 42

B-5 Engineeringata

B-5.2 Discharge Friction Loss

..................

42

B-5.3Discharge-Elbow Head Loss

...........

42

B-4.5Discharge Pipe

.................................

41

B-4.7 Impellers

..........................................

42

B-5.1Discharge Pipe ................................. 42

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SEC. PAGE

B-6 FactoryInspectionandTests

B-6.1 Tests ................................................. 42

B-6.2 RunningTest

...................................

43

B-6.3Typical Laboratory Test

Arrangement

.................................

44

B-6.4 Capacity Measurement ................... 44

B-6.5 Head Measurement

.........................

46

B-6.6Velocity Head ................................... 46

B-6.7 Power Input

to

Pump Motor........... 46

B-6.8 Large-Pump Tests ........................... 46

B-6.9 Hydrostatic Tests

.............................

46

B-6.10 Recording and Computation of

Test Results

..................................

46

B-6.11 Other Tests ...................................... 49

Appendices

A FieldTesting ofVertical

Turbine Pumps

Purpose of Field Tests ..................... 50

Accuracy of Field Testing

...............50

Definitions and Symbols ................. 54

Approved Instrumentation.............. 55

Test Procedure................................. 61

B

Suggestedpecification Form

for the Purchase

of

Vertical Turbine Pumps.......... 66

Figures

1 Open Line-Shaft Pump (Surface

Discharge, Threaded Column,

and Bowls) ....................................... 6

(Discharge Below Base, Threaded

2 Enclosed Line-Shaft Pump

Column, and Bowls)........................ 7

3 Friction-Loss Chart for Standard

4 Head Loss in Discharge Heads

.......

20

5 Mechanical Friction in Line

.

Shafts ............................................. 21

6 Typical Laboratory Test

Arrangement-Line-Shaft Vertical

Turbine Pumps.............................. 25

Pipe Col 19

SEC.

7

8

9

10

11

12

A.1

A.2

A.3

A.4

A.5

PAGE

Typical Submersible-Pump

Submersible-Pump Discharge

Assembly (Bowl Assemblies)

.......

34

Styles and Surface-Plate

Assemblies ..................................... 35

Head-Loss Chart for Standard

Pipe

................................................

43

Head-Loss Chart for 90' Elbow ...... 44

Typical Laboratory-Test

Arrangement-Submersible

Vertical Turbine Pumps

...............

45

Power-Loss

Chart

for Three-

Field-Test Diagram for Line-Shaft

Conductor Copper Cable

..............

48

Vertical Turbine Deep-Well

Pump ..............................................

55

Submersible Pump ........................ 56

Field-Test Diagram for

Field-Test Diagram for Vertical

Turbine Pump for Booster

Service............................................ 56

Flow Nozzles, and Venturi

Tubes .............................................. 57

Field-Test Report Fo

m...... ......... ..

62

Piping Requirements for Orifices,

Tables

1 Standard Nomenclature-Line-

2 Diameters and Weights of

Shaft Vertical Turbine Pumps

.......

8

Standard Discharge Column

Pipe Sizes ...................................... 17

3

Line-Shaft Selection Chart for

Type B Material ............................ 22 .

4 Standard Nomenclature-

Submersible Vertical Turbine

Pumps

............................................

36

A.l Limits of Accuracy of Pump-

Test Measuring Devices in

Field Use

........................................

51

V



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Foreword

This

oreword is for information nly and is not a part of AWWA E101.

I. History

of

Standard. This standard for vertical turbine pumps presents

the composite findings from studies conducted from 1949

t o

1986 by committees con-

sisting of manufacturers, consumers, and engineers. The

first

standard was

published in 1955. In 1961 the standard was revised t o include standards for sub-

mersible vertical turbine pumps. Additional technical changes were added in the

1971 revision. Solid shaft motors were added in the 1977 revision, together with

numerous editorial changes and soft conversions

t o

the nternational system of

units. The 1977 standardwas reaffirmed in 1982 without evision.

The standard is intended

t o

serve

as

a guide in the preparation

of

specifica-

tions for the procurement of vertical turbine pumps in normal water service, as well

as an aid in designing pumps t o be used for special conditions. Material lists are

provided from which he purchaser can select the proper pump metals o r alloys

for

a

particular installation or wear environment. If any special items are not listed by

the purchaser, the selection of pump material

will

be made by the pump manufac-

turer.

II. Information RegardingUse of ThisStandard. The pump manufac-

tur er will require local basic data prior

t o

furnishing a pump and driver that will

meet the buyers needs. The nformation will include such items as the ype of prime

mover and pump that

is

being requested, as well

as

the operating range and other

pert inen t items that will be necessary in designing the unit. A specification form

that will provide the manufacturer with the needed information,

as

well as any ex-

ceptions to the standard that the useray wish t o include, is given in Appendix B.

In addition t o the information required on the suggested specification form, the

purchaser should include provisions or the following items n upplementary

specifications.

1. In all cases

a.

b.

C.

d.

e.

f.

h.

i.

j.

Standard used-that is, AWWA E101, Standard for Vertical

Turbine Pumps-Line Shaft and Submersible Types.

Certification and test results y manufacturer (Sec. A-3.3.2, Sec. A-6.2.2,

Sec. B-3.3.2, and Sec. B-6.2.2), if required.

Sanitary codes (Sec.A-3.5 and Sec. B-3.5).

Liquid to be pumped (Sec. A-1and Sec. B-1).

Details of installation,

if

other than

a

well (Sec. A-1 an d Sec. B-1).

Whether the impellers are t o be enclosed, open, r of the semiopen type

(Sec. A-4.2.2 or Sec. A-4.3.2 nd Sec. B-4.7), if here

is a

preference.

Performance tests (Sec. A-6.1 and Sec. B-6.1) th at

will

be required, if

any.

If field conditions f installation are to be duplicated

n

the laboratory

test arrangement (Sec. A-6.3 and Sec. B-6.3), provide complete etails

and a description of the arrangement.

If pump bowl assembly tests are not t o be made in open sumps

(Sec. A-6.5 and Sec. B-6.5), specify est conditions.

If bowl size exceeds 20 n. (500 mm) OD, specify the basis for

performance guarantees (Sec. A-6.9.3 and Sec. B-6.8).

vi



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k.

If tests other than those specified in

this

standard are

o

be performed

(Sec.

A-6.12

and Sec.

B-6.111,

specify.

2.

For line-shaft vertical turbine pumps, also specify

a.

Type of motor, if other than specified

in

Sec.

A-4.1.2.

b. Whether an oil-lubricated pump (Sec.

A-4.2)

or

a

water-lubricated pump

(Sec.

A-4.3)

is desired.

c. Table 1 lists two

or

more materials for certain parts. If there

is

a

preference for one material or the other, specify

in

each instance.

d. Whether pump-column sections are

t o

be joined by threaded couplings

o r

by flanges.

3.

For submersible vertical turbine pumps, also specify

a.

Whether

a

strainer (Sec.

B-4.4)w

be required.

b. Discharge-elbow head loss (Sec.

B-5.31,

f this

is

essential,

c. Table

4

lists two

or

more materials for certain parts.

If

there is

a

preference for one material

or

the other, specify in each instance.

d. Whether pump column sections are

t o

be joined by threaded couplings

or by flanges.

III. Major Revisions.

The

AWWA

Standards Committee

on

Vertical Turbine

Pumps (formerly ANSI

B58)

was reactivated

in 1985 to

review the 1977 standard

and

t o

make revisions. The committee made several editorial changes for clarity and

accuracy. The mater ial lists

in

Tables

1

and

4

were revised

t o

delete references

to

obsolete standards and

to

comply

with

current manufacturing practices.

A

formula

for design of shaft couplings was added as Sec.

A-4.1.4.

Tables for selection of

electrical cables for submersible pumps, which were included in earlier standards,

were deleted as not appropriately being

a

part of

a

pump standard.

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A WW A

ELO1

B B 0783350

0 0 0 2 7 5 3 2

American Water Works Association

AWWA E IO 1-88

Revision

of

ANSVAWWA EI

O 1

-77 [R82])

AWWA STANDARD FOR

VERTICAL TURBINE PUMPS-LINE

SHAFT A N D

SUBMERSIBLE TYPES

Part A-Line-Shaft Vertical Turbine Pumps

Part A of this standard provides minimum requirements for line-shaft vertical

turbine pumps utilizing discharge column pipe up t o and including 16 in.

(400

mm)

in size. The standard deals with

a

pump configuration up

t o

and including the

driver. Only electric motors are referred t o as prime movers.

Purchasers who intend t o use the pumps for pumping liquids other than clear,

cold water should modify the requirements t o

fit

conditions of intended use,

preferably after consultation with pump manufacturers.

A-2.1

Line-shaft vertical turbine pump:

A vertical-shaft centrifugal or mixed-

flow pump with rotating impeller or impellers, and with discharge from the pump-

ing element coaxial with the shaft. The pumping element is suspended by the con-

ductor system, which encloses

a

system of vertical shafting used

to

transmit power

t o the impellers, the prime mover being external t o th e flow stream.

A-2.2 Pump: For purposes of thisstandard,a pump may bedefined as a

device used t o provide energy for initiating

or

maintaining the movement of liquid.

A pump consists of three elements, defined as follows:

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A W W A E L O 1 8 87 8 3 3 5 00 0 2 7 5 2

4

2 AWWA El O 1-88

A-2.2.1 Th e pu mp bowl assembly

is either a single

or

multistage, centrifugal or

mixed-flow vertical pump with discharge coaxial with the shaft. It has open, semi-

open,

or

enclosed impellers. Assemblies are constructed for use with either open

or

enclosed line shafts .

A-2.2.2 The olumn-and-shaf t ssembly consists of the column ipe th at

suspends the pump bowl assembly from the head assembly and serves as a conduc-

tor

for

the fluid from the pump bowl assembly

t o

the discharge head. Contained

within the column pipe is the line shaft, which transmits the power from the driver

t o the pump shaft. The line shaft is maintained in alignment throughout its length

by means of bearings and may be enclosed in a shaft-enclosing tube and generally

lubricated with oil, or

it

may be open and lubricated with the fluid that is being

pumped.

A-2.2.3 The headassembly consists of the driver, the base fromwhich the

column-and-shaft assembly and the bowl assembly are suspended, and may include

the discharge head, which directs the fluid into the desired piping system.

A-2.2.3.1 Thedriver is he mechanismmounted on the head assembly that

transmits o r furnishes the power t o the top shaft. It may contain the means for im-

peller adjustment, and

it

provides a bearing t o carry the thrust load. It may o r may

not be a prime mover.

A-2.2.3.2

The

discharge tee,

in

a

discharge-below-base installation, is separated

from the head assembly and installed in a column pipe at a desired distance below

the head assembly.

A-2.3 Driver: For purposes of this standard,

a

driver maybedefined as a

device used to provide mechanical energy for the operation of a pump.Types of

drivers a re defined as follows:

A-2.3.1 The verticalhollow-shaftmotordrive isan electric motor having

a

motor

shaft

tha t has been bored on the center of

its

axis to receive the top shaft of

the pump. Impeller adjustment

is

made at theupper end of the motor, and a means

to carry the thruston a bearing within he motor

is

provided.

A-2.3.2 The vertical solid-shaft motor drive

is

an electric motor having a con-

ventional solid shaft coupled to the top shaft of the pump. Thecoupling should

provide

a

means for impeller adjustment. The mechanical and hydraulic thrust of

the pump is carried by a thrust bearing in the motor.

A-2.3.3 Th e vertical hollow-shaft right-angle gear drive is a gear mechanism

having a shaft that has been bored on the center of

its

axis to receive the top shaft

of

the pump. The horizontal shaft of the gear drive receives its powerfrom the

prime mover and, through a pair of bevel gears, transmits

it

t o the top shaft. Im-

peller adjustment is made

at

the upper end of the gear drive, and a means t o carry

the thrusto n a bearing within he gear drive

is

provided.

A-2.3.4 The vertical hollow-shaft belted drive

is a

flat- or V-belt-driven

mechanism having

a

shaft that has been bored on the center of

its

axis

t o

receive

the top shaft of the pump. Impeller adjustment is made at th e upper end of the

belted drive, and a means to carry he thrust on a bearing within the belted drive is

provided.

A-2.3.5 The combination drive includes a means for operating the pump with

two

or

more prime movers.

A-2.4 D at um : Theelevation of th at surface fromwhich the weight of the

pump is supported. This

is

normally the elevation of the underside of the discharge

head

o r

head base plate.



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A WW A

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0783350 0002753

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VERTICAL

TURBINE

PUMPS

3

A-2.5 Setting: The nominal vertical distance, in feet (metres), from the datum

t o the column pipe connection

at

the bowl assembly.

A-2.6 Staticwater level: Thevertical distance, in feet (metres), from the

datum t o the level of the atmospheric surface while no water is being drawn from

the pool.

A-2.7 Pum ping water level: The vertical distance, in feet (metres), from the

datum

t o

the level of the atmospheric surface while the specified fluid flow

is

being

drawn from the pool.

A-2.8

Drawdown:

The difference, in feet (metres), between the pumping water

level and the staticwater level.

A-2.9

Specif ic yield:

The r ate of flow being pumped for a well divided by the

total drawdown

as

measured during the metered flow rate.

It

is expressed in

US

gallons per minute per foot of drawdown (litres per second per metre of drawdown).

A-2.10 Pump capaci ty

Q):

The volume rate of flow, expressed in gallons per

minute (cubic metres per

hour),

produced by the pump, calculated for specified con-

ditions.

A-2.11 Pu mp speed of rotation n): The rate of rotation of the pump shaft, ex-

pressed in revolutions per minute or revolutions per second.

A-2.12

Head:

A quantity used t o express the energy content of the liquid per

unit

weight of the liquid, referred

t o

any arbitrary datum. In terms of foot-pounds

(metre-kilograms) of energy per pound (kilogram) being pumped, all head quantities

have the dimension of feet (metres) of liquid.

A-2.12.1 Head be low datum

h b

is the vertical distance, in feet (metres), be-

tween the datum and theumping water level.

A-2.12.2 Head above datum ha is

the

head measured above the datum, ex-

pressed in feet (metres) of liquid, plus the velocity head (Sec. A-2.12.3) at the point

of measurement.

A-2.12.3 Velocity head hu is the kinetic energy per unit weight of the liquid at

a given section, expressed

in

feet (metres) of liquid. Velocity head is specifically

defined by the expression

v

2

h v

=

2g

(Eq 1)

Where:

v = velocity, in feet per second (metres per second)

g = 32.17

ft/s2

9.81 d s 2 )

A-2.12.4 Suct ion head hs (closed system) is the algebraic sum of the pressure

in fee t metres) of liquid (measured at the pump suction connection) and the velocity

head at tha tpoint. Pump suction connection is thepoint at which the suction piping

is attached t o the pump bowl assembly o r its enclosing vessel. Note that a negative

suction head will add t o the vertical distance from the datum, due t o the algebraic

subtraction of

a

negative quantity.



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A W W A E LO 1 8 8 W 0 7 8 3 3 5 0 0 0 2 7 5 4 8 M

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AWWA El O 1 -88

A-2.12.5 Pu mp total head

H

is the bowl assembly head (Sec. A-2.12.6) minus

the column loss (Sec. A-2.12.7)and discharge head loss (Sec. A-2.12.8).This is the

head generally called for in pump specifications.

A-2.12.5.1 On open-suct ion nstal lat ions, pump total head

is

the sum

of

the

head below datum and the ead above datum.

A-2.12.5.2 O n closed-suction installations, pump total head is the head above

datum plus the vertical distance, in feet (metres), from the datum t o the pump suc-

tion connection minus the suction head.

A-2.12.6 Bowl assembly head hl is the energy imparted t o the liquid by the

pump bowl assembly, expressed in feet (metres) of liquid.

It

is the head developed

at

the discharge connection of the bowl assembly and is an integral multiple of the

head per stage as shown on the catalog rating chart, depending on the number of

stages in the bowl assembly.

A-2.12.7 The column

loss

hc is the value of the head loss, expressed in feet

(metres), caused by the flow friction in the column pipe.

A-2.12.8 Discharge head loss

he

is the value of the head loss, expressed in feet

(metres), caused by the flow friction in th e discharge head assembly.

A-2.13 Line-shaf t loss: Thepower,expressed

in

horsepower (kilowatts), re-

quired t o overcome the rotation friction

of

the line shaft. This value is added to the

bowl assembly input (Sec.

A-2.14.3)

o predict the pump input (Sec.

A-2.14.1).

A-2.14 Power is expressed in units of horsepower (kilowatts). One horsepower

is equivalent t o 550 ft-lb/s, 33,000 ft-lb/min, 2545 Btdh, o r 0.746 kW.

A-2.14.1 P um ppower nput is the powerdelivered

t o

the top shaR by the

driver, expressed in horsepower (kilowatts).

A-2.14.2 Driverpower nput is the power input to the driver, expressed in

horsepower (kilowatts).

A-2.14.3 Bowlassemblypower nput is the powerdelivered o the bowl

as-

sembly shaft, expressed in horsepower (kilowatts).

A-2.15 Pump power output : For

water having

a

specific weight of

62.4

lb/ft3,

(relative density of

l . O ,

pump power output is defined as QH/3960. Pump power

output s expressed in horsepower (hp x 0.746 = kW)when

Q

is

in gallons per

minute andH

is

in feet

of

water.

A-2.16 Bowl output:

For water having

a

specific weight of

62.4

lb/ft3 (relative

density of l . O ) , bowl output

is

defined

as Qhd3960.

Bowl output

is

expressed in

horsepower (hp x 0.746 = kW) when Q is in gallons per minute and hl is in feet of

water.

A-2.17 Pump eff iciency (Ep): The ratio of pump power output to pump input,

expressed

in

percent.

A-2.18 Overall ef f iciency E): The ratio of pump power output to prime mover

power input, expressed

in

percent.

A-2.19 Driver eficiency mg): The ratio of the driver power output t o the driver

power input , expressed in percent.

A-2.20 Bowl assemb ly efficiency

EI:

The ratio of the bowl output t o the bowl

assembly input, expressed in percent. This is the efficiency that isusually shown on

catalog rating charts .



13/75

A WW A E L O 1 8 8 a 0783350 0 0 0 2 7 5 5 T W

VERTICAL

TURBINE PUMPS

5

Sec. A-3.1 Standard Nomenclature

Table 1 (page

8)

ists the names of parts

in

vertical turbine pumps, the

func-

tion of each part, the material or materials from which the par t is typically made,

and the ASTM* material designation. In the table, pa rts are listed by number; the

part number refers t o the numbers in Figures

1

and 2 (pages

6

and 7).

Sec. A-3.2 Order Form

A specification form recommended for se in purchasing vertical turbine pumps

is given in Appendix

B.

Sec. A-3.3 Inspection and Certification by Manufacturer

A-3.3.1 The manufacturer shall establish the necessary quality-control and in-

spection practices t o ensure compliance with

this

standard.

A-3.3.2 The manufacturer shall,

if

required by the purchasers supplemental

specifications, furnish a sworn statemen t that the equipment furnished under the

purchasers order complies with all applicable requirements of this standard.

Sec. A-3.4 Information to Be Supplied by Bidder

The bidder shall submit, with its proposal, sufficient descriptive material

o r

outline drawings t o demonstrate compliance with this standard and thepurchasers

supplemental specifications, and a performance curve showing pump total head,

pump input power, and pump efficiency over the specified head range for the in-

stalled pump.

Sec. A-3.5 Sanitary Codes

The pump shall conform t o the sanitary codes governing the installation. The

purchaser shall furnish, as part of these Specifications, all information necessary for

the construction of the pump to meet these requirements.

Sec. A-4.1 Pump Components

A-4.1.1 Pump base. A suitable base of cast iron or fabricated steel shall be

provided for mounting the driver and supporting the pump column.

A-4.1.2 Driver. With electric power, the motor, unless specified otherwise by

the purchaser, shall be of the full-voltage starting, vertical hollow-shaft squirrel-cage

induction type, and shall comply with ANSI C50.10.t The connection

t o

the top shaft

American Society forTesting and Materials, 1916 ace

St.,

Philadelphia, PA 19103.

fANSI C50.10-General Requirements for Synchronous Machines. Available from

American National Standards Institute, 1430roadway, New York, NY 10018.



14/75

A W W A El01 88 0 7 8 3 3 5 00 0 2 7 5 6

L

6

AWWA

E101-88

Figure 1 Open line-shaft pump (surface discharge, threaded column and bowls).



15/75

AWW A

E L O 1 BI3 W

0783350

0 0 0 2 7 5 7

3

M

VERTICAL TURBINEPUMPS 7

Figure

2

Enclosed line-shaft

pump

(discharge below base, threaded column and bowls).



16/75

8 AWWA

E l

O 1-88

C

3

2

t i 3

% $

42

m

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17/75

0 0 0 2 7 5 7 7 m

W W A E L O 1

8 8

W 0 7 8 3 3 5 0

VERTICAL

TCTRBINE

PUMPS 9

5

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+

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1

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18/75

10 AWWA

E101-88

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19/75

O

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4

00

A W W A E L O 1 88

W

0783350 00027bL 5 W

VERTICAL

TURBINE PUMPS

11

U

O

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m

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20/75

12

AWWA E101-88

C

O m

4

rk

k

C

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I n I n



21/75

A WW A E L O 1 8 8 m 0783350

0 0 0 2 7 b 3

9

VERTICAL

TURBINE PUMPS 13

al

3

g

2

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+;,

o

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5

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22/75

A W W A El01 88 9 0 7 8 3 3 5 0 0 0 2 7 b l l O

H

14 AWWA E101-88

shall be through a coupling

o r

clutch in the motor head. The, motor shall be

of

the

proper size

t o drive the pump continuously over the specified operating range

without the load exceeding the nameplate rating of the motor. The motor shall be

rated as drip proof with class

B

insulation and with a

1.15

service factor.

With an engine drive, the power shall be applied

t o

the pump shaft through a

right-angle gear drive. The connection t o the vertical shaft shall be through a

cou-

pling

o r

clutch in the gear head. The horizontal shafi shall rotate in the same direc-

tion as the engine drive, and shall be connected t o the engine by a flexible shaft cou-

pling.

An optional method of driving, for an engine o r horizontal electric motor, shall

be a belted dr ive-ei ther a flat belt on a modified cylindrical pulley o r a V-belt on a

V-groove pulley.

Rotation of the vertical shaftshall be counterclockwisewhenviewed rom

above.

A thrust bearing of ample capacity

t o

carry the weight of all rotating par ts plus

the hydraulic thrus t atmaximum operating conditions shall be incorporated into the

driver. For antifriction bearings, the bearings shall beof such capacity tha t the

AFBMA*

calculated rating life

(L101

shall be no less than

8800

h. If the design and

operating conditions are such that upthrust can occur, then proper provisions shall

be made

t o

accommodate the upthrus t. This shall be done by the supplier.

A-4.1.3 Suct ionpipeandstrainer. A strainer,

if

required, shall have anet

inlet area equal to at least three times the suction pipe area . The maximum opening

shall not be more than 75 percent of the minimum opening of the water passage

through the bowl or impeller.

A-4.1.4 Shaf t coupl ings. Line shafts shall be coupled with steel couplings that

shall have a left-hand thread

t o

tighten during pump operation. The maximum com-

bined shear stress, determined by the following formula, shall not exceed 20 percent

of the elastic limit in tension nor be more than 12 percent of the ultimate tensile

strength

of

the shafting steelused.

2F 321,OOOP

s =

r

n D 2 - d 2 ) n D3

-

d3) l 2

Where:

S =

combined shear tress, n pounds per square inch

F

= total axial thrust of the shaft, including hydraulic thrus t plus the

D = outside diameter of the coupling,in inches

d =

inside diameter of the coupling a t the

root

of the threads, in inches

P

=

power transmitted by the shaft, n horsepower

n

= rotational speed of the shaft, n revolutions per minute

weight of the shaft and all rotating parts supported by it, in pounds

*Anti-FrictionBearing Manufacturers Association,1101 Connecticut Ave. N.W., Suite 700,

Washington,DC

20036.



23/75

VERTICAL TURBINE PUMPS

15

NOTE: n. x 25.40 = mm; lb x 0.454 = kg; psi x 6.895 = kPa; hp X 0.746 = kW,

rpm x 0.0167 = rps.

A-4.1.5 Bowl assembly shaft. The bowl assembly shaft shall have a surface

finish not

t o

exceed RMS-CO (ANSI B46.1*), and it shall be supported by bearings

above and below each impeller. The minimum size

of

the shaft shall be determined

by the following formula for steady loads of diffiser-type pumps with shaft in ten-

sion due

t o

hydraulic th ru st

369,OOOP

2n n

D 3 =

(Eq

3)

or

s = Il

2F ) 2 + (

nD3

21,OOOP

n

D 2

o r

P =

321,000

Where:

D = shaft diameter a t the root of the threads

or

the minimum diameter of

S =

combined shear stress, in pounds per square inch

F

=

total axial thrust of the shaft, including hydraulic thrust plus the

P

=

power transmitted by the shaft, in horsepower

n

=

rotational speed of the shaft, in revolutions per minute

any undercut, in inches

weight of the shaft and ll rotating parts supported by it, in pounds

NOTE: n. x 25.40 = m m ; lb x 0.454 = kg; psi X 6.895

=

kPa; hp X 0.746 = kW,

rpm x 0.0167 = rps.

The maximum combined shear stressS shall not exceed 30 percent of the elas-

tic limit in tension or be more than 18 percent of the ultimate tensile streng th of the

shafting steelused.

The straightness and machining tolerances shall be the same as those given

in

Sec. A-4.2.3or Sec. A-4.3.3.

*ANSI B4 6. 1S ur fac e Texture (Surface Roughness, Waviness, and Lay). Available from

American National Standards Institute, 1430 Broadway, New York, NY 10018.



24/75

A W W A E L O 1

8 8

W 0 7 8 3 3 5 0 0 0 2 7 6 6 LI

16 AWWA E101-88

Sec.

A-4.2

Oil-Lubricated Pump

Column

A-4.2.1 Pump bowls. The castings shall be free of blowholes, sand holes, and

other detrimental defects. The bowls shall be capable of withstanding a hydrostatic

pressure equal t o twice the pressure at rated capacity

or

11/2 times shut-off head,

whichever is greater. Bowls may be equipped with replaceable seal rings on the suc-

tion side of enclosed impellers. The discharge case shall be provided with a means of

reducing

to

a minimum the leakage of water into the shaft-enclosing tube, and must

have bypass ports of sufficient area t o permit the escape of water through the seal

or bushing.

A-4.2.2

Impellers.

The impellers shall beof the enclosed,semiopen, o r open

type, statically balanced. They shall be fastened securely to the impeller shaft with

keys, taper bushings, lock nuts, o r split thrust rings. They shall be adjustable verti-

cally by means of a nut in the driver

or

an adjustable coupling between the pump

and the driver.

A-4.2.3 Line

shafts.

The line shafts shall be of a material listed in Table

1

and

have a surface finish not t o exceed

RMS

40

(ANSI

B46.1), and of a size that con-

forms to Sec. A-4.1.5.

For

convenience, Table 3 (on page 22) may be used. The shaft

shall be furnished in interchangeable sections having a nominal length not

t o

exceed

20 ft

(6

m). To ensure accurate alignment of the shafts, they shall be straight within

0.005

in.

(0.13

m m )

total indicator reading for a 10-ft (3-m) section; the butting faces

shall be machined with center relief and square to the axis of the shaft; the maxi-

mum permissible error in the axial alignment

of

the thread axis with the axis of the

shaft shall be 0.002 in. in 6 in. (0.05 mm in 150

mm).

The line shaft shall be coupled

with steel couplings th at comply with the requirements of Sec. A-4.1.4.

A-4.2.4 Line-shaftbearings. The line-shaft bearings, which are also integral

tube couplings, shall be spaced not more than

5

f t (1.5 m) apart. The maximum

angle error of the thread axis t o the bore axis shall be within 0.001 in. per in. (0.001

mm per mm) of thread length. The concentricity of the bore to the threads shall be

within 0.005 in. (0.13 mm) total indicator reading. The bearings must contain one o r

more oil grooves or a separate bypass hole that will readily allow the oil

t o

flow

through and lubricate the bearings below.

A-4.2.5 Shaft-enclosingube. The shaft-enclosing tube shall be made of

schedule 80 steel pipe in interchangeable sections not more than

5

f t (1.5 m)

in

length. The ends of the enclosing tube shall be square with the axis and shall butt

t o ensure accurate alignment. The maximum angle error of the thread axis relative

t o the bore axis shall be 0.001 in. per in. (0.001 mm per mm)

of

thread length. The

enclosing tube shall be stabilized in the column pipe by stabilizers.

A-4.2.6 Discharge column pipe. The pipe size shall be such that the friction

loss will not exceed

5

f t per 100 ft (5 cm per ml, based on the rated capacity of the

pump.Thepipe shall be furnished in interchangeable sections having a nominal

length of 10 f t

(3

m); shall conform t o the provisions in Table 2; and shall be con-

nected by threaded-sleeve couplings

or

flanges. The ends of each section of the pipe

may be faced parallel and machined with threads

to

permit ends

t o

butt,

or

they

may be fured with ANSI B1.20.1 standard tapered pipe threads.

A-4.2.7 Discharge-head assembly. A t the surface or below-base discharge head,

a proper lubrication system must be installed. It shall consist

of

a manually

operated sight-feed drip lubricator and an oil reservoir, constructed as an integral

part of the head or as a separate auxiliary unit. A tubing tension nut shall be in-



25/75

VERTICAL

TURBINE PUMPS 17

Table

2

Diameters and Weights of Standard Discharge Column Pipe Sizes

Nominal Size ID) OD Weight (PlainEnds)

in.

(mm)

in.

(mm) lb

If

(kg

I

m)

2% (65)

2.875

(73.0)

5.79

(8.62)

3 (75)

3.500

(88.9)

7.58

(11.28)

4 (100)

4.500

(114.3)

10.79

(16.06)

5125)

5.563

(141.3)

14.62

(21.76)

8200)

8.625

(219.1)

24.70

(36.76)

10 (255)

10.750

(273.0)

31.20

(46.43)

12 (305)

12.750

(323.8)

43.77

(65.14)

6150)

14 (355)

14.000

(355.6)

54.57

(81.21)

16 (405)

16.000

(406.4)

62.58

(93.13)

*OD

stalled in he head to allow tension to be placed

o n

the shaft-enclosing tube.

Provision must be made for sealing off the thread

at

the tension nut.

Sec. A-4.3 Water-LubricatedPump Column

A-4.3.1

Pu mp bowls .

The castings shall be free of blowholes, sand holes, and

other detrimental defects. The bowls shall be capable of withstanding a hydrostatic

pressure equal to twice the pressure

at

rated capacity

or

1% times shut-off head,

whichever is greater. Bowls may be equipped with replaceable seal rings on the suc-

tion side of enclosed impellers.

A-4.3.2 Impellers. The impellers shall be of the enclosed, semiopen, o r open

type, statically balanced. They shall be fastened securely

t o

the impeller shaft with

keys, taper bushings, or lock nuts. They shall be adjustable vertically by means of a

nut in the driver

or

an adjustable coupling between he pump and thedriver.

A-4.3.3 Line sha f ts . The line shafts shall be of a material listed in Table 1 and

have

a

surface finish not

to

exceed

RMS

40

(ANSI

B46.1),

and of a size tha t con-

forms t o Sec. A-4.1.5 of this standard.

For

convenience, Table 3 (on page 22) may be

used. The shaft shall be furnished in interchangeable sections having a nominal

length of 10 ft (3 m). To ensure accurate alignment of the shafts, they shall be

straight within 0.005 in. (0.13 m m ) total indicator reading for

a

10-ft (3-m) section;

the butting faces shall be machined square to the axis of the shaft; the maximum

permissible error in the axial alignment of the threadaxis with the axis of the shaft

shall be

0.002

in. in

6 in. 0.05

mm in

150 mm).

The line shaftshall be coupled with

steel couplings complying with the requirements of Sec. A-4.1.4.The shaft shall be

provided with a noncorrosive wearing surface

at

the location of each guide bearing.

A-4.3.4 Line-shaf t bearings. The shaft bearings shall be designed for vertical

turbine pump service,

to

be lubricated by the liquid pumped. They shall be mounted

in bearing retainers tha t shall be held in position in thecolumn couplings by means

of the but ted ends of the column pipes. The bearings shall be spaced

at

intervals of

not more than 10 ft (3 ml.

A-4.3.5 Discharge column pipe. The pipe size shall be such that the friction

loss will not exceed

5 t

per 100 ft

5

cm per metre), based on the rated capacity of

the pump. The pipe shall be furnished in interchangeable sections having a nominal

length of not more than 10 f t (3 m); shall conform

t o

the specifications in Table 2;



26/75

18 AWWA E101-88

and shall be connected with threaded sleeve-type couplings or flanges. The ends of

each section of column pipe shall be faced parallel and the threadsmachined

t o

such

a

degree tha t the ends will butt against the bearing retainer shoulder

to

ensure

proper alignment and t o secure the bearing retainers when assembled.

A-4.3.6 Discharge-headassembly. The pump shall beprovided with a dis-

charge head of the surface

o r

underground type, as required, and shall be provided

with a shaft packing box and a renewable bronze bushing. The head shall also in-

clude a prelubrication connection

t o

wet down the line-shaft bearings adequately

before starting thepump.

A-4.3.7 Prelubrication. On installations with a setting of more than 50

R

(15

m), provisions shall be made by the manufacturer

t o

prelubricate line-shaft bearings

adequately before the pump is started.

If manual control

is

used and a source of fresh water under pressure is not

available, a prelubricating tank, with the necessary valves and fittings t o connect

it

to the pump, shall be provided. The size of the t ank shall be adequate

t o

permit a

thorough wetdown

of

all the line-shaft bearings before the power is applied, with an

adequate reserve for repeating the process in the event that the pump does not s ta rt

the first time.

If an automatic system is used, bypass fittings or other suitable means shall be

provided

t o

bring the prelubricating water from ahead of the check valve into the

prelubricating opening of the discharge head. Normally this implies the use of a

time-delay relay in the start ing system and a solenoid valve in the prelubricating

line.

A-4.3.8 Ratchets. Water-lubricated vertical turbine pumps having a setting of

50 f t

(15 m) or more shall be provided with a nonreverse mechanism in the motor

t o

protect the line shaft and the motor from reverse rotation when the power is inter-

rupted and the water mpties from the discharge column.

Sec. A-5.1 Discharge Column Pipe

Diameters and weights of standard discharge column pipe sizes are given in

Table

2.

Sec. A-5.2 Column-Friction

Loss

The column-friction chart (Figure 3) should be used as a design guide

t o

deter-

mine the loss of head due t o column friction. This chart was compiled from data on

head loss where the flow is between the inside diameter of the column pipe and the

outside diameter

of

the shaft-enclosing tube.

For open line shafting, assume the head losses

to

be equal

to

those indicated in

Figure 3 for a shaft-enclosing tube of a size that would normally enclose the open

line shaft in question.

Sec. A-5.3 Discharge Head Loss

The discharge head loss chart (Figure

4)

should be used

t o

determine the

hydraulic losses in the discharge head. Losses in discharge heads vary with the size

of the head; the design of the head; and the size of tubing o r shaft, column, and dis-

charge pipesed. Figure

4

represents estimated average lossesased on



27/75

AWWA

E l 0 1 8 8 0783350

0 0 0 2 7 6 7 T


19

Capac i t y -gpm

~OTE: riction loss determined by laboratory tests on new pipe (C = 140).

)iagonals are labeled to show n ominal diameters (in inches) of outer pipe column and inner shaft-enclosing tube. For the outer

lipe columns, the calculations used in c onstructing the chart w ere based on inside diameters, w hich are close to the nominal

izes for pipe u p to an d including 12 in. (for example, 10 in. = 10.2-in.

ID).

For pipe sizes 14 in. and larger, the diameters shown

.re equivalent

to

the outside diameter of pipe with 3/8-in. wall thickness (for example, 1 6 in.

= 15

1/4-in.

ID).

For the inner

olumns (shaft-enclosing ubes), the calculations were based on the outside diameters of standard or extra-heavy pipe. Thus, 8

: 2

on the chart is actually 8.071 x

2 3/8,

and 16 x 3 is 15 I l 4

x 3

/2.

:onversion

factor: in. x 25.40 = mm.

Figure

3

Friction-loss chart for standard pipe column.



28/75

20

AWWA E101-88

Capacity m3lh

10

20 40 60

EO 100 200

400

700

1

O00 2000

4000 10

o

Capacity-gprn

>onversion

factor: in.

x

25.40

=

mm.

Figure 4

Head

loss

in discharge heads.

manufacturers' information. When extreme accuracy is imperative, actual loss

measurements in the discharge head-with the correct tubing or shaft, column, and

discharge pipe-should be specified on the bid request by the purchaser.

Sec.

A-5.4

Mechanical Friction

The mechanical-friction chart (Figure 5 ) should be used to determine the added

horsepower required t o overcome the mechanical friction

in

rotating the line shaft.

The chart was compiled from test data submitted by representative turbine-pump

manufacturers. Variations in designs used by individual manufacturers may affect

the figures slightly.



29/75

Diamete r -mm

Diameter- in.

VOTE:

The chart shows values for enclosed shaft with oilor water lubrication and drip feed, or for open shaft with water lubrica-

:ion. For enclosed shaft with flooded tube, read two times the value of friction shown on the chart.

7 8

Figure 5 Mechanical friction in line shafts.



30/75

A W W A E L O 1

8 87 8 3 3 5 00 0 2 7 7 2

T M

22 AWWA E101-88

Table 3 Line-Shaft Selection Chart

for

Type B Material*

in.

(mm)

rpm

3/4

(19.05) 3500

2900

1760

1460

1 (25.40) 3500

2900

1760

1460

1 3/16 (30.16) 3500

2900

1760

1460

1 7/16 (36.51) 3500

2900

1760

1460

1160

960

1

1/2

(38.10) 3500

2900

1760

1460

1160

960

1

11/16

(42.86) 1760

1460

1160

960

860

71O

Power Rating-hp (hp

X

0.746= kW)

39.7

38.8

37.4 32.4

32.9 32.2 31.0 26.9

20.0 19.5

18.8

16.3

16.6 16.2

15.6

13.5

94.5 93.8

93.0

89.5 82.5

78.3 77.7 77.0

74.2 68.4

47.5

47.2

46.7

45.0 41.5

39.4 39.1 38.7 37.3

34.4

167.0

167.0

166.0

163.0 157.0

149.0

138.4 138.4

137.5

135.1 130.1

123.5

84.0

84.0

83.5 82.0

79.0

75.0

69.6

69.6

69.2 67.9

65.5

62.1

296.0

294.0 289.0 283.0 264.0

245.3

243.6 239.5 234.5 218.7

149.0

146.0 145.0

142.0

133.0

123.5 121.0

120.1

117.7

110.2

98.3 97.6 96.0 94.0

87.6

81.4

80.8 79.5 77.8 72.5

336.0

334.0 330.0 324.0 306.0

278.4 276.7

273.4

268.5

253.5

169.0 168.0 166.0 163.0 154.0

140.0 139.2 137.5 135.1 127.6

111.2 110.7

109.2

107.2

101.4

92.01.60.48.7 83.9

252.0

251.0 248.0 246.0 239.0

227.0

209.1

208.2 205.7

204.1

198.3

188.3

166.0 165.0 164.0 162.0 157.0 150.0

137.4

136.6 135.7 134.1 129.9

124.1

123.0

122.0 121.0

120.0

117.0

111.0

101.6 100.7 99.9 99.1 96.6 91.6

*Steel with a minimum elastic limitof 40,000 psi (276,000 kPa) anda minimum ultimate tensile strength

of 67,000 psi (462,000 Wal .



31/75

A W W A

E L O L 8 8 m 0783350

0002773 L

VERTICAL TZTRBINE PUMPS 23

Table

3continued

PUP

ThrUst1000

Zb

( k m

Shaft

1 2 3 5 7.5 105 200

Diameter Speed (4.448)8.896)13.344)22.24)33.36)44.48)66.72)88.96)133.44)

in. (mm)

rpm Power

Rating-hp (hp

x 0.746 =

kW)

1 15/16 (49.21)

2 3/16 (55.56)

2 7/16 (61.91)

2

l1/16

(68.26)

1760

1460

1160

960

860

71O

1760

1460

1160

960

860

71

O

1760

1460

1160

960

860

710

1760

1460

1160

960

860

710

393.0

326.0

259.0

214.3

192.0

158.5

578.0

479.5

382.0

316.1

283.0

233.6

392.0

325.2

258.0

213.5

192.0

158.5

577.0

478.7

381.0

315.3

282.0

232.8

816.0

676.9

537.0

444.4

398.0

328.6

390.0 382.0

373.0

323.5 316.9

309.4

257.0 252.0

246.0

212.7 208.6

203.6

191.0 187.0

182.0

157.7 154.4

150.3

576.0

570.0

562.0

477.8 472.8 466.2

380.0 376.0

371.0

314.5

311.2 307.0

281.0 279.0

275.0

232.0 230.3 227.0

815.0 810.0

802.0

676.1 671.9 665.3

537.0 533.0

529.0

444.4 441.1

437.8

398.0 395.0

392.0

328.6 326.1

323.6

1070.0

1062.0

1055.0

887.6 881.0

875.2

703.0 700.0

696.0

581.8 579.3

576.0

520.0 518.0

515.0

429.3 427.7

425.2

345.0

286.2

228.0

188.7

169.0

139.5

538.0

446.3

355.0

293.8

263.0

217.1

781.0

647.9

515.0

426.2

381 O

314.6

1035.0

858.6

682.0

564.4

505.0

416.9

Sec.

A-5.5

Line-Shaft Selection

Line-shaft selection shall be made in accordance with the following procedure

using Table

3, or

shall be calculated for th e specific material used in accordance

with Sec. A-4.2.3

or

Sec. A-4.3.3.

A-5.5.1 Table

3

does not limit the maximum rotative speed of shafts, the maxi-

mum setting of shafts,

or

the bearing spacing used with the shafting.

A-5.5.2Table3defines the maximum recommendedhorsepowerfor a given

size of shaft, taking into account the effect of the hydraulic thrust of the pumping

equipment and the weight of the shaft and suspended rotating parts. The table is

applicable t o any steel having a minimum elastic limit of 40,000 psi (276,000 kPa)

and a minimum ultimate ensile strength of 67,000 psi (462,000 Wa).

A-5.5.3Horsepower ratings shown in Table 3 anccalculated n accordance

with Sec. A-4.1.5 represent maximum loads and should not be increased by electric-

motor service factors.



32/75

24

AWWA

E101-88

Sec. A-6.1 Tests

A-6.1.1 The procedure

for

determining the performance of a vertical turbine

pump by making a factory laboratory test of the bowl assembly and then calculating

the anticipated field performance is describedbelow. Performance testsshall be

made only when specified in the purchasers inquiry and order. The inquiry and

order shall specify which of the following are required:

1. Running test.

2. Witnessed running test.

3.

Sample calculation from test readings.

4.

Shop inspection.

5.

Hydrostatic test

of

discharge head.

6. Hydrostatic tes t of bowl assembly.

If other tests are required, the purchaser shall describe them in detail.

A-6.1.2 The manufacturer shall notify the purchaser not less than five days

prior

t o

the date tha t the pump or pumps

will

be ready for inspection or witness

test.

Sec. A-6.2 Running Test

A-6.2.1 The pump bowl assembly will be operated from zero capacity to the

maximum capacity shownn the performance curve submitted with the

manufacturers bid. Readings shall be taken at a minimum of five capacity points,

including one point within

k

2 percent of the design capacity specified on the request

for bid.

The pump shall be operated at a speed within k

5

percent of the design speed.

This does not apply t o model

or

slow-speed tests described in Sec. A-6.9.

A-6.2.2 At the conclusion of the est, hree copies of the anticipated field-

performance curve shall be supplied

t o

the purchaser, unless the purchaser requests

tes t curves based on the actual test data without corrections for anticipated field

performance.

Sec. A-6.3 Typical Laboratory Test Arrangement

Figure 6 shows a typical laboratory arrangement for the testing of a line-shaft

vertical turbine pump. A test laboratory will normally be constructed t o provide

favorable suction conditions for pump performance. If the purchaser plans

t o

use the

pump under questionable well or sump conditions and wants the pump t o be tested

under these exact conditions, complete information should be included in the request

for bid.

If

there is nothing stated in the bid with relation t o required well or sump

conditions, it shall be assumed that standard laboratory arrangements will be used.

Sec.

A-6.4

Capacity Measurement

The capacity of the pump shall be measured by means of a standard venturi

tube, nozzle, rifice plate, pitot-tube traverse, or magnetic meter. The pump

manufacturer shall supply evidence that the capacity-measuring deviceemployed

has been properly calibrated, that

it

is in good condition, and that the pressure taps

and piping are proper for the inst rumentbeing used and are essentially the same as



33/75

AWWA.EL OL 88 W 0783350 0002775 5 W

VERTICAL TURBINE

PUMPS

25

Water Head

Datum

Manometer

Mercury Head

Manometer

5

..

.

.....?

Figure G Typical laboratory test arrangement-line-shaft

vertical

turbine pumps.

during he calibration. Ins tru ments hat have not been calibrated should be

geometrically similar t o properly calibrated models.

A description of the application of fluid meters is contained

in

the ASME publi-

cation Fluid Meters-Their Theory and Application. A detailed description of the

various meters and their application is given in Chapter

B-2

f tha t publication, the

physical constants and meter coefficients are indicated

in

Section C, and the dis-

charge coefficient tolerances of the various meters are ndicated

in

Chapter C-7.

The surface conditions, size, and lengthof the pipe precedihg the fluid-measur-

ing device are as mportan t as he calibration of the device itself. Thus, piping

should be in close conformity with th at used when the inst rumentwas calibrated

o r

in

accordance with the recommendations by the manufacturerof the fluid-measuring

device.

Fluid manometers o r other instruments of equal accuracy should be used for

measuring the pressure differential across the meter.

Sec.

A-6.5

Head Measurement

All

pump bowl assembly tests shall be made

in

open sumps, unless otherwise

stated in theequest for bid.

*Fluid-Meters-Their Theory and Application.

Rept.

ASME

Res. C o m . o n Fluid Meters.

Amer. Soc. Mech.Engr.,New York (5th ed., 1959.) Available from AmericanSociety

of

Mechanical Engineers,

345

East 47th

St.,

New York,

NY

10017.



34/75

26

AWWA E101-88

The pressure tap for headmeasurementshall be located in the discharge

column not less than 2

ft

(0.6 m) above the pump bowl assembly. The pressure tap

opening shall be a t right angles t o the pipe, free from burrs, flush with the surface

of the column pipe, and with a diameter of 1/8-1/4 in. (3.18-6.35 m m ) .

As an alte rnate method, the pressure tap for head measurement can also be lo-

cated not less than 10 diameters downstream from the discharge elbow of the test

pump. (The elbow

t o

be furnished with the pump shall be used.) When the pump

head is measured a t this point, no deduction for elbow oss need be made in an-

ticipating field performance.

For head measurements of 36

f t (11

m) or less, only fluid manometers shall be

used. For head measurements in excess of 36 f t (11m), calibrated bourdon or other

gauges with equivalent accuracy and reliability can be used. All gauges shall be

calibrated before and after each series of tests.

Sec.

A-6.6

Velocity Head

The average velocity in the pump column used t o determine the velocity head

shall be calculated from dimensions obtained by actual internal measurement of the

pipe and external measurement of the shaft or enclosing tube at th e point of pres-

sure measurement.

If the pressure measurement is made downstream from the discharge elbow,

the velocity head shall be obtained from actual measurement of the inside diameters

of the discharge pipe at th epoint where the pressure tap is ocated.

Sec. A-6.7 Horsepower Input

The power input t o the pump shall be determined with a vertical dynamometer

or a calibrated electric motor.

The torque of the dynamometer shall be measured by means

of

a calibrated

scale, calibrated strain gauge, or other device of equivalent accuracy.

Squirrel-cage induction motors (when operated at greater than half the

nameplate rating), direct-current motors, synchronous motors, or wound-rotor induc-

tion motors with short-circuited secondary resistance may be employed for the deter-

mination of shaft input, provided the efficiencies or losses have been ascertained by

an IEEE test r its equivalent.

When the specifications call

for

an overall efficiency guarantee, the actual job

motor can be used without calibration and the overall efficiency calculated directly.

Calibrated laboratory-type electric meters and transformers shall be used

t o

measure power input

t o

all motors.

Sec. A-6.8 Measurement

of

Speed

The rotating speed of the pump shall be obtained by a hand counter, electronic

computer, o r a stroboscope counting slip.

It

should be noted that an accurate speed

reading is important

in

determining power input when a dynamometer is used. Ac-

curacy is less important when a calibrated motor is used.

*Institute of Electrical

and

Electronics

Engineers,

345 East 47th St., New York, NY 10017.



35/75

A WWA E L O 1 8 1 W 0783358 0002777 9 W


27

Sec. A-6.9 Large-Pump Tests

A-6.9.1 On all pump bowl assemblies where the horsepower

is

not in excess of

200 hp (150 kW) and the bowl diameter is not in excess

of

20 in. (500 mm), the ac-

tual pump shall be tested in the manufacturers laboratory.

A-6.9.2 If th e horsepower exceeds 200 hp (150 kW), it shall be permissible for

the manufacturer

t o

test only the number of stages of the

unit

th at come within this

power requirement. If a test is made on

a

limited number of stages,

no

increase in

efficiency shall be permitted for an increased number of stages when predicting the

final performance of the complete bowl assembly. The head andhorsepower shall be

increased in .direct proportion

to

the number of stages in the final assembly, com-

pared with the number of stages used in the aboratory test.

A-6.9.3 When the size of the bowls exceeds 20-in. (500-mm)

OD,

a laboratory

test 0n.a model pump, homologous with the actual unit, may be used as

a

basis for

the determination of the performance of the actual unit.

NOTE:

In general, when contract guarantees are

to

be based on model tests,

the contract should specify model performance rather than inferred actual-unit per-

formance. In theabsence of this provision, allowance for he scale effect, if any, shall

be agreed on in writing by the representatives of both parties prior

to

the tests.

The model pump shall be r un at a speed sufficient

to

develop

a

head per stage

at leas t equal to that of the actual unit, so that the velocities will equal os exceed

those of the actual unit;

or

the manufacturer must submit evidence that

a

single-

stage model does not cavitate under specified field suction conditions when operated

at a speed such tha t thevelocities will equal

or

exceed those of the actual unit.

A-6.9.4 On bowl assemblies that have an OD exceeding 20 in.

(500

mm) os re-

quire more than 200 hp (150 kW),

it

shall be permissible to test the actual bowl as-

sembly at a speed slower than that at which the pump

will run

in the field, rather

than make

a

model test.

No

efficiency increase will be allowed when the perfor-

mance in the slow-speed tes t is translated into that at ull speed. The manufacturer

must submit evidence that a single-stage bowl assembly

o r

a single-stage model does

not cavitate under specified field suction conditions when operated

at

a speed such

that thevelocities willequal

o r

exceed those of the actual unit.

A-6.9.5 All large bowl assembly

full

speed tests o r model tests should be con-

ducted with identical submergence tha t will exist in the field, as shown on the re-

quest for bids, except as otherwise agreed on between the manufacturer and t he

purchaser.

Sec. A-6.10 Hydrostatic Tests

A-6.10.1 A hydrostatic test on the pump bowl castings shall be made at

1

times the shut-off head developed by the pump bowl assembly or at twice the rated

head, whichever is greater.

A-6.10.2 A hydrostatic test on the discharge head shall be made at the pres-

sure defined in Sec. A-6.10.1, less the pump setting specified on th e order.

Sec.

A-6.11

Recording and Computationof Test Results

A-6.11.1

All

instrument test readings, as well as corrected readings, shall be

recorded on the test sheet. Complete data concerning the pump, driver, and instru-

ment identification shall also be recorded.



36/75

WW E L O 1 8 87 8 3 3 5 00 0 2 7 7 8

0

M

28

AWWA E101-88

A-6.11.2 All test results shallbe translated into performance at the anticipated

speed of the driver a t th e esign point by the following formulas:

Q = Q t

(

nt 1

H = H t

(

nt

P = P t

(

nt l 3

L

Where:

Q = pumpcapacity,

in

gallons perminute (cubic metresperhour)

t =

indicated tes t values

n = anticipatedoperating speed, in revolutions perminute

H =

head, in feet (metres)

P

=

power, in horsepower (kilowatts)

(revolutions per second)

NOTE:

gpm x 0.2271 = m3/h; rpm

x

0.0167 = rps;

f t x

0.3048 = m; hp x 0.746 =

kW.

A-6.11.3 The bowl assembly input power Pl in horsepower, when measured by

a vertical dynamometer, is found using the expression

Where:

K

=

dynamometer constant, 2d/33,000

Where:

L = length of the lever arm, n feet (metres)

F

=

net force

at

the end of the lever arm, n pounds (Newtons)

nt = speed of the driver when the test reading is taken, in revolutions

per minute (revolutions per second)

NOTE: f t x 0.3048 = m; lb x 4.448 = N; rpm

x

0.0167 = rps.

A-6.11.4 The lectric-motor ower input,n horsepower, is the corrected

kilowatt input

to

motor divided by

0.746.



37/75

A WW A E L O 1 88783350002777

2 W

VERTICALTURBINE

PUMPS

29

A-6.11.5 The bowl assembly input power P I ,

in

horsepower, t o a pump driven

by an electric motor is

kW

0.746

P1 =

Eg

Where:

kW

= corrected kilowatt input t o motor

E g =

motor efficiency from the calibration curve

A-6.11.6

The pump-bowl assembly efficiency

E1 is

Qhl

E1 =

3960 x

P I )

Where:

Q

=

measured capacity, in gallons per minute

hl = bowl assembly head, including velocity head, in feet

P1 = brake horsepower

t o

the pump bowl assembly, measured by

dynamometer or calibrated motor

NOTE: gpm 0.2271

=

m3k; f t x

0.3048

=

m; hp x 0.746 = kW.

A-6.11.7

The pump total head

H , in

feet, is found by

Where:

hl

=

bowl assembly head from test, in feet

h c =

column loss, in feet, obtained from Figure 3 and based on

complete pump setting

h e

= discharge head loss, in feet, from Figure

4

or actual test

NOTE: f t x 0.3048 = m.

A-6.11.8

The pump input power, in horsepower, is found by

P = P l

+

PC

+

Pt. (Eq 13)

Where:

P1 =

bowl assembly input power, in horsepower, calculated from test,

as inSec.

A-6.11.3

o r Sec.

A-6.11.5



38/75

30

AWWA E101-88

PC = line-shaft loss in power, in horsepower, obtained from Figure 5 and

Pt =

thrust-bearing loss, in horsepower

NOTE: hp

X

0.746 = kW.

based on complete pump setting

A-6.11.9 The pump efficiency E p is found using the equation

H

E p =

3960 x P

(Eq 14)

in which the pump total head

H ,

in feet f t x 0.3048

=

m), is obtained from Sec. A-

6.11.7 and the power input P in horsepower (hp x 0.746 = kW), is obtained from

Sec. A-6.11.8.

A-6.11.10

The overall efficiency E is the pump efficiency

E p

multiplied by the

driver efficiencyEg.

A-6.11.11 The completepump totalhead, efficiency, and pump input power

should be plotted as ordinates on the same sheet against the capacity as abscissa t o

show the anticipated field performance

of

the complete pumps.

Sec.

A-6.12

Other Tests

For more complete tests or for tests involving fluids other than water refer

t o

Hydraulic Institute test standards, as pplicable.

*Hydraulic Institute, 712 LakewoodCenterNorth, 14600 Detroit Ave., Cleveland, OH

44107.



39/75

AWWP E L O 1 B 8

W 0783350

0002781 O

Part

B-SUBMERSIBLE VERTICAL TURBINE PUMPS

Part B of this standard provides minimum requirements for submersible verti-

cal turbine pumps utilizing a T1/2-hp motor o r larger.

Purchasers who intend t o use the pumps for pumping liquids other th an clear,

cold water should modify the requirements, preferably after consultation with pump

manufacturers, t o fit conditions of intended use.

In addition

to

the defmitions in this section, Sec. A-2.4 through Sec. A-2.12 and

Sec. A-2.14 through Sec. A-2.20 (line-shaft pumps) also apply t o submersible pumps.

B-2.1 Submersible pump: An integral combination of a vertical turbine pump

close coupled t o an electric motor designed for sustained and continuous operation

under water. The unit is suspended from a surface plate by the vertical discharge

pipe and receives electrical energy through a submersible power cable. This type of

pump has no line shaft

or

shaft-enclosing tube.

B-2.2 Pump:

Forpurposes of thisstandard,

a

pump may bedefmed asa

device used

t o

provide energy for initiating or maintaining the movement of liquid.

A pump consists of seven elements, defhed as ollows:

B-2.2.1 The pump. bowl assembly is

a

single or multistage, centrifugal o r

mixed-flow vertical pump with discharge coaxial with the shaft.

It

can have open,

semiopen,

or

enclosed impellers.

B-2.2.2 The vertical discharge pipe conducts water from the pump bowl as-

sembly t o the surface-plate connection. It supports the pump and driver in the well

and also supports an electric cable tha t carries curren t from the surface to the motor

lead connection.



40/75



41/75

A WW A E L O 1 8 8 .O783350 0 0 0 2 7 8 3

LI

W

VERTICAL TURBINE

PUMPS

33

Sec.

B-4.1

Submersible Motor

B-4.1.1

Materials.

Construction materials shall be suitable for their applica-

tion from the standpoints of corrosion resistance and mechanical performance.

B-4.1.2

Design.

The motor shall bef the squirrel-cage induction type,

suitable for across-the-line sta rting and shall be capable of reduced-voltage starting.

It shall be capable of continuous operation under waterat the conditions specified.

B-4.1.3 Temperature. The motor temperature shall be rated no higher than

the allowable operating temperature of the motor thrust and radial bearings and in

no case shall it exceed the tempera ture rating of the insulation class used to wind

the motor.

B-4.1.4 Thrus t bear ing . A thrust bearing of ample capacity t o carry the weight

of al l rotating par ts plus the hydraulic thrust at maximum operating head shall be

an integral p art of the driver.

For

antifriction bearings, the bearing shall be of such

capacity that the

AFBMA

calculated rat ing life

(Lid

shall be no less than 8800 h.

If the design and operating conditions are such that up thrust canccur, then proper

provision shall be made

to

accommodate the upthrust . This shall be done by the

supplier.

It

shall also have ample capacity

t o

permit the pump t o operate for short

periods with the discharge valveclosed.A

AWWA E 101 (Vertical Turbine Pumps).pdf

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