AWWA E 101 (Vertical Turbine Pumps).pdf

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American Water Works Association

ANSVAWWA E l O1-88 (Revision of ANSVAWWA E101-77 [R82])

AWWA STANDARD

FOR

VERTICAL TURBINE PUMPS-LINE SHAFT AND 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 Institute,h . , May 31,1988.

AMERICAN WATER WORKS ASSOCIATION 6666 West Quincy Avenue, Denver, Colorado 80235

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A W A Standard This document is an American Water Works Association (AWWA) standard. It 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 contain options that must be evaluated by the user of the standard. Until each optional feature is specified by the user, the product or service is not fully defined. AWWA publication of a standard does not constitute endorsementof any product or product type, nor does AWWA test, certify, or approve any product. The use ofAWWA standards is entirely voluntary. AWWA standards are intended to representa consensus of the water supply industly that the product described will provide satisfactory service. When AWWA revises or withdraws this standard, an official notice of action will be placed on the first 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 publication of the official notice.

American National Standard An American National Standard implies a consensus of those substantiallyconcerned with its scope and provisions. An American National Standard is intended as a guide to aid the manufacturer, the consumer, and the general public. The existence of an American National Standard does not in any respect precludeanyone, whetherhe has approved thestandard or not, from manufacturing, marketing, purchasing, or using products, processes, or procedures not conforming to the standard. American National Standards are subject to periodic review, and users are cautioned to obtain the latest editions. Producers of goods made in conformity with an American National Standard are encouraged to state on their own responsibility in advertising and promotional materials or on tags or labels that thegoods are produced in conformity with particularAmerican National Standards.

CAUTIONNOTICE:TheAmerican National Standards Institute (ANSI) approval date on the front cover of this standard indicates completion of the ANSI approval process. This American National Standard may be revised or withdrawn at any time. ANSI procedures require that action be taken to reaffirm, revise, or withdraw this standard no later 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, N Y 10018 (212) 354-3300.

Copyright O 1988 by American Water Works Association Printed in USA

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Committee Personnel The Subcommittee o n Revision ofANSUAWWA standard, had thefollowing personnel at the time:

E101, whichdeveloped this

Chester A. Green, Chairman 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 the following personnel at the time of approval: Chester A. Green, Chairman

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,Inc., Los Angeles, Calif. Chi-Seng Yang, GouldsPumps, Inc., Lubbock, Texas

*Liaison, nonvoting ?Alternate

...

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Contents SEC.

SEC.

PAGE

Foreword I History of Standard .......................... II Information Regarding Use of This Standard ................................ III Major Revisions ..............................

PAGE

A-6.4 Capacity Measurement ................... A-6.5 Head Measurement ......................... A-6.6VelocityHead ................................... A-6.7Horsepower Input ............................ A-6.8 Measurement of Speed .................... A-6.9Large-Pump Tests ........................... A-6.10 Hydrostatic Tests ............................ A-6.11 Recording and Computation of Test Results ................................... A-6.12 Other Tests ......................................

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Part A-Line-Shaft Vertical Turbine Pumps

24 25 26 26 26 27 27 27 30

A-1

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

1

A-2

Definitions .......................................

1

A-3 A-3.1 A-3.2 A-3.3

General

Part B-Submersible Vertical Turbine Pumps

5 5

B-1

ScopeandPurpose ......................

31

B-2

Definitions .....................................

31

Standard Nomenclature .................... Order Form ........................................ Inspection and Certification by Manufacturer .................................. A-3.4 Information to Be Supplied by Bidder .............................................. A-3.5 Sanitary Codes ...................................

5

B-3 General B-3.1 Standard Nomenclature .................. B-3.2 Order Form ...................................... B-3.3 Inspection and Certification by Manufacturer ................................ B-3.4 Information to Be Supplied by Bidder ............................................ B-3.5 Sanitary Codes ................................

5 5

Specifications A-4 A-4.1 Pump Components ............................. 5 A-4.2 Oil-Lubricated Pump Column ........ 16 A-4.3 Water-Lubricated Pump 17 Column........................................... 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

B-4 Specifications B-4.1 Submersible Motor .......................... B-4.2 Submersible Cable ........................... B-4.3 Surface Plate .................................... B-4.4 Strainer ............................................ B-4.5Discharge Pipe ................................. B-4.6 Pump Bowls ..................................... B-4.7 Impellers .......................................... B-4.8 Pump MotorCoupling .....................

Engineering Data Discharge Column Pipe ................... Column-Friction Loss ...................... Discharge Head Loss ....................... Mechanical Friction ......................... Line-Shaft Selection ........................

18 18 18 20 23

Factory Inspection and Tests Tests ................................................. Running Test ................................... Typical Laboratory Test Arrangement .................................

24 24

32 32 32

33 33 41 41 41 42 42 42

B-5 Engineering Data B-5.1Discharge Pipe ................................. 42 B-5.2 Discharge Friction Loss .................. 42 B-5.3Discharge-Elbow Head Loss ........... 42

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SEC.

SEC.

PAGE

7

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 46 B-6.5 Head Measurement ......................... 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

8

9 10 11

12 A.1

Appendices

A

A.2

Field Testing of Vertical Turbine Pumps

A.3

Purpose of Field Tests ..................... 50 Accuracy of Field Testing................ 50 Definitions and Symbols ................. 54 Approved Instrumentation.............. 55 Test Procedure ................................. 61

A.4

A.5

B

Suggested Specification Form for the Purchase of Vertical Turbine Pumps.......... 66

Typical Submersible-Pump Assembly (Bowl Assemblies)........ 34 Submersible-Pump Discharge 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 ThreeConductor Copper Cable............... 48 Field-Test Diagram for Line-Shaft Vertical Turbine Deep-Well Pump .............................................. 55 Field-Test Diagram for Submersible Pump ........................ 56 Field-Test Diagram for Vertical Turbine Pump for Booster 56 Service............................................ Piping Requirements for Orifices, Flow Nozzles, and Venturi Tubes .............................................. 57 Field-Test Report Form.......,...........62

Tables 1 Standard Nomenclature-LineShaft Vertical Turbine Pumps ....... 8 2 Diameters and Weights of Standard Discharge Column Pipe Sizes....................................... 17 3 Line-Shaft Selection Chart for Type B Material ............................ 22 4 Standard NomenclatureSubmersible Vertical Turbine Pumps ............................................ 36 A.l Limits of Accuracy of PumpTest Measuring Devices in Field Use ........................................ 51

Figures 1 Open Line-Shaft Pump (Surface Discharge, Threaded Column, and Bowls) ....................................... 6 2 Enclosed Line-Shaft Pump (Discharge Below Base, Threaded Column, and Bowls)........................ 7 3 Friction-Loss Chart for Standard 19 Pipe Col................................... 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

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Foreword This foreword is for informationonly 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 to 1986 by committees consisting of manufacturers, consumers, and engineers. The first standard was published in 1955. In 1961 the standard was revised to include standards for submersible vertical turbine pumps. Additional technical changes were added in the 1971 revision.Solid shaft motorswere added in the 1977 revision, together with numerous editorial changes and soft conversions to theinternational system of units. The 1977 standardwas reaffirmed in 1982 withoutrevision. The standard is intended to serve as a guide in the preparation of specifications for the procurement of vertical turbine pumps in normal water service, as well as an aid in designing pumps to be used for special conditions. Material lists are provided from whichthe purchaser can select the proper pump metals or 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 manufacturer. II. Information RegardingUse of ThisStandard. The pump manufacturer will require local basic data prior to furnishing a pump and driver that will meet the buyer’s needs. Theinformation will include such items as thetype of prime mover and pump that is being requested, as well as the operating range and other pertinent 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 exceptions to the standard that the user may wish to include, is given in Appendix B. In addition to the information required on the suggested specification form, the purchaser should include provisionsfor the following itemsinsupplementary specifications. 1. In all cases a. Standard used-that is, AWWA E101, Standard for Vertical Turbine Pumps-Line Shaft and Submersible Types. b. Certification and test resultsby manufacturer (Sec. A-3.3.2, Sec. A-6.2.2, Sec. B-3.3.2,and Sec. B-6.2.2), ifrequired. C. Sanitary codes (Sec. A-3.5 and Sec. B-3.5). d. Liquid to be pumped (Sec. A-1and Sec. B-1). e. Details of installation, if other than a well (Sec. A-1and Sec. B-1). f. Whether the impellers are to be enclosed, open,or of the semiopen type (Sec. A-4.2.2 or Sec. A-4.3.2 and Sec. B-4.7), ifthere is a preference. Performance tests (Sec. A-6.1 and Sec. B-6.1)that will be required, if any. h. If field conditionsof installation are to be duplicatedin the laboratory test arrangement (Sec. A-6.3 and Sec. B-6.3), provide completedetails and a description of the arrangement. i. If pump bowl assembly tests are not to be made in open sumps (Sec. A-6.5 and Sec. B-6.5), specifytest conditions. j. If bowl size exceeds 20in. (500 mm) OD, specify the basis for performance guarantees (Sec. A-6.9.3 and Sec. B-6.8).

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k. If tests other than those specified in this standard are t 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 to be joined by threaded couplings or by flanges. 3. For submersible vertical turbine pumps, also specify a. Whether a strainer (Sec. B-4.4) w l ibe required. b. Discharge-elbow head loss (Sec. B-5.31,if 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 to 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 material lists in Tables 1 and 4 were revised to 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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American Water Works Association

AWWA E IO1-88

(Revision of ANSVAWWA EI O1 -77 [R82])

AWWA STANDARD FOR

VERTICAL TURBINE PUMPS-LINE SHAFT AND 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 to 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 to 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 mixedflow pump with rotating impeller or impellers, and with discharge from the pumping element coaxial with the shaft. The pumping element is suspended by the conductor system, which encloses a system of vertical shafting used to transmit power t o the impellers, the prime mover being external t o the 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 ELO1 80 87 8 3 3 50 0 0 2 7 5 2 2

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A-2.2.1 The pump bowl assembly is either a single or multistage, centrifugal or mixed-flow vertical pump with discharge coaxial with the shaft. It has open, semiopen, or enclosed impellers. Assemblies are constructed for use with either open or enclosed line shafts. A-2.2.2 Thecolumn-and-shaftassembly consists of the columnpipe that suspends the pump bowl assembly from the head assembly and serves as a conductor for the fluid from the pump bowl assembly to the discharge head. Contained within the column pipe is the line shaft, which transmits the power from the driver to 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 the mechanismmounted on the head assembly that transmits or furnishes the power to the top shaft. It may contain the means for impeller adjustment, and it provides a bearing to carry the thrust load. It may or 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 are defined as follows: A-2.3.1 The verticalhollow-shaftmotordrive isan electric motor having a motor shaft that 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 withinthe motor is provided. A-2.3.2 The vertical solid-shaft motor drive is an electric motor having a conventional 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 The 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 to the top shaft. Impeller adjustment is made at the upper end of the gear drive, and a means to carry the thruston a bearing withinthe 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 to receive the top shaft of the pump. Impeller adjustment is made at the upper end of the belted drive, and a means to carry the 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 Datum: Theelevation of that surface fromwhich the weight of the pump is supported. This is normally the elevation of the underside of the discharge head or head base plate.

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VERTICAL TURBINE PUMPS

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A-2.5 Setting: The nominal vertical distance, in feet (metres), from the datum to the column pipe connectionat the bowl assembly. A-2.6 Staticwater level: Thevertical distance, in feet (metres), from the datum to the level of the atmospheric surface while no water is being drawn from the pool. A-2.7 Pumping water level: The vertical distance, in feet (metres), from the datum to 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 Specific yield: The rate 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 capacity (Q):The volume rate offlow, expressed in gallons per minute (cubic metres per hour), produced by the pump, calculated for specified conditions. A-2.11 Pump speed of rotation (n): The rate of rotation of the pump shaft, expressed in revolutions per minute or revolutions per second. A-2.12 Head: A quantity used to express the energy content of the liquid per unit weight of the liquid, referred to 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 below datum h b is the vertical distance, in feet (metres), between the datum and the pumping water level. A-2.12.2 Head above datum ha is the head measured above the datum, expressed 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

hv

=

v2 2g

(Eq 1)

Where:

v g

= =

velocity, in feet per second (metres per second) 32.17 ft/s2(9.81 d s 2 )

A-2.12.4 Suction head hs (closed system) is the algebraic sum of the pressure in feet(metres) of liquid (measured at the pump suction connection) and the velocity head at thatpoint. Pump suction connection is thepoint at which the suction piping is attached to the pump bowl assembly or its enclosing vessel. Note that a negative suction head will add t o the vertical distance from the datum, due to the algebraic subtraction of a negative quantity.

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A-2.12.5 Pump 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 O n open-suction installations, pump total head is the sum of the head below datum and thehead above datum. A-2.12.5.2 On closed-suction installations, pump total head is the head above datum plus the vertical distance, in feet (metres), from the datum to the pump suction connection minus the suction head. A-2.12.6 Bowl assembly head hl is the energy imparted to 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 the discharge head assembly. A-2.13 Line-shaft loss: Thepower,expressed in horsepower (kilowatts), required to overcome the rotation friction of the line shaft. This value is added to the bowl assembly input (Sec. A-2.14.3) to predict the pump input (Sec. A-2.14.1). A-2.14 Power is expressed in units of horsepower (kilowatts). One horsepower is equivalent to 550 ft-lb/s, 33,000 ft-lb/min, 2545 Btdh, or 0.746 kW. A-2.14.1 Pumppowerinput is the powerdelivered to the top shaR by the driver, expressed in horsepower (kilowatts). A-2.14.2 Driverpowerinput is the power input to the driver, expressed in horsepower (kilowatts). A-2.14.3 Bowlassemblypowerinput is the powerdeliveredto the bowl assembly 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), pumppower output is defined as QH/3960. Pump power output is 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 efficiency (Ep): The ratio of pump power output to pump input, expressed in percent. A-2.18 Overall efficiency (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 to the driver power input, expressed in percent. A-2.20 Bowl assembly efficiency EI:The ratio of the bowl output to the bowl assembly input, expressed in percent. This is the efficiency that is usually shown on catalog rating charts.

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Sec. A-3.1 Standard Nomenclature Table 1 (page 8) lists the names of parts in vertical turbine pumps, the function of each part, the material or materials from which the part is typically made, and the ASTM* material designation. In the table, parts are listed by number; the part number refers to the numbers in Figures 1 and 2 (pages 6 and 7).

Sec. A-3.2 Order Form A specification form recommended for use 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 inspection practices to ensure compliance with this standard. A-3.3.2 The manufacturer shall, if required by the purchaser’s supplemental specifications, furnish a sworn statement that the equipment furnished under the purchaser’s 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 or outline drawings to demonstrate compliance with this standard and thepurchaser’s supplemental specifications, and a performance curve showing pump total head, pump input power, and pump efficiency over the specified head range for the installed pump.

Sec. A-3.5 Sanitary Codes The pump shall conform to 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 to the top shaft

“American Society forTesting and Materials, 1916Race St., Philadelphia, PA 19103.

fANSI C50.10-General Requirements for Synchronous Machines. Available from American National Standards Institute, 1430 Broadway, New York, NY 10018.

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

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A W W A E L O 1 BI3 W 0783350 0 0 0 2 7 5 7 3 M VERTICAL TURBINE PUMPS

Figure 2 Enclosed line-shaft pump (discharge below base, threaded column and bowls).

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COPYRIGHT American Water Works Association Licensed by Information Handling Services

11

12

AWWA E101-88 C

O

m

C

kl

3

8

4 k

rk

m I

COPYRIGHT American Water Works Association Licensed by Information Handling Services

n

I

m n

A W W A ELO1 8 8

m 0783350

00027b3 9 VERTICAL TURBINE PUMPS

al

3 Y g

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+;,

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COPYRIGHT American Water Works Association Licensed by Information Handling Services

8

a G

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13

A W W A El01 8 8 9 0 7 8 3 3 5 00 0 0 2 7 b l l 14

O H

AWWA E101-88

shall be through a coupling or clutch in the motor head. The, motor shall be of the proper size to 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 to the pump shaft through a right-angle gear drive. The connection to the vertical shaft shall be through a coupling or clutch in the gear head. The horizontal shafi shall rotate in the same direction as the engine drive, and shall be connected t o the engine by a flexible shaft coupling. An optional method of driving, for an engine or horizontal electric motor, shall be a belted drive-either a flat belt on a modified cylindrical pulley or a V-belt on a V-groove pulley. Rotation of the vertical shaftshall be counterclockwisewhenviewedfrom above. A thrust bearing of ample capacity to carry the weight of all rotating parts plus the hydraulic thrust atmaximum operating conditions shall be incorporated into the driver. For antifriction bearings, the bearings shall beof such capacity that 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 to accommodate the upthrust. This shall be done by the supplier. A-4.1.3 Suctionpipeandstrainer. 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 Shaft couplings. Line shafts shall be coupled with steel couplings that shall have a left-hand thread to tighten during pump operation. The maximum combined 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.

r

s =

2F

n (D2-d2)

1

321,OOOP +

n (D3 - d3)

l2

Where: S F

= =

D

= =

d P n

= =

combined shearstress,in pounds per square inch total axial thrust of the shaft, including hydraulic thrust plus the weight of the shaft and all rotating parts supported by it, in pounds outside diameter of the coupling, in inches inside diameter of the coupling at the root of the threads, in inches power transmitted by the shaft,in horsepower rotational speed of the shaft,in revolutions per minute

*Anti-FrictionBearing Manufacturers Association,1101 Connecticut Ave. N.W., Suite 700, Washington, DC 20036.

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VERTICAL TURBINE PUMPS

NOTE:in. x 25.40 = mm; lb x 0.454 = kg; psi x 6.895 = kPa; hp rpm x 0.0167 = rps.

X

15

0.746 = kW,

A-4.1.5 Bowl assembly shaft. The bowl assembly shaft shall have a surface finish not to 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 tension due t o hydraulic thrust

D3

=

369,OOOP 2n n

-

(Eq 3)

or

s

=

Il(

2F n D2

)2+(

321,OOOP nD3

or

P

=

321,000

Where:

D

=

S F

= =

P n

= =

shaft diameter at the root of the threads or the minimum diameter of any undercut, in inches combined shear stress, in pounds per square inch total axial thrust of the shaft, including hydraulic thrust plus the weight of the shaft andall rotating parts supported by it, in pounds power transmitted by the shaft, in horsepower rotational speed of the shaft, in revolutions per minute

NOTE:in. x 25.40 = m m ; lb x 0.454 = kg; psi rpm x 0.0167 = rps.

X

6.895 = kPa; hp

X

0.746 = kW,

The maximum combined shear stressS shall not exceed 30 percent of the elastic limit in tension or be more than 18 percent of the ultimate tensile strength 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 B46.1Surface Texture (Surface Roughness, Waviness, and Lay). Available from American National Standards Institute, 1430 Broadway, New York, NY 10018.

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A W W A ELO1 8 8 W 0 7 8 3 3 5 00 0 0 2 7 6 6 16

LI

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 to 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 suction 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 to permit the escape of water through the seal or bushing. A-4.2.2 Impellers. The impellers shall beof the enclosed,semiopen, or open type, statically balanced. They shall be fastened securely to the impeller shaft with keys, taper bushings, lock nuts, or split thrust rings. They shall be adjustable vertically 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 beof a material listed in Table 1 and have a surface finish not to exceed RMS 40 (ANSI B46.1), and of a size that conforms 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 to 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 maximum 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 that 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 ft (1.5m) apart. The maximum angle error of the thread axis to 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 or more oil grooves or a separate bypass hole that will readily allow the oil to flow through and lubricate the bearings below. A-4.2.5 Shaft-enclosing tube. The shaft-enclosing tube shall be made of schedule 80 steel pipe in interchangeable sections not more than 5 ft (1.5 m) in length. The ends of the enclosing tube shall be square with the axis and shall butt to ensure accurate alignment. The maximum angle error of the thread axis relative to 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. Thepipesize shall be such that the friction loss will not exceed 5 ft 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 ft (3 m); shall conform to the provisions in Table 2; and shall be connected 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 to butt, or they may be fured with ANSI B1.20.1 standard tapered pipe threads. A-4.2.7 Discharge-head assembly. At 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-

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VERTICAL TURBINE PUMPS

17

Table 2 Diameters and Weights of Standard Discharge Column Pipe Sizes Nominal Size (ID) in. (mm)

(125) (150) (200)

2% 3 4 5 6 8 10 12 14" 16"

(65) (75) (100)

(255) (305) (355) (405)

OD in.

(mm)

Weight (Plain Ends) lb If¿ (kg I m)

2.875 3.500 4.500 5.563

(73.0) (88.9) (114.3) (141.3)

5.79 7.58 10.79 14.62

(8.62) (11.28) (16.06) (21.76)

8.625 10.750 12.750 14.000 16.000

(219.1) (273.0) (323.8) (355.6) (406.4)

24.70 31.20 43.77 54.57 62.58

(36.76) (46.43) (65.14) (81.21) (93.13)

*OD

stalled inthe head to allow tension to be placed o n the shaft-enclosing tube. Provision must be made for sealing off the threadat the tension nut.

Sec. A-4.3 Water-LubricatedPump Column A-4.3.1 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 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 suction side of enclosed impellers. A-4.3.2 Impellers. The impellers shall be of the enclosed,semiopen, or open type, statically balanced. They shall be fastened securely to 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 betweenthe pump and thedriver. A-4.3.3 Line shafts. 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 that conforms to 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-shaft 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 that shall be held in position in thecolumn couplings by means of the butted 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 ft 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 ft (3 m); shall conform to the specifications in Table 2;

COPYRIGHT American Water Works Association Licensed by Information Handling Services

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 to such a degree that the ends will butt against the bearing retainer shoulder to ensure proper alignment and to secure the bearing retainers when assembled. A-4.3.6 Discharge-headassembly. The pump shall beprovided with a discharge head of the surface or underground type, as required, and shall be provided with a shaft packing box and a renewable bronze bushing. The head shall also include a prelubrication connection to 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 to 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 to connect it to the pump, shall be provided. The size of the tank shall be adequate to 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 start the first time. If an automatic system is used, bypass fittings or other suitable means shall be provided to 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 starting system and a solenoid valve in the prelubricating line. A-4.3.8 Ratchets. Water-lubricated vertical turbine pumps having a setting of 50 ft (15 m) or more shall be provided with a nonreverse mechanism in the motor to protect the line shaft and the motor from reverse rotation when the power is interrupted and the waterempties 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-FrictionLoss The column-friction chart (Figure 3) should be used as a design guide to determine the loss of head due to 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 to 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 or shaft, column, and discharge pipe used. Figure 4 represents estimated average losses based on

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AWWA E l 0 1 88

0783350 0 0 0 2 7 6 7 T VERTICAL TURBINE PUMPS

19

Capacity-gpm

~OTE:Friction loss

determined by laboratory tests on new pipe (C = 140).

)iagonals are labeled to show nominal diameters (in inches) of outer pipe column and inner shaft-enclosing tube. For the outer lipe columns, the calculations used in constructing the chart were based on inside diameters, which are close to the nominal izes for pipe up to and 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, 16 in. = 15 1/4-in. ID). For the inner olumns (shaft-enclosing tubes), 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.

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20

AWWA E101-88

Capacity"m3lh

10

20

40

60 EO 100

200

400

7 0 0 1 O00

2000

4000

10 o00

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 to 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.

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Diameter-mm

7

8

Diameter-in.

VOTE: The chart shows values for enclosed shaft with oil or 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.

Figure 5 Mechanical friction in line shafts.

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A W W A ELO1 8087 8 3 3 5000 0 2 7 7 2 22

T M

AWWA E101-88

Table 3 Line-Shaft Selection Chart for Type B Material*

Power Rating-hp

(hp X 0.746 = kW)

in.

(mm)

rpm

3/4

(19.05)

3500 2900 1760 1460

39.7 32.9 20.0 16.6

38.8 32.2 19.5 16.2

37.4 31.0 18.8 15.6

32.4 26.9 16.3 13.5

1

(25.40)

3500 2900 1760 1460

94.5 78.3 47.5 39.4

93.8 77.7 47.2 39.1

93.0 77.0 46.7 38.7

89.5 74.2 45.0 37.3

82.5 68.4 41.5 34.4

1 3/16

(30.16)

3500 2900 1760 1460

167.0 138.4 84.0 69.6

167.0 138.4 84.0 69.6

166.0 137.5 83.5 69.2

163.0 135.1 82.0 67.9

157.0 130.1 79.0 65.5

149.0 123.5 75.0 62.1

1 7/16

(36.51)

3500 2900 1760 1460 1160 960

296.0 245.3 149.0 123.5 98.3 81.4

294.0 243.6 146.0 121.0 97.6 80.8

289.0 239.5 145.0 120.1 96.0 79.5

283.0 234.5 142.0 117.7 94.0 77.8

264.0 218.7 133.0 110.2 87.6 72.5

1 1/2

(38.10)

3500 2900 1760 1460 1160 960

336.0 278.4 169.0 140.0 111.2 88.7 90.4 91.6 92.0

334.0 276.7 168.0 139.2 110.7

330.0 273.4 166.0 137.5 109.2

324.0 268.5 163.0 135.1 107.2

306.0 253.5 154.0 127.6 101.4 83.9

1 11/16

(42.86)

1760 1460 1160 960 860 71O

252.0 209.1 166.0 137.4 123.0 101.6

251.0 208.2 165.0 136.6 122.0 100.7

248.0 205.7 164.0 135.7 121.0 99.9

246.0 204.1 162.0 134.1 120.0 99.1

239.0 198.3 157.0 129.9 117.0 96.6

227.0 188.3 150.0 124.1 111.0 91.6

*Steel with a minimum elastic limit of 40,000 psi (276,000 kPa) anda minimum ultimate tensile strength of 67,000 psi (462,000Wal.

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AWWA ELOL 88

m

0783350 0002773 L VERTICAL TZTRBINE PUMPS

23

Table 3“continued PUP ThrUst”1000 Zb ( k m Shaft Diameter

Speed

1 2 3 5 157.5 10 (4.448) (8.896) (13.344) (22.24) (33.36) (44.48) (66.72) (88.96) (133.44)

30

20

in.

(mm)

rpm

1 15/16

(49.21)

1760 1460 1160 960 860 71O

393.0 326.0 259.0 214.3 192.0 158.5

392.0 325.2 258.0 213.5 192.0 158.5

390.0 323.5 257.0 212.7 191.0 157.7

382.0 316.9 252.0 208.6 187.0 154.4

373.0 309.4 246.0 203.6 182.0 150.3

345.0 286.2 228.0 188.7 169.0 139.5

2 3/16

(55.56)

1760 1460 1160 960 860 71O

578.0 479.5 382.0 316.1 283.0 233.6

577.0 478.7 381.0 315.3 282.0 232.8

576.0 477.8 380.0 314.5 281.0 232.0

570.0 472.8 376.0 311.2 279.0 230.3

562.0 466.2 371.0 307.0 275.0 227.0

538.0 446.3 355.0 293.8 263.0 217.1

2 7/16

(61.91)

1760 1460 1160 960 860 710

816.0 676.9 537.0 444.4 398.0 328.6

815.0 676.1 537.0 444.4 398.0 328.6

810.0 671.9 533.0 441.1 395.0 326.1

802.0 665.3 529.0 437.8 392.0 323.6

781.0 647.9 515.0 426.2 381.O 314.6

2 l1/16

(68.26)

1760 1460 1160 960 860 710

Power Rating-hp

(hp x 0.746 = kW)

1070.0 1062.0 1055.0 1035.0 887.6 881.0 875.2 858.6 703.0 700.0 696.0 682.0 581.8 579.3 576.0 564.4 520.0 518.0 515.0 505.0 429.3 427.7 425.2 416.9

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 the specific material used in accordance with Sec. A-4.2.3or Sec. A-4.3.3. A-5.5.1 Table 3 does not limit the maximum rotative speed of shafts, the maximum 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 to any steel having a minimum elastic limit of 40,000 psi (276,000 kPa) and a minimum ultimatetensile strength of 67,000 psi (462,000 Wa). A-5.5.3Horsepower ratings shown in Table 3 anccalculated in accordance with Sec. A-4.1.5 represent maximum loads and should not be increased by electricmotor service factors.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

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 purchaser’s 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 test of bowl assembly. If other tests are required, the purchaser shall describe them in detail. A-6.1.2The manufacturer shall notify the purchaser not less than five days prior to the date that the pump or pumps will be ready for inspection or witness test.

Sec. A-6.2 Running Test A-6.2.1Thepumpbowl assembly willbe operated fromzero capacity to the maximum capacity shown on the performance curve submitted with the manufacturer’s 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 to model or slow-speed tests described in Sec. A-6.9. A-6.2.2 At the conclusion of thetest,three copies of the anticipated fieldperformance curve shall be supplied to the purchaser, unless the purchaser requests test 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 to provide favorable suction conditions for pumpperformance. If the purchaser plans to use the pump under questionable well or sump conditions and wants the pump to 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 to 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,orifice 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 instrumentbeing used and are essentially the same as

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AWWA.ELOL 88 W 0783350 0002775 5 W VERTICAL TURBINE PUMPS

25

Water Head Manometer Mercury Head Manometer

Datum

-

........?.:(. 5.

,.:

Figure G Typical laboratory test arrangement-line-shaft

vertical turbine pumps.

duringthe calibration. Instrumentsthat 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 publication Fluid Meters-Their Theory and Application." A detailed description of the various meters and their application is given in Chapter B-2of that publication, the physical constants and meter coefficients are indicated in Section C, and the discharge coefficient tolerances of the various meters areindicated in Chapter C-7. The surface conditions, size, and length of the pipe precedihg the fluid-measuring device are as important as the calibration of the device itself. Thus, piping should be in close conformity with that used when the instrument was calibrated or in accordance with the recommendations by the manufacturerof the fluid-measuring device. Fluid manometers or 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 the request for bid.

*Fluid-Meters-Their Theory and Application. Rept. ASME Res. C o m . on 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.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

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 at right angles to 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 alternate method, the pressure tap for head measurement can also be located not less than 10 diameters downstream from the discharge elbowof the test pump. (The elbow to be furnished with the pump shall be used.) When the pump head is measured at this point, no deduction for elbow loss need be made in anticipating field performance. For head measurements of 36 ft (11 m) or less, only fluid manometers shall be used. For head measurements in excess of 36 ft (11 m), 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 to 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 the point of pressure 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 thepoint where the pressure tap is located.

Sec. A-6.7 Horsepower Input The power input to 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 induction motors with short-circuited secondary resistance may be employed for the determination of shaft input, provided the efficiencies or losses have been ascertained by an IEEE” testor 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 to measure power input to all motors.

Sec. A-6.8 Measurement of Speed The rotating speed of the pump shall be obtained by a hand counter, electronic computer, or a stroboscope counting slip. It should be noted that an accurate speed reading is important in determining power input when a dynamometer is used. Accuracy is less important when a calibrated motor is used.

*Institute of Electrical and Electronics Engineers, 345 East 47th St., New York, NY 10017.

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A W W A E L O 1 8¿!1 W 0783358 0002777 9 W VERTICAL TURBINE PUMPS

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 actual pump shall be tested in the manufacturer’s laboratory. A-6.9.2 If the horsepower exceeds 200 hp (150 kW), it shall be permissible for the manufacturer t o test only the number of stages of the unit that 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, compared with the number of stages used in thelaboratory 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 onmodel tests, the contract should specify model performance rather than inferred actual-unit performance. In theabsence of this provision, allowance forthe 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 run at a speed sufficient to develop a head per stage at least 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 singlestage model does not cavitate under specified field suction conditions when operated at a speed such that thevelocities willequal or exceed those of the actual unit. A-6.9.4 On bowl assemblies that have an OD exceeding 20 in. (500 mm) os require more than 200 hp (150 kW), it shall be permissible to test the actual bowl assembly 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 performance in the slow-speed test is translated into that atfull speed. The manufacturer must submit evidence that a single-stage bowl assembly or a single-stage model does not cavitate under specified field suction conditions when operated at a speed such that thevelocities willequal or exceed those of the actual unit. A-6.9.5 All large bowl assembly full speed tests or model tests should be conducted with identical submergence that will exist in the field, as shown on the request for bids, except as otherwise agreed on between the manufacturer and the 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 pressure defined in Sec. A-6.10.1, less the pump setting specified on the 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 instrument identification shall also be recorded.

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A W W A E L O 1 8087 8 3 3 5000 0 2 7 7 8 28

0 M

AWWA E101-88

A-6.11.2 All test results shallbe translated into performance at the anticipated speed of the driver at thedesign point by the following formulas: Q=Qt

(

H=Ht

(

P=Pt

(

" 1

nt

nt IL

nt

l3

Where: Q

=

t n

= =

H P

= =

pumpcapacity, in gallons perminute (cubic metresperhour) indicated test values anticipatedoperating speed, in revolutions perminute (revolutions per second) head, in feet (metres) power, in horsepower (kilowatts)

NOTE:gpm x 0.2271 = m3/h; rpm x 0.0167 = rps; ft x 0.3048 = m; hp x 0.746 = kW.

A-6.11.3 The bowl assembly input power P l , in horsepower, when measured by a vertical dynamometer, is found using the expression

Where:

K

=

dynamometer constant, 2d/33,000

Where:

F nt

L

=

= =

net force at the end of the lever arm, in pounds (Newtons) speed of the driver when the test reading is taken, in revolutions per minute (revolutions per second)

length of the lever arm, in feet (metres)

NOTE: ft x 0.3048 = m; lb x 4.448 = N; rpm

x 0.0167 = rps.

A-6.11.4 Theelectric-motorpower input,in kilowatt input to motor divided by 0.746.

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horsepower, is the corrected

1

A W W A ELO1 0783350 0002777 88

2 W VERTICAL TURBINE PUMPS

29

A-6.11.5 The bowl assembly input power P I , in horsepower, to a pump driven by an electric motor is

P1 =

kW 0.746

Eg

Where:

kW = Eg

=

corrected kilowatt input t o motor motor efficiencyfrom the calibration curve

A-6.11.6 The pump-bowl assembly efficiency E1 is

E1 =

Qhl 3960 x ( P I )

Where:

Q hl P1

=

= =

measured capacity, in gallons per minute bowl assembly head, including velocity head, in feet brake horsepower t o the pump bowl assembly, measured by dynamometer or calibrated motor

NOTE: gpmx 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

=

hc

=

he

=

bowl assembly head from test, in feet column loss, in feet, obtained from Figure 3 and based on complete pump setting 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 = Pl

+ PC + Pt.

(Eq 13)

Where:

P1

=

COPYRIGHT American Water Works Association Licensed by Information Handling Services

bowl assembly input power, in horsepower, calculated from test, as inSec. A-6.11.3 or Sec. A-6.11.5

30

AWWA E101-88

PC

=

Pt

=

NOTE: hp

line-shaft loss in power, in horsepower, obtained from Figure 5 and based on complete pump setting thrust-bearing loss, in horsepower X

0.746 = kW.

A-6.11.9 The pump efficiency Ep is found using the equation Ep =

&H 3960 x P

(Eq 14)

in which the pump total head H, in feet (ft x 0.3048 = m), is obtained from Sec. A6.11.7 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 Ep multiplied by the driver efficiency Eg. 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 to 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 to Hydraulic Institute" test standards, asapplicable.

*Hydraulic Institute, 712 LakewoodCenterNorth, 44107.

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14600 Detroit Ave., Cleveland, OH

AWWP, ELO1 B8 W 0783350 0002781 O

Part B-SUBMERSIBLEVERTICALTURBINEPUMPS

Part B of this standard provides minimum requirements for submersible vertical turbine pumps utilizing a T1/2-hp motor or larger. Purchasers who intend t o use the pumps for pumping liquids other than clear, cold water should modify the requirements, preferably after consultation with pump manufacturers, to 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 to 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 to provide energy for initiating or maintaining the movement of liquid. A pump consists of seven elements, defhed asfollows: B-2.2.1 The pump. bowl assembly is a single or multistage, centrifugal or 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 assembly t o the surface-plate connection. It supports the pump and driver in the well and also supports an electric cable that carries current from the surface to the motor lead connection.

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COPYRIGHT American Water Works Association Licensed by Information Handling Services

A W W A ELO1 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 application from the standpoints of corrosion resistance and mechanical performance. B-4.1.2 Design. The motor shall be of the squirrel-cage induction type, suitable for across-the-line starting 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 temperature rating of the insulation class used to wind the motor. B-4.1.4 Thrust bearing. A thrust bearing of ample capacity to carry the weight of all rotating parts plus the hydraulic thrust at maximum operating head shall be an integral part of the driver. For antifriction bearings, the bearing shall be of such capacity that the AFBMA" calculated rating life (Lid shall be no less than 8800 h. If the design and operating conditions are such that upthrust can occur, then proper provision shall be made to accommodate the upthrust. This shall be done by the supplier. It shall also have ample capacity to permit the pump to operate for short periods with the discharge valveclosed.Any operation of a submersible pump against a closed valve is not advised due to possible damage t o the motor. B-4.1.5 Foreign matter. Suitable precautions shall be taken to restrict sand, silt, or foreign material from entering the motor. B-4.1.6 Pump size. The maximum motor diameter and the minimum inside diameter of the well shall be in such relationship that under any operating condition the water velocity past the motor shall not exceed 12 fiYs (3.7 d s ) nor be~less than 0.5 ft/s (0.1 d s ) . For this purpose a minor irregularity in the motor shape, such as that caused by the cable connection, shall not be included in the motor-diameter measurement.

Sec. B-4.2 Submersible Cable

.

B-4.2.1 Conductors. The cable shall consist of three or more separate conductors, including a ground cable or a single-cable assembly with three or more conductors, including onefor a ground. Strandingshallmeet ASTM class designation standards"r1ass B on No. 10 and smaller cable and No. 1 through 4/0 cable; class C on No. 9 through No. 2 cable. Each conductor shall be insulated by synthetic rubber or plastic insulation suitable for continuous immersion in water. When three or

*Anti-Friction Bearing Manufacturers Association, 1101 Connecticut Ave. N.W., Suite 700, Washington, DG 20036. *Class B on No. 10 and smaller cable provides for at least 7 strands minimum; class C on No. 9 through No. 2 cable provides for at least 19 strands minimum; and class B on No. 1 through 4 0 cable provides for at least 19 strands minimum. -~ " .

COPYRIGHT American Water Works Association Licensed by Information Handling Services

A W W A ELO1 88 raDl U 7 8 3 3 5 0 000278Lt b 34

AWWA E101-88

r

Typical Assembly

Figure 7 Typical submersible-pump assembly (bowl assemblies).

COPYRIGHT American Water Works Association Licensed by Information Handling Services

VERTICAL TURBINE PUMPS

Well Seal Surface-Plafe Assembly*

Surface Plate with Vertical Flange connection

Surface Plate with Flanged Elbow

Ordinary Surface-Plate Assembly

Surface Plate with Integral Welding Elbow

Vel1 seal surface plates are for use where well sealing is required; a flange must be welded to the casing by a continuous ateflight weld or the plate must be grouted in place. Ordinary surface plates may be used where sanitary well seals are not quired.

Figure 8 Submersible-pump discharge styles and sufiace-plate assemblies.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

35

AWWA 36

E L O L A B R U783350 0002786 T m

AWWA E101-88

v)

m

COPYRIGHT American Water Works Association Licensed by Information Handling Services

c o m m m

A W W A E 1 0 1 88

= 0783350 0002787

L M

VERTICAL TCTRBINE PUMPS

i7 a .

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m

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6 B

ml

rl

rl

COPYRIGHT American Water Works Association Licensed by Information Handling Services

37

A W W A ELO1 8 8 W 0783350 0 0 0 2 7 8 8 3 38

AWWA E101-88

3

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COPYRIGHT American Water Works Association Licensed by Information Handling Services

al al

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A W W A E l 0 1 88 M 0783350 0002787 5 M VERTICAL TURBINE PUMPS

al

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COPYRIGHT American Water Works Association Licensed by Information Handling Services

39

A W W A ELO1 88 40

m

0783350 0 0 0 2 7 7 0 L

AWWA E101-88

W

2 cd

C

*

m

rl

COPYRIGHT American Water Works Association Licensed by Information Handling Services

r

m

m

l

d

A W W A E l O l 88

= 0783350

0002773 3 VERTICAL TURBINE PUMPS

41

more single conductors are used, each must be jacketed. When a cable with three or more conductors is used, it must be jacketed. The jacket material must be oil- and water-resistant synthetic rubber, metal, or other suitable mechanically protective material. The cable shall have a sufficient conductor area to meet the minimum requirement of the ICEA*codefor operation in air. (The connecting electrical cable from the starting equipment to the surface plate shall meet the National Electrical Code or local codes, whichever govern.) B-4.2.2 Supports. The cable shall be suitably supported from the column at several points adequate for the type of cable used with corrosion-resistant clamps. B-4.2.3 Fittings. AU cable fittings andterminalsshall be watertight at the pressure encountered in use. B-4.2.4 Lengths. For each 50 ft (15 m) of setting, 1 R (0.3 m) of extra cable shall be allowed to compensate for possible twist or sag of the cable during installation; 10 ft (3 m)shall beprovidedbeyond the surface plate, unless otherwise specified. B-4.2.5 Mechanical shielding. The electrical conductors shall be protected by a corrosion-resistant mechanical-type shield where they passthe pump bowls.

Sec. B-4.3 Surface Plate The surface plate (pump base) shall berigidenough to support the entire weight of the suspended parts when filled with water. The plate shall provide suitable openings for the power cable, well vent, and water-level indicator as required. The plate shall provide a support for the power cable as required by the electrical code. The plate shall also support the discharge connection furnished in a size adequate for the required flow rate and in apressure series consistent with the surface pressure to be delivered by the pump.

Sec. B-4.4 Strainer A strainer,if furnished, shall have a netinlet area equalto at least three times the impeller inlet area. The maximum unit opening shall not be more than 75 percent of the minimum opening of the waterpassage through the bowl or impeller.

Sec. B-4.5 Discharge Pipe The discharge pipe may be furnished in random lengths connected by threaded sleeve couplings. For settings up to 500 ft (150 ml, the minimum weight shall conform to the values shown in Table 2 (on page 17) and shall have ANSIB1.20.1 standard taperedpipe threads. For pumps with a total head inexcess of 500 ft (150 m), each application shall be checked t o determine that the strengths of the pipe and threaded joints are adequate. Thedischarge pipe will be secured so that it will not unscrew. The reaction t o the starting torque of the motor gives a force equal in magnitude but opposite in direction to the turning force that the motor delivers to the pump. A joint-tightening torque of 10 ft-lbhp(18.2 N.m/kW) occurs in submersible pumps. The size shall be such that velocities are not less than 4-5 ft/s (1.2-1.5 d s ) nor more than 12W s (3.7 d s ) .

*InsulatedCableEngineers Association, P.O. Box P,South (Formerly the Insulated Power Cable Engineers Association.)

COPYRIGHT American Water Works Association Licensed by Information Handling Services

Yarmouth, MA 02664.

.

42

AWWA E101-88

Sec. B-4.6 Pump Bowls Pump bowl castings shall be free of blowholes, sand holes, and other detrimental defects. The finished bowls shall be capable of withstanding a hydrostatic pressure equal to twice the head at rated capacity or I V 2 times the shut-off head, whichever is greater. The bowls may be equipped with replaceable seal rings on the suction side of enclosed impellers.

Sec. B-4.7 Impellers The impellers shall beof the open,semiopen,orenclosed type, statically balanced.They shall be fastened securely to the impeller shaft with keys, taper bushings, lock nuts, or set screws.

Sec. B-4.8 Pump Motor Coupling The pump motorcoupling shall beof a noncorrosive material and shall be capable of transmitting the total torque and total thrust of the unit in either direction.

Sec. B-5.1 Discharge Pipe Diameters and weights of standard discharge pipe sizes are given in Table 2 (page 17).

Sec. B-5.2 Discharge Friction Loss The discharge pipe friction loss chart (Figure 9) may be used t o determine the loss in head due to friction.

Sec. B-5.3 Discharge-Elbow Head Loss The discharge-elbow head-loss chart (Figure 10) may be used to determine the hydraulic losses in the discharge elbow. When extreme accuracy is imperative, actual loss measurements in the discharge elbow to be used-with the correct discharge pipe-should be specified on bid requested by purchaser.

Sec. B-6.1 Tests B-6.1.1Theprocedurefor 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 described below. Performance tests will be made onlywhenspecified in the purchaser's 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.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

VERTICAL TURBINE PUMPS

43

Capacity-m3lh

Capacity-gprn ~ O T E :Diagonals are labeled to show nominal diameters of discharge column pipe (in inches). The calculations used in construct. ng the chart were based on inside diameters, which are close to the nominal sizes (for example, 10 in. = 10.12 in. ID). :onversion factor: in. x 25.4 = mm.

Figure 9 Head-loss chart for standard pipe.

4. Shop inspection. 5 . Hydrostatic test of bowl assembly..

If other tests are required, the purchaser shall describe them in detail. B-6.1.2 The manufacturer shall notify the purchaser not less than five days prior t o the date that the pump or pumps will be ready for inspection or witness test. Sec. B-6.2 Running Test

B-6.2.1 The pump bowl assembly shall be operated from zero capacity to the maximum capacity shown on the performance curve submitted with the manufacturer’s bid. Readings shall be taken at a minimuin of five capacity points, including the shut-off head and one point within k 2 percent of the design capacity specified on the requestfor bid. B-6.2.2 At the conclusion of the test, three copies of the anticipated field performance curve shall be supplied to the purchaser, unless the purchaser requests test curves based on the actual test data without corrections for anticipated field performance.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

A W W A ELO1 8 8 44

O783350 0 0 0 2 7 7 4 9 W

AWWA E101-88

I .W

O 305

o 80

O 244

O 60

O 183

O 50

0.152

O 40

o 122

0 30

o o91 O061

7

v)

v) v)

v)

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O

x

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I

370

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r 006

O018

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2 04

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J

a,

a,

I

o O09 O006

(I 02

20

30

40 5 0 60

80 100

200

300 400

600 800 1 O00

2030

4

WO 6000

O 003 10000

Capacity-gpm

JOTE: Diagonals are labeled to show nominal diameters of discharge elbow pipe (in inches). The calculations used in constructi g the chart were based on inside diameters, which are close to the nominal sizes (for example, 10 in. = 10.12 in. ID). :onversion factor: in. x 25.4 = mm.

Figure 10 Head-loss chart for 90° elbow.

Sec. B-6.3 Typical Laboratory Test Arrangement Figure 11 shows a typical laboratory arrangement for the testing of a submersible vertical turbine pump. A test laboratory will normally be constructed to provide favorable suction conditions for pump performance. If the purchaser plans to use the pump under questionable well or sump conditions and wants the pump to 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 to required well or sump conditions, it shall be assumed that standard laboratory arrangements will be used.

Sec, B-6.4 Capacity Measurement The capacity of the pump shall be measured by means of a standard venturi tube, nozzle,orifice 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 instrument being used and are essentially the same as

COPYRIGHT American Water Works Association Licensed by Information Handling Services

A W W A ELO1 88 9 0783350 000279.5-0- 9 VERTTGAL TURBINE

pUMps 45

Water Head mBourdon rManometer Manometer VentUridl G a z eMercury Head MaForneter

1

Venturi Meter

Figure 1 1 Typical laboratory-test arrangement-submersible vertical turbine

pumps.

duringthe calibration. Instrumentsthat have not been calibrated should be geometrically similar t o properly calibrated models. A description of the application of fluid meters is contained in theASME publication Fluid Meters-Their Theory and Application.:': A detailed description of the various meters and theirapplication is given in Chapter B-2of that publication, the physical constants and meter coefficients are indicated in Section C, and the discharge coefficient tolerances of the various meters are indicated in Chapter C-7. The surface conditions, size, and length of the pipe preceding the fluid-measuring device are as important as the calibration of the device itself. Thus, piping should be in close conformity with thatused when the instrument was calibrated or in accordance with the recommendations by the manufacturer of the fluid-measuring device. Fluid manometers or other instruments of equal accuracy should be used for measuring the pressuredifferential across the meter.

*Fluid Meters-Their Theory and Application. Rept. ASME Res. C o m . on Fluid Meters. American Society of Mechanical Engineers, New York (5th ed.,1959).

COPYRIGHT American Water Works Association Licensed by Information Handling Services

A W W A E L O 1 A8 46

= 0783350 0 0 0 2 7 9 6

2

AWWA E101-88

Sec. B-6.5 Head Measurement All pump bowl assembly tests shall be made in open sumps, unless otherwise stated in the request for bid. The pressure tap for head measurement shall be located in the discharge pipe not less than 2 ft (0.6 m) above the pump bowl assembly. The pressure tap opening shall be at right angles to the pipe, free from burrs, flush with the surface of the discharge pipe, and with the diameter of 1/81/4 in. (3.18-6.35 mm). As an alternate method, the pressure tap for head measurement can also be located not less than 10 diameters downstream from the discharge elbowof the test pump. (The elbow to be furnished with the pump shall be used.) When the pump head is measured at this point, no deduction for elbow loss need be made in anticipating field performance. For head measurements of 36 ft (11 m) or less, only fluid manometers shall be used. For head measurements in excess of 36 f t (11 m), 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. B-6.6 Velocity Head The average velocity in the pump column used to determine the velocity head shall be calculated from dimensions obtained by actual internal measurement of the pipe diameter at thepoint of pressure 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 thepoint where the pressure tap islocated.

Sec. B-6.7 Power Input to Pump Motor The actual job motor shall be used, and the overall submersible-pump efficiency shall be calculated from the measured power input. Calibrated laboratory-type electric meters and transformers shall be used to measure the power input to all motors.

Sec. B-6.8 Large-Pump Tests Sec. A-6.9 of this standardshall also apply to submersible pumps.

Sec. B-6.9 Hydrostatic Tests A hydrostatic test on the pump bowl castings shall be made at 11/2 times the shut-off head developed by the pump bowl assembly or at twice the rated head, whichever is greater.

Sec. B-6.10 Recording and Computationof Test Results B-6.10.1 All instrument test readings, as well as corrected readings, shall be recorded on the test sheet. Complete data concerning the pump, driver, and instrument identification shall also be recorded.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

VERTICAL TURBINE PUMPS

47

B-6.10.2 All test results shall be translated into performance at the anticipated speed of the driver at thedesign point, by the following formulas:

Q=Qt

(

H=Ht

(

P=Pt

(

" >

nt

nt

> 2

nt

l3

Where:

Q t n

=

H P

= =

=

=

pump capacity, in gallons per minute (cubic metres per hour) indicated test values anticipated operating speed, in revolutions per minute (revolutions per second) head, in feet (metres) power, in horsepower (kilowatts)

NOTE:gpm x 0.2271 = m3/h; rpm x 0.0167 = rps; ft x 0.3048 = m; hp x 0.746 =

kW. B-6.10.3 The motor power input, in horsepower, is the corrected kilowatt input to motor divided by0.746. B-6.10.4 The bowl assembly input horsepower PI to a pump driven by an electric motor is

P1

=

0.746

Eg

Where:

kW =

Eg =

corrected kilowatt input to motor motor efficiency fromthe calibration curve

B-6.10.5 The pump bowl assembly efficiencyEI is

E1

COPYRIGHT American Water Works Association Licensed by Information Handling Services

=

Qhl 3960 x Pi

(Eq 19)

A W W A ELO1 8 8 48

0783350 0 0 0 2 7 7 8 b W

AWWA E101-88

4 90 I

2.00

T I

/ 1.00 0.90

~

-~

0.80

~

0.70

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0.60 0.50

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245 220

1.96 1 71 147

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t

0.05 n .” M 20

10

30

40

50

60

200

70 80 90 100

o

12

I1 O10 300 400

Current-amp JOTE: Diagonals are labeled to show sizes (American Wire Gage of cable conductor wire, and are based on a copper temperaJre of 6OoC and an ambient air temperature of 3OoC. Current should not exceed the plotted maximum on any given line. Maxinum values must be reduced by a factorof 0.82 for an air temperature of 4OoC.

Figure 12 Power-loss chart for three-conductor copper cable. Where Q hl

P1

= = =

measured capacity, in gallons per minute bowl assembly head, including velocity head,in feet brake horsepower to the pump bowl assembly

NOTE:gpm x 0.2271 = m3/h; ft x 0.3048 = m; hp x 0.746 = kW. B-6.10.6 The pump total head H , in feet, is found using the equation

H = hl

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- hc -

he

~~

A W W A E L O 1 88 0783350 0002777

B VERTICAL TURBINE PUMPS

49

Where: hl hc

= =

he

=

bowl assembly head from test,in feet column loss, in feet, obtained from Figure 9 and based on complete pump setting discharge-elbow loss, in feet, from Figure 10 or actual test

NOTE:fi x 0.3048 = m. B-6.10.7 The pump input power P equals the bowl assembly input power PI plus the cable loss Pw (obtained from Figure 121, from the surface plate to the motor.

B-6.10.8 The overall efficiency E is found using the equation

E =

&H 3960 x P

in which the pump total head H , in feet (ft x 0.3048 = m), is obtained from Sec. B6.10.6 and the power input P , in horsepower (hp x 0.746 = kW), is obtained from Sec. B-6.10.7. B-6.10.9 The complete pump total head, overall pumpefficiency, and pump input power should be plotted as ordinates on the same sheet against the capacity as abscissa to show the anticipated field performance of the complete pumps.

Sec. B-6.11 Other Tests

For more complete tests or for tests involving fluids other than water refer t o Power Test Code for Centrifugal and Rotary Pumps" as applicable.

*Available from American Society of Mechanical Engineers, 345 E. 47th St.,New York, NY 1O017.

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APPENDIX A Field Testing of Vertical Turbine Pumps This appendixis for information only and isnot a partof AWWA E101.

Purpose of Field Tests A field test gives an indication of the performance of a pump when it is operating under actual field conditions. Such a test indicates the operation of the pump bowl assembly, the friction loss in the column pipe and discharge elbow, the bearing losses in the line-shaft assembly or the cable loss on a submersible pump, the well or system characteristics, the air content or sand content of the water, the vibration and noise levels, and the operation of the driver and control equipment. Although all of these items are important, they are normally judged on a qualitative basis as compared to what is considered to be good engineering practice, unless specific requirements are indicated in the individual specifications. The purpose of this appendix is to establish a guide for the quantitative evaluation of the hydraulic performance of the complete pumping unit as installed in the field. It is desirable to make field tests on new or reconditioned pumps to serve as a standard of comparison for future tests. Thus, pump wear and changing operating conditions may be indicated. Periodic tests should be made by the same procedure, and an accurate record kept to give a complete and comparable history. Field tests are sometimes used as acceptance tests. When this is done, the accuracy of the test obtainable under field conditions with the specific test equipment employed should be taken into account. Data t o help determine the best possible accuracy obtainable with various instruments are included in AWWA E101, Standard for Vertical Turbine Pumps-Line Shaft and Submersible Types. Under most conditions, it is recommended that acceptance of the pump should be based on tests made in a laboratory where accurate instruments used under controlled conditions permit precise measurements. It is also recommended that field tests be used as an overall indication of pump performance and as a guide to show when the pump or well requires service.

Accuracy of Field Testing The accuracy with which a field test can be made depends on the instruments used in the test, the proper installation of the instruments, and the skill of the test engineers. If accurate field tests are required, it is necessary t o design the complete pump installation with this in mind and to provide for the use of the most accurate calibrated instruments. It should be recognized that environmental conditions in a well or the design of a sump can significantly affect field performance and also affect the apparent results of field tests. Table A.l gives an indication of the best possible accuracy that can be expected with the various instruments that may be used for a field test. The values given assume that each instrument is properly installed, that it is the correct size for the values to be measured, and that it is used by experienced engineers. A method of es-

50

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A W W A ELO1 8 8

0783350 00028OL 2 W VERTICAL TURBINE PUMPS

51

Table A. 1 Limits of Accuracy of Pump-Test Measuring Devices in Field Use

Quantity to be Measured Capacity

meter tube

weight-tank

or

Type of Measuring Device Venturi Nozzle Pitot Orifice Disc Piston Volume Propeller meter Magnetic meter

Calibrated Limitof Accuracy percent f 314

fl f 1 112 f 1 114 f2 k 114 L-1 *4

f2

Electric sounding line

Head

Air line Liquid manometer (3-5-in. deflections) Liquid manometer (over 5-in. deflections) Bourdon gauge-5-in. min. dial, 114112 full scale 112-314 full scale over 314 scale Power Input

Watt-hour meter andstopwatch Portable recording watt meter Test typeprecision watt meter '/&/2 scale 1/e3/4 scale over 314 scale Clamp-on ammeter

Speed

Revolution counter and stopwatch Hand-held tachometer Stroboscope Auto. counter and stopwatch

Voltage

Test m e t e r ~ 1 4 ~ 1scale 2 Test meter-%44 scale Test meter-314-full scale Rectifier voltmeter

+1 f 3/4

+ 112 +5

timating the probable combined accuracy that will be obtained with the instruments selected is illustratedin the following examples: Example 1 . Pump conditions: head, 500 ft (150 m); setting, 450 f t (135 m). Instrumentation is shown in the charton page 52. First, the head accuracy is weighted. Weighted accuracy of the electric sounding line is 450/500 x 114 = 0.225 percent; weighted accuracy of the bourdon gauge is 50/500 x V 2 = 0.050 percent; and the sum, or weighted-average head accuracy, is 0.275 percent, The combined accuracy of the efficiency & is the square root of the quantity of the square of the weighted-average head accuracy plus the square of the

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AWWA E L O 1 88 52

= 0783350 0 0 0 2 8 0 2

4

AWWA E101-88

venturi-meter accuracy plus the squareof the watt-meter accuracy. Pump speed and voltage are not necessary in determining efficiency, so the values for the tachometer and thevoltage meter are not included under theradical. Field-Test Report Form Line Number* 3 Bourdon gauge,4 9 14 19 11

Accuracy? percent

Instrument Electric sounding line 5-in. (127-mm) dial, 314 scale Venturi Watt over 314 scale Hand-held tachometer Voltage meter, 314 full scale

meter meter,

f l/4 f 3/4 f 3/4 f

114

rf: 1 114

f 112

*From Figure A.5. $From Table A.l.

Ac =

4

0.2752

+

0.752 + O.2Ei2

= f 0.837 percent

(Eq A.1)

Example 2. Pump conditions: head, 500 f t (150 m); setting, 450 ft (135 ml. Instrumentation is shown in the chartbelow. Number*

Field-Test Report Form Line 3

4 9 14 19 11

tube

Accuracyt percent

Instrument Air line Bourdon gauge, 5-in. (127-mm) dial, 112 scale Pitot stopwatch Watt-hour and meter Stroboscope Rectifier voltmeter

f

112

f1 1 112 f 1 112 f 1 112 f 5

*

*From Figure A.5. -?From TableA.l.

The head accuracy is weighted in the same way as in Example 1.

Air line .......................................

450 ft (135 m) 500 f t (150 m)

x V2 percent = 0.45 percent

Bourdon gauge ..........................

50 ft (15 m) 500 ft (150 m>

x 1 percent = 0.10 percent

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A W W A ELO1 8 8

= 0783350

0002803 b W VERTICAL TURBINE PUMPS

Weighted-average head accuracy ...................................

53

0.55 percent

The combined accuracy of the efficiency Ac is the squareroot of the quantityof the square of the weighted-average head accuracy plus the square of the pitot-tube accuracy plus the squareof the watt-hour meter accuracy.

Ac =

-

.\I O.5Ei2 + 1.Fi2+ 1.Ei2 4.8

Example 3. Pump conditions: head, 500 ft (150 m); setting, 20 ft (6 ml. Instrumentation is shown in the chartbelow. Field-Test Report Form Line Number" 3 4 9 14 19 11

meter

Accuracyf percent

Instrument

Air line Bourdon gauge, 5-in. (127-mm) dial, full scale Venturi meter Watt over, 314 scale stopwatch Automatic and counter scale Voltage full test meter,

k 112

c 314 f 314 f 114 f 112 f 112

*From Figure A.5. tFrom Table AS.

Weighted head accuracy is

Air line .......................................

20 ft (6 m) 500 ft (150 m) x 112 percent = 0.02 percent

Bourdon gauge ..........................

480 ft (144 m) 500 ft (150 m) x 112 percent = 0.48 percent

Weighted-average head accuracy ...................................

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0.50 percent

54

AWWA E101-88

The combined accuracyof the efficiency is

Ac =

4

0.52

+

0.752 + 0.252

= f 0.93 percent

(Eq A.3)

Theapproved and recommended procedure forconductingpumpacceptance tests is outlined in Sec. A-6 and Sec. B-6 of this standard. It will be apparent that if the accuracy of all instrumentation is not taken into account, the final result will possibly appear more accurate than it actually is. Individual errors in reading the instruments are not accounted for, so the final combined accuracy may be consideredan optimistic figure at best.

Definitions and Symbols Rate of flow (Q): Flow expressed in gallons per minute (cubic metres per hour). Datum: The elevation of that surface from which the weight of the pump is supported. This is normally the elevation of the underside of the discharge head or head base plate. Headabove datum (ha): The head measured above the datum, expressed in feet (metres) of liquid, plus the velocity head at thepoint of measurement. Velocity head (hu): The kinetic energy per unit weight of the liquid at the point of measurement, expressed in feet (metres) of liquid. Using the average velocity in feet per second (metres per second) at the point of measurement, it is calculated from the following expression:

Where:

v g

= =

velocity, in feet per second (metres per second) 32.17 ft/s2 (9.81 m/s2)

Head below datum (hb): The vertical distance, in feet (metres), from the datum to the pumping level. Pump total head (H): The sum of the heads above and below datum (ha+ hb). Pump speed of rotation (n): This is expressed in revolutions per minute (rpm) or revolutions per second (rps).The speed of submersible motors cannot be measured conveniently in field testing. Pump output, inhorsepower (hp): Calculated from the following expression:

hp =

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QH x specifìc gravity of liquid pumped 3960

(Eq A.5)

T

AWWA E l 0 1 88 0783350 O002805

VERTICAL TURBINE PUMPS

55

Where:

Q H

rate of flow, in gallons per minute pump total head, in feet

= =

Driver power input: The power input to the driver, expressed in horsepower. In a line-shaft vertical turbine pump powered by an electric motor, driver power input is equivalent to kilowatt input measured at the motor conduit box divided by 0.746. In a submersible vertical turbine pump, it is equivalent to kilowatt input measured at theconduit box on the discharge head divided by 0.746. No satisfactory evaluation of this term for engine-driven pumps is available. Driver eficiency (Ed):The ratio of the driver output to the driver input, expressed in percent. Overall eficiency (E): The ratio of pump output, in horsepower, to motor power input.

Approved Instrumentation Figures A . l , A.2, and A.3 show the placement of instruments and the dimensions for three types of pump installation. Figure A.4 shows piping requirements for orifices, flow nozzles, and venturi tubes. Pitot-statictube. These instruments, available in several forms, correlate ~~~~

Kilowatt-Hour Meter or Test Meter

I

Minimum Minimum Dimension -yD/mension M/inimum 10 Diameters Manometer Discharge Gauge (4)

-I iI

Datum to L of /Discharge Gauge

L Datum Line Y

Head Below Datum, Static Level (1)

\

Line &Datum

F

Discharge Pipe Capacity ID, h,, Calculated Orifice, Venturi, at Gauge Tap (6)

Measuring Device, Pitot or Tube

Drawdown (2)

Head Below Datum,’ Pumping (3)

1.

I

JOTE: Numbers in parentheses refer to item numbers in report form (Figure A.5). Minimum dimensions are the lengths of straight ipe required in Figure A.4 for the particular type of capacity-measuring device used.

Figure A. 1 Field-test diagram for line-shaft vertical turbine deep-well pump.

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56

AWWA E101-88

NOTE: Numbersin parentheses refer to item numbers in report form (Figure A.5). Minimum dimensions are the lengths of straight pipe required in Figure A.4 for the particular type of capacity-measuring device used.

Figure A.2 Field-test diagram for submersible pump.

Kllowatt-Hour Meter or Test Meter

= suction gauge reading converted to feet of water and corrected to datum. plus V 2 / 2 g at gauge tap

h,

NOTE: Numbersin parentheses refer to item numbers in report form (Figure A.5). Minimum dimensions are the lengths of straight pipe required in Figure A.4 for the particular type of capacity-measuring device used.

Figure A.3 Field-test diagram for vertical turbine pump for booster service.

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A W W A ELO1 88

m 0783350 0002807 3 m . VERTICAL TCTRBINE PUMPS

,CFIIFLCEOR FLOW NOZZLE

O 0.100.200.300.400.500.600.70 0.800,

Diameter Ratio, ß

Diameter Ratio, ß (B) For orifices and flow nozzles all fittings in same plane

(A) For orifices and flow nozzles

all fittings in same plane ORIFICE OR FLOW NOZZLE,

1

ORIFICE OR FLOW NOZZLE

ELLS.TUBE TURNS, OR LONG RADIUS BENDS

ORIFICE OR FLOW NOZZLE,

Diameter Ratio, ß (C) For orifices and flow nozzles fittings in different planes

Diameter Ratio, ß (D) For orifices and flow nozzles fittings in different planes

IOTE:All control valves must be installed on outlet side of primary element.

Figure A.4 Piping requirements for orifices, flow nozzles, and venturi tubes.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

50

40

57

0783350 0002808 5 M

A W W A ELO1 8 8 58

AWWA E101-88

ORIFICE OR FLOW NOZZLEi

O W

a a

2 DIAM. LONG

c

W

a_

10 I

20

I?

; 1

a c

cl

Lo

(L

a

o w

10

W

lu c ul

5

o O

I O 10 0.20 030 O 40 0.50 0.60 0.70 0.800.90

o 0.10 0 . 2 0 0 3 0 0 . 4 0 0 . 5 o a 5 o Diameter Ratio, ß

O.~OO.~OO.QO

(F) For orifices and flow nozzles in atmospheric intake

with reducers and expanders

,ORIFICE

f0

O

L

Diameter Ratio, ß (E) For orifices and flow nozzles

G (L

z

i

6

OR

4

’ FLOW NOZZLE

2

O

“A-54 T

f

5TRAIGHTEN:NG VANE 2 DIAM LONG

3

26 24

22 20;

W

1 8L

30 %

a

16:

c

I4

I

U 20

10

E m

8 5

a

4;

: 6

W

2 0

t-

10

3

12:

O 10

g 5

8

O

6 4

2

O 80

O O

0.10 0 . 2 0 0 3 0 0 . 4 0 0 . 5 0 0 . 6 0 0 3 0 0 8 0 0 . 9 0

Diameter Ratio, ß ( G ) Valves

Diameter Ratio, ß (H) For venturi tubes

IOT TE: All control valves must be installed on outlet side of primary element. In diagram H, the distances shown are double those

it which there seemed to be no effect. V I diagrams in Figure A.4, except diagram H, abstracted from Supplement on lnsfruments andApparatus, Part 5, Chap. 4, Flow deasurement (PTC 195; 4-1959), Power Test Codes Comm., ASME, New York, N.Y.

Figure A.4 Piping requirements for orifices, flow nozzles, and venturi tubes (continued).

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A W W A ELO1 8 8

m

0783350 0 0 0 2 8 0 9 7

m

VERTICAL TURBINE PUMPS

59

velocity head with rate of flow. Velocity-headdistribution in pipe flow is nonuniform, and for acceptable accuracy, a multiple-point traverse of the pipe cross section is mandatory. Pitot-static tube designs using a series of impact holes, each transmitting different velocity pressures to a common cavity within the tube, produce internal circulation and cannot be presumed t o measure average velocity head, unless the velocity profile in thepipe flow under test agrees exactly with that prevailing in the pipe in which the instrument was calibrated-an unusual circumstance. Consequently, these devices are not deemed acceptable. Complete details on construction, formulas, and useof acceptable types have been published." Thin-platesquare-edgedorifice. The orifice plate correlates statichead difference, measured upstream and downstream, with rate offlow. Data on dimensions, limitations, installation effects, and formulas have been published.* Venturis and flow nozzles. These devices are based on the same principle as the orifice plate, but introduce somewhat less head loss in a flow system." Flow measurement by volume or weight. The accuracy of volumetric measurement depends on the accuracy of tank dimensional measurements and differences in liquid level. The derivation of rate of flow, in turn, depends on the accuracy of time measurement of the period of flow. It is recommended that the minimum change in liquid level during any test run not be less than 2 f t (0.6 m). The duration of any test runshall not be less than 1 min, when the tank is filled from an open discharge pipe. A submerged entrance into the tank will cause an increase in the system head as the tank fills and will result in a nonlinear change in rate of flow. Correlation of rate of flow with weight is seldom feasible, except for extremely small flow. Evaluation of various methods of flow measurement. It is impossible to extend flow measurement beyond that corresponding t o the system head which, of course, equals the pump total head, unless the head above datum can be lowered for the test. Moreoften than not, this is not feasible, so the only portion of the pump characteristic that can be measured in a field test is the region of rates of flow lower than the design rate. It is also possible that thedesign rate cannot be reached if the method of flow measurement introduces friction head loss, thereby raising the system head. Substantial head losses are, indeed, incurred by introducing orifice plates and flow nozzles into the system. In some cases this may reduce their usefulness. The friction head loss introduced by insertion of a Pitot-static tube, on the other hand, can generally be neglected. Venturis also introduce very low losses, but because of their weight and length they are somewhat more expensive to employ in field tests (unless they are a permanent partof the installation). Head below datum hb. This distance can be measured by steel tape, electric sounder, or the air-line gauge method. The elevation of the pumping water level is determined electrically by measuring the length below datum of waterproof insulated wire terminating in a shielded electrode that completes the circuit through a magneto or dry cell to an indicating lamp, bell, or meter on touching the water's surface. The elevation of the pumping water level can be determined with the air-line gauge method by subtracting the calibrated bourdon-tube gauge reading (converted

*Fluid Meters-Their Theory and Application. Rept. ASME Res. Comm. on Fluid Meters. American Society of Mechanical Engineers, New York (5th ed., 1959).

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A W W A E L O 1 88 0783350 0002810 3 60

W

AQWA E101-88

to feet of liquid) from the known length of airtight tubing (open at the bottom) that has been pumped full of air to the maximum gauge reading that can be attained. The air-line gauge length, of course, must exceed the head below datum. In the airline gauge method, the gauge accuracy tolerance must be included (dependent on gauge quality andthe portion of the gauge range in use), unless the gauge is calibrated before and after the test. Head above datum ha. This quantity can be measured by means of a calibrated bourdon-tube gauge (reading converted to feet of liquid) plus the distance from the datum to the centerline of the gauge plus velocity head. When the head above datum is quite low, it may be measured with manometers, using mercury or the liquid being pumped as a manometer fluid. The choiceof manometer fluid should produce manometer deflections of at least6 in. (150 mm). Power measurement. Although not impossible, it is generally consideredimpractical to attempt to measure pump power input by means of a transmission dynamometer in field tests. The most frequently encountered alternative is that of measuring driver power input, which is then multiplied by the driver efficiency. The derived pump power input obtained by this method is subject to the accuracy tolerance on the driver efficiency. Since the only pump driver on which power input measurements of the requisite degree of accuracy can be made is the directdrive electric motor, this standard deals with the measurement of electricpower only. Watt-hour meters. These devices measure total energy, but maybeusedfor measuring power by introducing the time factor in thefollowing formula: driver power input =

4.826 K M R t

(Eq A.5)

Where:

K M

= =

R t

= =

disc constant, representing watt-hours perrevolution product of current and potential transformer ratios (if not used, omit from formula) total revolutions of watt-hour meter disc time for total revolutions of disc, in seconds

The duration of this measurement shall not be less than 1 min. Commercial watt-hour meter power measurements are expected to be within f l V 2 percent, unless specifically calibrated and used with a calibration chart. In this case the stated accuracy of the calibration shall prevail. Portable wattmeters. Used with or without portable current and potential transformer, portable watt meters are available in varying degrees of precision. They may be used with the manufacturer’s statement of accuracy tolerance if they are in good condition. Clamp-on electrical measuring devices. Except for rough checks on motor loading, these devices are deemed not acceptable for pump field tests. Pump-speedmeasurement. Therevolutioncounter and stopwatchprovide a simple and direct method of pump-speed measurement. They are to be preferred for field tests over more elaborate devices that read directly in revolutions per minute or revolutions per second. The expected accuracy tolerance for measurements based on a duration may be improved by extending the duration of the reading.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

VERTICAL TURBINE PUMPS

a

I

~

61

Test Procedure Preliminary agreement. The contractual obligations of the several parties involved should be clarified to the point of mutual agreement before the start of testing. The following salient points in hydraulic performance are among those that may be considered desirable: 1. Rate of flow with specified tolerance. 2. Pump total head with specified tolerance. 3. Driver power input with specified tolerance. 4. Pump speed with specified tolerance. 5. Overall efficiency with specified tolerance. 6. Stipulation of hydraulic performance tolerance on field testsmusttake strict account of the accuracy limitations inherent in field testing. Choice of instrumentation and installation effects shall be considered to avoid specification of unrealistic tolerances. The following points in mechanical performance are also desirable: 1. Acceptable vibration limits specifying point of measurement and maximum total indicator reading in mils (Pm). 2. Noise-level limits above specified ambient noise level, also specifying location at which noise level is t o be measured. Instrumentation. Choice, installation location,accuracy tolerances, and requirements for calibration curves shall be mutually decided on. Time limits. The effect of wear caused by abrasive material in the liquid being pumped makes it mandatory that field tests, if conducted for the purpose of acceptance, be concluded as soon as possible after installation. This effect varies within wide limits, so as much preliminary information as it is possible to obtain shall be made available to all contracting parties for the purpose of agreement on the time of test, or any allowances that shall be made for undue wearbefore the testis run. Inspection and preliminary operation. All contracting parties shall make as complete an inspection as possible of the installation to determine compliance with installation requirements and correct connection of all instrumentation. On satisfactory completion of this requirement, the pump shall be started. The pump, as well as the instrumentation, should be checked immediately for any evidence of malfunction. An immediate check of pumping water level shall be made, followed periodically by additional checks until the level has stabilized t o the satisfaction of all parties. Any evidence of cascading within the well or the presence of gas or abrasive material shall also be collected a t this time. A preliminary check of all test values can then be made for stability of reading, and a h a 1 check can be made on any possible malfunction. Recording. The recording of test data may take any convenient form and shall include make, type, size, and serial number of pump and driver; date of test; duration of run; description of instrumentation used; instrument constants or multipliers; other basic physical constants or formulas used that arenot specifically listed in this code; and liquid temperature at pump discharge and pump submergence, as well as the instrument readings. Additional data or remarks may also be included by mutual agreement. Copies of test data and accompanying instrument calibration curves shall be made available to all contracting parties. If several test runs are made at different rates of flow, a performance curve can be drawn and it shall become a part of the recorded data. An example of a satisfactory field test report form is shown in Figure A.5.

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A W W A ELO1 88 M 0783350 0002812 7

62

AWWA E101-88

Pump Field-Test Report Test Owner: Name Address

n

Pump: Serial No.

Make

Serial No.

Motor: Make Rated hp:

subm

rPm vhs

vss

PowerSupply:NominalVoltage Column: Pipe Size

Frequency

Size Pipe Discharge Size Shaft

or Length

Cable Conducted

Test

Serial

Pump

Test Instruments Head Below Datum Measured With Length Air Line (if used) Discharge Pressure: Size

Gauge

Make

Date Calibration:Gauge

cific

Fluid

by

No.

Chart

Manometer

Measured Pipe Inside Diameter at Pressure Tap Type Capacity-Measuring Device Used Size

Make

Serial No. Date

Calibration: ft Downstream From

(Valve, Elbow, or Other Fixture)

ft Upstream From

(Valve, Elbow, or Other Fixture)

Measured Diameter of Pipe at Instrument PoorCondition Good Excellent Upstream: of Pipe Type and Make of Power-Measuring Device Used No. Constant DiscWatt-Hour Meter

plier

Meter

No.

Watt

Ratio Transformers Current No.

Ratio Transformers Potential

No.

Calibration Chart of Meter by

Date

pe

Voltmeter:

e

Ammeter: Speed-Measuring Device

Figure A.5 Field-testreport form.

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A W W A E 1 0 1 8 8 W 0783350 0002813 7

”

VERTICAL TURBINE PUMPS

63

Expected Accuracyof Field Test Measurement

InstrumentAccuracy

Accuracy

Squared

-

Head above datum Head below datum Weighted-average head accuracy* Capacity Power

squared

-

.I

Sum of accuracy Combined accuracy

*Average is weighfed according to-the proportion of head above datum and head below datum to total head: (accuracy hb) x hb / H + (accuracy ha) x ha / H = weighted-average head accuracy.

Test Readings and Calculations All readings except No. 1 are taken when pumping

No. 1 2 3 4 5 6 7 8

9 10

11

12 13 14 15 16 17 18 19 20 21 22 23 24

Symbol

3

2

hb

Head below datum when not pumping Drawdown Head below datum Datum to centerline discharge gauge Pressure head reading

hv ha H

Pressure head above datum Velocity head in discharge pipe’ Head above datum* = (6) + (7) Total head* = (3) + (8) Capacity

Q

Current Line A Currenf Line B Current Line C Voltage Phase AB Voltage Phase BC Voltage Phase AC Revolutions of watt-hour meter disc (constant) Time Watt meter reading Electrical input* from (13 & 14) or (15) Horsepower input* = (1 6)/0.746 Revolutions of counter Time Pump speed = (18)x 60/(19) Pump output = (9) x (10) x sp gr/3960 Overall efficiency* = (21) x (17) Motor efficiency* (source) Pump field efficiency* = (22)/(23) . . . .

Units

1

ft (ml ft (m)

ft (m) ft ft or psi (m or kg/cm2) ft (ml ft (ml ft (m) ft (m) readings gpm (m3/h) amp amp amp V V V

sec kW hP

sec rpm hPt

percent percent percent

*Calculated. tResults will be in horsepower only if head measurements are in feet of liquid (hp x 0.746 = kW).

Figure A.5 (continued)

COPYRIGHT American Water Works Association Licensed by Information Handling Services

~~

A W W A ELO1 8 8 64

0783350 0 0 0 2 8 2 4 O

AWWA E101-88

Test observations. Since at least two persons will generally be present during a field acceptance test, the duties of making test observations may be distributed among those present. It may be preferable, however, if the instrument locations permit, to record each reading as a matter of mutual agreement. The practice of making simultaneous andinstantaneous readings of allinstrumentsmust be avoided. For example, the transient response of a bourdon-tube gauge is much faster than that of a mercury manometer. The recommended procedure is to make a continuous observation of at least 1 min of all instrumentation showing rate (or instantaneous values). During the prescribed observation period, if possible, all totaling instruments are read against time to determine rate. With some experience, it is possible to observe rate (instantaneous reading) instruments, mentally rejecting random fluctuations, and selecting the value that represents that prevailing most of the time during the observation period. It should be mentioned that the use of linear scales for nonlinear values (inch scales on differential manometers recording velocity head pressure from a pitotstatic tube,for example) may cause error in the process of obtaining a time-weighted average, if the fluctuation is appreciable. Not withstanding any skill that may be obtained with experience, it must be recognized that a considerable observational error can still exist. If possible, readings should be repeated and different observers should be employed to ensure complete agreement among all parties. It is difficult to evaluate the effect of fluctuating readings because of the highly variable damping that may be present with some types of instrumentation. It is not recommended that any devices be used t o increase damping of instrument readings, as it is occasionally possible for some of these methods to superimpose a rectifying effect or asymmetrical response on theinstrumentreading when subjected to dynamic fluctuations. It is desirable that the contracting parties agree in advance of the test on minimum (or maximum) scale readings of instruments and on the magnitude of fluctuation that may be acceptable, although fluctuations in readings occasionally reflect system response and cannot be readily controlled. Adjustment of field-testresults. Occasionally the pump-driver speeds will deviate slightly from the nominal value on which the pump performance guarantee is based. In such cases, the application of the following hydraulic affinity relationships should be made to adjust the test values to the design operating speed:

" >

Q = Q t (

nt

H=Ht(

nt

P=Pt(

nt

l2 l3

Where:

Q t

= =

pump capacity, in gallons per minute (cubic metres per hour) indicated test values

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A W W A El03 88 W 0783350 0002835 2 W VERTICAL "URBINE PUMPS

n

=

H P

= =

65

anticipated operating speed, in revolutions per minute (revolutions per second) head, in feet (metres) power, in horsepower (kilowatts)

Evaluation of accuracy tolerances. Observation errors do not necessarily follow the law of probability. If agreement on instrument readings cannot be reached before recording, the arithmeticaverage shall be used. Instrumentation accuracy tolerances for individual measurements are given in Table A . l . The value of the overall efficiency, however, is calculated from the head, capacity, and driver power input measurements. It must be recognized that, in the extreme case, the accuracy tolerance on overall efficiency could be as large as the sum of the accuracy tolerances of these three measurements. It will, however, be assumed that the most probable value of the overall efficiency accuracy tolerance is the squareroot of the sumof the squaresof the individual tolerances. In the computation of test data, the final values obtained for head, capacity, driver power input, overall efflciency, and pump speed shall be shown with the appropriate tolerance following each value.

COPYRIGHT American Water Works Association Licensed by Information Handling Services

or

A W W A ELO1 8 8 W 0783350 0002836 4

This appendix is for information only and is not a part of AWWA E101.

Suggested Specification Form for the Purchase of Vertical Turbine Pumps

Vertical Turbine Pump Specifications

1.

Purchaser

2.

Address

3.

Installation site

4.

Job reference no.

Date 5. Electric

mover: 6.

no.

Item

No. required

required

Prime Other

7.

Prime mover data: PhaseElectrical: FrequencyVoltage

rPm

Mechanical: Engine desired): (type

Gas

Gasoline

Diesel

Other

Maximum operating rpm

a.

Driver: Vertical hollow-shaft motor drive (Sec.A-2.3.1) Vertical solid-shaft motor drive (Sec. A-2.3.2) Vertical hollow-shaft right-angle gear drive (Sec. A-2.3.3) Vertical hollow-shaft belted drive (Sec. A-2.3.4) Combination drive (Sec. A-2.3.5) Submersible motor (Sec. B-2.1) Other

9. I o.

Water

Line-shaft lubrication required: Oil

Below base

Type of discharge:Surface If below base: Distance from datum discharge tee

II.

Other requirements

66

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Other

(see Sec. A-2.4) to centerline of ft (my

A W W A €101 8 4

0783350 0002817 b VERTICAL TURBINE PUMPS

67

Pump Operating Conditions 12.

Design capacity

gpm (m3/h)”

13.

Datum elevation

14.

Pumping level below datum at design capacity

15.

Total head above datum

16.

Total pump head at

17.

Operating Minimum range:

ft (m)” ft (m)”

ft (m)”

(static plus system friction) at design capacity

fi (m)”

design capacity (line 14 plus line 15) total pump head

ff

Maximum total pump head 18.

Other operating conditions

19.

Overall length (datum

20.

Length of suction pipe required

h)”

ft (m)”

to inlet of pump suction case-Part 40,

Table 1)

ff (m)t

ft (m)” Description of Installation

21.

Type of installation: Well

Can

OtherSump

22.

Minimum inside diameter of well or casing to pump setting

23.

Maximum permissible outside diameter of pump

24.

Total depth of well

in. (mm)” in. (mm)”

ft (m)”

NOTE:A well is considered straight if a 20-ft (6-m) long cylinder equal to the maximum permissible outsidc diameter of the pump will not bind when lowered to a depth equal to the pump setting.

ft (m)*

25.

Static water level below datum

26.

Sand in water: (After

15-min pumping interval) Concentration-ppm (mg/L)*

27.

Gas in water: (Type,

if known) Concentration-ppm

28.

Other conditions:

29.

Special materials required to resist corrosion and/or erosion:

(mg/L)*

Connections and Accessories 30.

Discharge flange:

31.

Companion flange required: Yes

32.

Strainer Yes required:

in. (mm)”, 125-lb ANSI

No

in. (mm)*, 125-lb ANSI

No

Frequency Lubricator Norequired: Yes 33.Voltage 34.

Prelube water tank required: Yes

35.

Automatic lubrication controls required: Time delay

36.

Air line and gauge required: Yes

No

gal (L)*

Capacity relay

Float switch

No

Pumps are to be furnished in accordance with AWWA E I O1-88, with the following exceptions

submersible pumps, items 9, 20, 33, 34, and 35 do not apply. ‘Indicate unit of measure.

~ O T E For :

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