Downloaded 20 times
![xi
from many materials, including concrete and steel pipe. Barrel inlet piping inlet velo-
city and barrel dimensions will affect pump performance. Barrel inlets located too
close to the pump suction inlet may produce turbulence affecting performance or caus-
ing vibration. Flow vanes and/or suction inlet devices may be required. This standard
does not include pump barrel requirements. Requirements for pump cans, including
installation, can be found in ANSI/HI 9.8, Rotodynamic Pumps for Pump Intake
Design. This standard does not require the pump manufacturer to furnish the barrel
nor to mount the barrel to the pump. If there is a requirement for furnishing the barrel
or mounting the pump in the barrel, this should be noted by the purchase documents.
II.B. Advisory Information on Product Application. This standard does not cover
applications or manufacturing technologies. Some waters may have high conductivity
levels well in excess of 200 µhm/cm, where it may be advisable to consult with a
metallurgist or corrosion expert to determine whether special materials or techniques
to deal with galvanic corrosion are required. The purchaser should identify special
requirements and deviations from this standard and include appropriate language in
the purchase documents. (For example, Sec. 4.4.3.2.3 of this standard requires vertical
pump suction cases and bells to have grease-packed CA [bronze] bearings. If other
types of bearings are required, this should be stated in the purchase documents.)
II.B.1 Materials. Materials required by this standard are selected based on suit-
ability for operation with water as described in the scope. Selection is based on success-
ful experience in the waterworks industry and local code and regulation requirements
for suitable materials.
II.B.1.1 Treatment chemicals. The potential for corrosion because of chemicals
added to the water should be considered. Materials, including some bronzes and rub-
ber compounds exposed to water containing chlorine, chloramines, or other chemicals,
may not be suitable. If such problems are anticipated, the purchase documents should
identify the maximum expected concentrations of these chemicals and other factors,
such as pH and temperature ranges, that may affect the corrosivity of these chemicals.
The purchaser and manufacturer should be aware that at times the pump may be used
to disperse chemicals into the system, which may result in local concentrations much
higher than normal concentration intended for the system. The purchaser should con-
sult with the manufacturer and, if appropriate, specify special requirements for these
materials in the purchase documents.
II.B.1.2 Disinfection chemicals. Pumps are often disinfected prior to being
placed in service initially or after a repair. During the disinfection process, wetted
surfaces are exposed to liquids far more corrosive than that allowed by the scope of
Copyright © 2016 American Water Works Association. All Rights Reserved.
©](https://image.slidesharecdn.com/awwa-e103-horizontalandverticalline-shaftpumps-230508125036-64c11722/75/AWWA-E103-Horizontal-and-Vertical-Line-Shaft-Pumps-pdf-11-2048.jpg)
![HORIZONTAL AND VERTICAL LINE-SHAFT PUMPS 45
Weighted-average head accuracy: 0.4 + 0.72 = 0.76 percent (Eq B.11)
The combined accuracy of the efficiency is
Ac = √ (0.76)2 + (0.75)2 + (0.25)2
= ±1.10 percent (Eq B.12)
SECTION B.3: DEFINITIONS AND SYMBOLS
1. Datum: The elevation of the 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.
2. Driver efficiency (Ed): The ratio of the driver output to the driver input,
expressed in percent.
3. Driver power input: The power input to the driver, expressed in horse-
power. 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 kilo-
watt input measured at the conduit box on the discharge head divided by 0.746.
No satisfactory evaluation of this term for engine-driven pumps is available.
4. Head above datum (ha): The head measured above the datum, expressed
in feet (meters) of liquid, plus the velocity head at the point of pressure measurement.
5. Head below datum (hb): The vertical distance, in feet (meters), from the
datum to the pumping level.
6. Overall efficiency (E): The ratio of pump output, in horsepower, to
motor power input.
7. Pump output, in horsepower (hp) [water hb (WHP)]: Calculated from
the following expression:
hp =
QH × specific gravity of liquid pumped
(Eq B.13)
3,960
Where:
Q = rate of flow, in gpm
H = pump total head, in ft
8. 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.
Copyright © 2016 American Water Works Association. All Rights Reserved.
©](https://image.slidesharecdn.com/awwa-e103-horizontalandverticalline-shaftpumps-230508125036-64c11722/75/AWWA-E103-Horizontal-and-Vertical-Line-Shaft-Pumps-pdf-65-2048.jpg)
![HORIZONTAL AND VERTICAL LINE-SHAFT PUMPS 55
Expected Accuracy of Field Test
Measurement Instrument Accuracy Accuracy Squared
Head above datum —
Head below datum —
Weighted-average head accuracy*
Capacity
Power
Combined accuracy
√ (Sum of accuracy squared (from above)
*Average is weighted according to the proportion of head above datum and head below datum to total head:
(Accuracy of hb) ×
hb
+
(Accuracy of ha) ×
hb
= weighted average head accuracy
H H
Test Readings and Calculations
All readings except No. 1 are taken when pumping.
No. Symbol Units 1 2 3
1 Head below datum when not pumping ft (m)
2 Drawdown ft (m)
3 hb Head below datum ft (m)
4 Zs Datum to centerline suction gauge ft (m)
5 Zd Datum to centerline discharge gauge ft (m)
6 hgs Suction pressure head reading ft or psi
(m or kg/cm2)
7 hgd Discharge pressure head reading ft or psi
(m or kg/cm2)
8 Suction pressure head above datam = (4)+(6) ft (m)
9 Discharge pressure head above datum = (5)+(7) ft (m)
10 hvs Velocity head in suction pipe* ft (m)
11 hvd Velocity head in discharge pipe* ft (m)
12 ha Head above datum* = [(11)+(9)] – [(10)+(8)] ft (m)
13 h Total head* = (3)+(12) ft (m)
14 Q Capacity gpm (m3/h)
Current Line A amps
15 Current Line B amps
Current Line C amps
16 Voltage Phase AB V
Voltage Phase BC V
Voltage Phase AC V
17 Revolutions of watt-hour meter disc (constant)
18 Time sec
19 Watt meter reading
20 Electrical input* from (17) and (18) or (19) kW
21 Horsepower input* = (16)/0.746 hp
22 Pump speed rpm
23 Pump output = (13) × (14) × sp gr/3,960 hp†
24 Pump efficiency* = (23)/(21) percent
25 Motor efficiency* (source) percent
26 Overall field efficiency* = (24) × (25) percent
*Calculated.
†Results will be in horsepower only if head measurements are in feet of liquid (hp × 0.746 = kW).
Figure B.6 Expected accuracy of field test
Copyright © 2016 American Water Works Association. All Rights Reserved.
©](https://image.slidesharecdn.com/awwa-e103-horizontalandverticalline-shaftpumps-230508125036-64c11722/75/AWWA-E103-Horizontal-and-Vertical-Line-Shaft-Pumps-pdf-75-2048.jpg)
More Related Content
Similar to AWWA-E103-Horizontal and Vertical Line-Shaft Pumps.pdf
AWWA-E103-Horizontal and Vertical Line-Shaft Pumps.pdf
- 1. AWWA Standard SM ® Horizontal andVertical Line-Shaft Pumps Effective date: Feb. 1, 2016. First edition approved by AWWA Board of Directors June 24, 2007. This edition approved June 7, 2015. Approved by American National Standards Institute Nov. 9, 2015. ANSI/AWWA E103-15 (Revision of ANSI/AWWA E103-07) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 2. ii AWWA Standard This documentis 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 pub- lication of a standard does not constitute endorsement of any product or product type, nor does AWWA test, certify, or approve any product. The use of AWWA standards is entirely voluntary. This standard does not supersede or take precedence over or displace any applicable law, regulation, or code of any governmental authority. AWWA standards are intended to represent a consensus of the water supply industry 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 Official Notice section of Journal – American Water Works Association. The action becomes effective on the first day of the month following the month of Journal – American Water Works Association publication of the official notice. American National Standard An American National Standard implies a consensus of those substantially concerned 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 preclude anyone, whether that person has ap- proved the standard 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 encour- aged to state on their own responsibility in advertising and promotional materials or on tags or labels that the goods are produced in conformity with particular American National Standards. Caution Notice: The American 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, 25 West 43rd Street, Fourth Floor, New York, NY 10036; 212.642.4900; or emailing info@ansi.org. ISBN-13, print: 978-1-62576-138-5 eISBN-13, electronic: 978-1-61300-364-0 DOI: http://dx.doi.org/10.12999/AWWA.E103.15 All rights reserved. No part of this publication may be reproduced or transmitted in any form or by any means, electronic or mechanical, including photocopy, recording, or any information or retrieval system, except in the form of brief excerpts or quotations for review purposes, without the written permission of the publisher. Copyright © 2015 by American Water Works Association Printed in USA hours of work by your fellow water professionals. Revenue from the sales of this AWWA material supports ongoing product development. Unauthorized distribution, either electronic or photocopied, is illegal and hinders AWWA’s mission to support the water community. This AWWA content is the product of thousands of Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 3. iii Committee Personnel The AWWAStandards Committee on Horizontal and Vertical Line-Shaft Pumps, which reviewed and approved this standard, had the following personnel at the time of approval: Anthony M. Naimey, Chairman General Interest Members E.P. Butts, 4B Engineering, Salem, Ore. (AWWA) J.J. Gemin,* Standards Council Liaison, Bath, Mich. (AWWA) S.N. Foellmi, Black & Veatch Corporation, Irvine, Calif. (AWWA) F.H. Hanson, Albert A. Webb Associates, Riverside, Calif. (AWWA) S.R. Hussain,† CH2M HILL, Redding, Calif. (AWWA) B. Kuhnel, Malcolm Pirnie, Water Division of Arcadis, Carlsbad, Calif. (AWWA) T.J. McCandless,* Standards Engineer Liaison, AWWA, Denver, Colo. (AWWA) C.T. Michalos, MWH, Colorado Springs, Colo. (AWWA) A.M. Naimey, CH2M HILL, Santa Ana, Calif. (AWWA) M. Seals, Indiana American Water, Greenwood, Ind. (AWWA) C. Yang, Keller, Texas (AWWA) Producer Members M.C. Bennett, Layne Christensen Company, Stuttgart, Ark. (AWWA) J. Bird, Flowserve Corporation, Taneytown, Md. (AWWA) J. Claxton, Patterson Pump Company, Toccoa, Ga. (AWWA) M. Coussens, Peerless Pump Co., Indianapolis, Ind. (AWWA) A.R. Sdano, Fairbanks Morse Pump Corporation, Kansas City, Kan. (AWWA) User Members S. Ahmed, Detroit Water and Sewerage Department, Detroit, Mich. (AWWA) D. Carroll, City of Aurora Water, Aurora, Colo. (AWWA) J.S. Casagrande, Connecticut Water Service Inc., Clinton, Conn. (AWWA) M. Higginbottom, Veolia Water North America, Fremont, N.H. (AWWA) J.P. Taylor, Granite City, Ill. (AWWA) * Liaison, nonvoting †Alternate Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 4. This page intentionallyblank. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 5. v Contents All AWWA standardsfollow the general format indicated subsequently. Some variations from this format may be found in a particular standard. SEC. PAGE SEC. PAGE Foreword I Introduction..................................... vii I.A Background...................................... vii I.B History............................................. vii I.C Acceptance...................................... viii II Special Issues..................................... ix II.A General............................................. ix II.B Advisory Information on Product Application.................................. xi II.C Pump Tests...................................... xii II.D Vibration Limits.............................. xiii III Use of This Standard....................... xiii III.A Information for Manufacturers........ xiii III.B Basic Data for Vertical Pumps......... xix III.C Basic Data for Horizontal Pumps.... xix IV Modification to Standard................. xx V Major Revisions................................ xx VI Comments....................................... xx Standard 1 General 1.1 Scope................................................. 1 1.2 Purpose.............................................. 2 1.3 Application......................................... 2 2 References......................................... 3 3 Definitions........................................ 5 4 Requirements 4.1 Materials.......................................... 10 4.2 General Design: Common to Horizontal and Vertical Pumps........................................ 16 4.3 General Design: Horizontal Pumps.. 20 4.4 General Design: Vertical Pumps....... 22 4.5 Coatings........................................... 27 4.6 Vibration Limits............................... 29 5 Verification 5.1 Factory Tests.................................... 29 5.2 Submittals........................................ 29 6 Marking, Preparation for Shipment, and Affidavit 6.1 Marking........................................... 30 6.2 Packaging and Shipping................... 30 6.3 Affidavit of Compliance................... 31 Appendixes A Pump Cross Sections........................33 B Field Testing of Pumps B.1 Purpose of Field Tests....................... 39 B.2 Accuracy of Field Testing................. 40 B.3 Definitions and Symbols.................. 45 B.4 Instrumentation.............................. 46 B.5 Procedure......................................... 53 C Suggested Data Form for the Purchase of Horizontal Pumps.........................................59 Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 6. vi D Suggested DataForm for the Purchase of Vertical Line-Shaft Pumps......................61 E Engineering Information and Recommendations E.1 Common for Horizontal and Vertical Pumps........................... 63 E.2 Horizontal Pumps............................ 63 E.3 Vertical Pumps................................ 64 Figures A.1 Separately Coupled, Single-Stage, Inline, Flexible Coupling Pump with Overhung Impeller...............34 A.2 Separately Coupled, Single-Stage, Inline, Rigid Coupling Pump with Overhung Impeller...............35 A.3 Separately Coupled, Single-Stage, Frame-Mounted Pump with Overhung Impeller.......................36 A.4 Separately Coupled, Single-Stage, Axial (Horizontal) Split-Case Pump with Impeller Between Bearings.......................................37 A.5 Deep-Well Pumps..............................38 B.1 Field-Test Diagram for Line-Shaft Vertical Turbine Well Pump....... 47 B.2 Field-Test Diagram for Vertical Turbine Pump for Booster Service........................................ 47 B.3 Field-Test Diagram for Horizontal Split-Case Pump........................ 48 B.4 Field-Test Diagram for End-Suction Pump......................................... 48 B.5 Pipe Requirements for Orifice, Flow Nozzles, and Venturi Tubes........ 49 B.6 Expected Accuracy of Field Test....... 55 B.7 Pump Field-Test Report.................... 57 E.1 Horizontal Pump Nominal Impeller-Ring Diametrical Clearance.................................. 64 E.2 Friction Loss in Discharge Heads...... 65 E.3 Friction Loss for Standard Pipe Column..................................... 66 E.4 Mechanical Friction in Line Shafts... 67 Tables 1 Pump (Horizontal or Vertical) Parts, Materials, and Definitions.......... 12 2 Horizontal Pump Parts, Materials, and Definitions.......................... 13 3 Vertical Pump Parts, Materials, and Definitions.......................... 15 4 Materials.......................................... 17 B.1 Limits of Accuracy of Pump Test Measuring Devices in Field Use.................................... 41 E.1 Diameters and Weights of Standard Discharge Column Pipe Sizes................................... 65 SEC. PAGE SEC. PAGE Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 7. vii Foreword This foreword isfor information only and is not a part of ANSI*/AWWA E103. I. Introduction. I.A. Background. This standard describes the minimum requirements for horizontal centrifugal pumps and for vertical line-shaft pumps for installation in wells, water treatment plants, water transmission systems, and water distribution systems. Pumps described in this standard are intended for pumping freshwater at flow rates (at best efficiency point) ranging from 100 gpm to 40,000 gpm (23 m3/hr to 9,100 m3/hr) at discharge pressures dictated by pump type and discharge conditions. This standard is applicable for driver power range from 10 hp to 1,500 hp (7 kW to 1,100 kW); however, this standard does not include requirements for drivers. I.B. History. The original standard for vertical line-shaft turbine pumps presented 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 motors were added in the 1977 revision, together with numerous editorial changes and conversions to the international system of units. The 1977 standard was reaffirmed in 1982 without revision. Additional revisions were made in 1988. In 1994, AWWA’s Standards Council approved development of a new standard for horizontal centrifugal pumps. The new standard was assigned to AWWA Standards Committee 276 for Horizontal Centrifugal Pumps. Upon review of pump standards development in 1996, AWWA’s Standards Council modified the development pro- cess to include two new pump standards to replace ANSI/AWWA E101-88, Vertical Turbine Pumps—Line Shaft and Submersible Types. As part of this action, two com- mittees were renamed. AWWA Standards Committee 276 for Horizontal Centrifugal Pumps was changed to AWWA Standards Committee 276 for Horizontal and Vertical Line-Shaft Pumps. Committee 276 was charged with development of ANSI/AWWA E103, Horizontal and Vertical Line-Shaft Pumps. AWWA Standards Committee 375 for Vertical Turbine Pumps was changed to AWWA Standards Committee 375 for Submersible Vertical Turbine Pumps. Committee 375 was charged with development * American National Standards Institute, 25 West 43rd Street, Fourth Floor, New York, NY 10036. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 8. viii of ANSI/AWWA E102,Submersible Vertical Turbine Pumps. During development of these two replacement standards, ANSI/AWWA E101-88 was withdrawn effective June 2000. The first edition of ANSI/AWWA E103 was approved by the AWWA Board of Directors on June 24, 2007. This edition was approved on June 7, 2015. I.C. Acceptance. In May 1985, the US Environmental Protection Agency (USEPA) entered into a cooperative agreement with a consortium led by NSF International (NSF) to develop voluntary third-party consensus standards and a certificationprogramfordirectandindirectdrinkingwateradditives.Othermembersof the original consortium included the Water Research Foundation* (formerly AwwaRF) and the Conference of State Health and Environmental Managers (COSHEM). The American Water Works Association (AWWA) and the Association of State Drinking Water Administrators (ASDWA) joined later. In the United States, authority to regulate products for use in, or in contact with, drinking water rests with individual states.† Local agencies may choose to impose requirements more stringent than those required by the state. To evaluate the health effects of products and drinking water additives from such products, state and local agencies may use various references, including 1. An advisory program formerly administered by USEPA, Office of Drinking Water, discontinued on Apr. 7, 1990. 2. Specific policies of the state or local agency. 3. Two standards developed under the direction of NSF‡: NSF/ANSI 60, Drinking Water Treatment Chemicals—Health Effects, and NSF/ANSI 61, Drinking Water System Components—Health Effects, and NSF/ANSI 372 Drinking Water System Components—Lead Content. 4. Other references, including AWWA standards, Food Chemicals Codex, Water Chemicals Codex,§ and other standards considered appropriate by the state or local agency. Various certification organizations may be involved in certifying products in accor- dance with NSF/ANSI 61. Individual states or local agencies have authority to accept or accredit certification organizations within their jurisdictions. Accreditation of certi- fication organizations may vary from jurisdiction to jurisdiction. * Water Research Foundation, 6666 West Quincy Avenue, Denver, CO 80235. †Persons outside the United States should contact the appropriate authority having jurisdiction. ‡NSF International, 789 North Dixboro Road, Ann Arbor, MI 48105. § Both publications available from National Academy of Sciences, 500 Fifth Street, NW, Washington, DC 20001. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 9. ix Annex A, “ToxicologyReview and Evaluation Procedures,” to NSF/ANSI 61 does not stipulate a maximum allowable level (MAL) of a contaminant for substances not regulated by a USEPA final maximum contaminant level (MCL). The MALs of an unspecified list of “unregulated contaminants” are based on toxicity testing guidelines (noncarcinogens) and risk characterization methodology (carcinogens). Use of Annex A procedures may not always be identical, depending on the certifier. ANSI/AWWA E103 does not address additives requirements. Users of this stan- dard should consult the appropriate state or local agency having jurisdiction in order to 1. Determine additives requirements, including applicable standards. 2. Determine the status of certifications by parties offering to certify products for contact with, or treatment of, drinking water. 3. Determine current information on product certification. NSF/ANSI 372, Drinking Water System Components—Lead Content, specifies restrictions for maximum lead content of materials in contact with drinking water. The user shall specify NSF/ANSI 372 when applicable in the purchase documents. Currently compliance with NSF/ANSI 372 is mandatory in some states and meets the new low lead requirements of the U.S. Safe Drinking Water Act, which went into effect January 2014. II. Special Issues. II.A. General. A pumping system consists of several components: the pump, the driver, the controls, the baseplate or mounting plate, the foundation, suction and discharge piping, and in many cases auxiliary equipment such as cooling water and lubrication systems. This AWWA E 103 standard discusses only the pump unit. Users of this standard should review other publications such as the American Petroleum Institute (API) Recommended Practice 686, Recommended Practices for Machinery Installation and Installation Design; Hydraulic Institute (HI) Standard 1.3, Standard for Centrifugal Pumps for Design and Application; and HI 2.3, Standard for Vertical Pumps for Design and Application. Users should especially review these and other publications for information on baseplates, mounting plates, foundation design, connection into suction, discharge piping systems, and component alignment recommendations. Conditions under which a pump will operate must be carefully evaluated by the purchaser and described by the purchase documents. II.A.1 Operating range. Evaluations should include the determination of the hydraulic characteristics of the pumping system and the extremes (maximum and minimum) of heads and flows under which the pump will be required to operate. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 10. x II.A.2 Inlet conditions.Pump field performance and service life can be signifi- cantly reduced if pump inlet conditions, including net pump suction head (NPSH), are not appropriate. Anticipated pump performance curves, including net pump suc- tion head required (NPSHR) curves provided by manufacturers, are based on a flow pattern at the pump inlet being uniform, steady, and free from swirls and vortices. Inadequate pump inlet conditions can result in damaging vibrations, excessive com- ponent stresses, and reduced performance. Hydraulic Institute (HI) Standard ANSI/ HI 9.8, Rotodynamic Pumps for Pump Intake Design, provides recommendations for both suction pipe arrangements and wet pits (sumps). II.A.3 Operating region. This standard does not require pumps to be furnished that will operate within a preferred operating region (POR) or within an allowable operating region (AOR) as defined by ANSI/HI 9.6.3, Rotodynamic (Centrifugal and Vertical) Pumps—Guidelines for Allowable Operating Region. Operation outside these regions will have an adverse effect on the life of the pump. Purchasers should be aware of the operating limits when specifying pumps and should, as a minimum, define the maximum and minimum anticipated operating heads and flow rates. Purchasers may require submittal of data by manufacturers defining the operating regions and advising anticipated bearing life and vibrations when operating within these regions. Refer to Section III of this foreword. II.A.4 Drivers. This standard does not include requirements for drivers (motors, engines, gear drives, etc.). Driver torque characteristics must be suitable for the pump torque requirements and the pump starting and stopping method. Driver requirements should be provided by the purchase documents. Refer to NEMA (National Electrical Manufacturers Association) MG 1, Motors and Generators, for guidance in the proper selection and application of motors and generators. II.A.5 Driver mounting and compatibility. Drivers are an integral part of a pumping unit. Drivers affect pump-to-driver coupling requirements, motor stands (vertical turbine pumps), base plates (horizontal pumps), shaft seals, and vibra- tion levels. Bearings in drivers that support rotating elements of the pump must be designed for static and dynamic thrust loads. This standard does not require the pump manufacturer to furnish the driver nor to mount the driver to the pump. If this is a concern, requirements for furnishing or mounting the driver should be pro- vided by the purchaser. II.A.6 Can pumps. Pump barrels or cans, while not an integral part of a vertical pumping unit, can significantly affect pump performance, as can any sump arrange- ment that affects the flow pattern at the pump inlet. Pump barrels may be fabricated Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 11. xi from many materials,including concrete and steel pipe. Barrel inlet piping inlet velo- city and barrel dimensions will affect pump performance. Barrel inlets located too close to the pump suction inlet may produce turbulence affecting performance or caus- ing vibration. Flow vanes and/or suction inlet devices may be required. This standard does not include pump barrel requirements. Requirements for pump cans, including installation, can be found in ANSI/HI 9.8, Rotodynamic Pumps for Pump Intake Design. This standard does not require the pump manufacturer to furnish the barrel nor to mount the barrel to the pump. If there is a requirement for furnishing the barrel or mounting the pump in the barrel, this should be noted by the purchase documents. II.B. Advisory Information on Product Application. This standard does not cover applications or manufacturing technologies. Some waters may have high conductivity levels well in excess of 200 µhm/cm, where it may be advisable to consult with a metallurgist or corrosion expert to determine whether special materials or techniques to deal with galvanic corrosion are required. The purchaser should identify special requirements and deviations from this standard and include appropriate language in the purchase documents. (For example, Sec. 4.4.3.2.3 of this standard requires vertical pump suction cases and bells to have grease-packed CA [bronze] bearings. If other types of bearings are required, this should be stated in the purchase documents.) II.B.1 Materials. Materials required by this standard are selected based on suit- ability for operation with water as described in the scope. Selection is based on success- ful experience in the waterworks industry and local code and regulation requirements for suitable materials. II.B.1.1 Treatment chemicals. The potential for corrosion because of chemicals added to the water should be considered. Materials, including some bronzes and rub- ber compounds exposed to water containing chlorine, chloramines, or other chemicals, may not be suitable. If such problems are anticipated, the purchase documents should identify the maximum expected concentrations of these chemicals and other factors, such as pH and temperature ranges, that may affect the corrosivity of these chemicals. The purchaser and manufacturer should be aware that at times the pump may be used to disperse chemicals into the system, which may result in local concentrations much higher than normal concentration intended for the system. The purchaser should con- sult with the manufacturer and, if appropriate, specify special requirements for these materials in the purchase documents. II.B.1.2 Disinfection chemicals. Pumps are often disinfected prior to being placed in service initially or after a repair. During the disinfection process, wetted surfaces are exposed to liquids far more corrosive than that allowed by the scope of Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 12. xii this standard. Materialsrequired by this standard may not be suitable for prolonged exposure to corrosive chemicals, including chlorine and sodium hypochlorite. There- fore, these chemicals should be removed and surfaces flushed with water meeting scope requirements immediately after disinfection. II.B.1.3 Dealloying. Some waters promote dealloying corrosion of some copper alloys in the form of dezincification or dealuminization, particularly when the material is exposed to water at high velocity. If this is a concern, the purchaser should consult with the manufacturer and, if appropriate, require alternate materials in the purchase documents. II.B.2 Coatings. This standard requires that ferrous (except for stainless) sur- faces of pumps exposed to water be coated. The purchase documents should delete this requirement if coatings are not required. II.C. Pump Tests. II.C.1 Factory tests. II.C.1.1 Procedures. This standard requires factory tests to be performed in accordance with the current version of ANSI/HI 14.6, Rotodynamic Pumps for Hydraulic Performance Acceptance Tests. II.C.1.2 Extent. This standard requires nonwitnessed hydrostatic testing only. 1. For horizontal pumps: the assembled pump. 2. For vertical pumps: the bowl assembly and discharge head. II.C.1.3 Additional factory tests. Additional factory tests, including hydro- static tests of an assembled vertical pump, vertical pump column section, performance, NPSHR, mechanical, and witnessed tests, may be included by the purchase documents. II.C.2 Field tests. This standard does not include field performance testing requirements. The following can be used to define field-test requirements. 1. ANSI/HI 1.6 and 2.6 test standards, as described above for factory tests, may be used for field testing at the discretion of the purchaser. ANSI/HI test standards require minimum pipe lengths, internal straightening vanes, and other criteria that, while practical in a controlled test loop, may not be available in the field. Application of these standards for field testing requires parties to agree on the scope and protocol of the test prior to the test. 2. ASME-PTC 8.2, Centrifugal Pumps, relies on the parties’ agreement beforehand on the scope and protocol of the test. The code does not include acceptable performance tolerances and does not address how test results shall be used to compare with guarantees. 3. Appendix B included with this standard. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 13. xiii II.D Vibration Limits.The vibration characteristics of a pumping system depend on a combination of pump and driver design and construction, baseplate or mounting plate design and construction, support foundation design and construction, balancing requirements, the pump installation, component alignment requirements, and the operating flow rate relative to the pump’s operating best efficiency point. Users of this standard should review various HI standards and other standards regarding these subjects and provide requirements within the purchase documents regarding vibration limits and vibration limit verification. III. Use of This Standard. It is the responsibility of the user of an AWWA standard to determine that the products described in that standard are suitable for use in the particular application being considered. Users of horizontal centrifugal and vertical line-shaft pumps should not expect long-lasting or reliable service unless all aspects of the pump application are defined: operating conditions, environmental conditions, and local ambient conditions. Additionally, the pump and driver unit, baseplate or mounting plate, foundation system, and connecting suction and discharge piping must be designed, installed, and aligned as an integrated system. III.A. Information for Manufacturers. When placing orders for pumps, purchasers should provide basic data to manufacturers so that pumps will meet purchase document’s requirements. Suggested forms that can be used to order pumps are located in appendixes C and D. Users of this standard should review HI standards Rotodynamic Centrifugal Pumps for Design and Application (ANSI/HI 1.3), and Rotodynamic Vertical Pumps of Radial, Mixed, and Axial Flow Types for Design and Application (ANSI/HI 2.3), which provide requirements for proper pump applications, principal pump features, and recommended precautions for pumps. III.A.1 Basic data for vertical and horizontal pumps. III.A.1.1 Standard used—that is, ANSI/AWWA E103, Horizontal and Vertical Line-Shaft Pumps, of latest revision. III.A.1.2 Installation location (country, state, or province). III.A.1.3 Water data. III.A.1.3.a Temperature range. III.A.1.3.b pH range. III.A.1.3.c Vapor pressure range (function of altitude and temperature). III.A.1.3.d Maximum concentration of corrosive chemicals, including but not limited to 1. Free chlorine. 2. Chloramine. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 14. xiv 3. Chlorides. 4. Ozone. 5.Other (include other oxidants and corrosive chemicals). III.A.1.3.e Solids. 1. Maximum sand concentration after a 15-minute pumping interval. 2. Maximum size of solids allowed to pass through the pump. III.A.1.4 Operating conditions. III.A.1.4.a Altitude at impeller shaft (for vertical pumps, use the eye of the lowest impeller). III.A.1.4.b Maximum suction pressure or maximum static suction lift. III.A.1.4.c Pump startup and shutdown conditions: 1. Describe in detail if discharge valve is other than a mechanical gravity- actuated type of check valve. 2. If the driver is variable speed and the discharge valve is other than a mechan- ical nonactuated type of check valve, describe the timing and coordination of valve opening and closure with pump speed ramp-up and ramp-down times. III.A.1.4.d Reverse rotation. 1. Indicate if the pump system will or will not be equipped with means to pre- vent reverse shaft rotation. Nonreverse ratchets are required for motors that drive open line-shaft vertical turbine pumps having a minimum water level that is 50 ft (15 m) or more below the elevation of the shaft seal in the discharge head. 2. For pump systems without means to prevent reverse rotation, indicate the maximum differential pressure across the pump during flow reversal. III.A.1.4.e Speed. Specify speed for constant-speed pumps (usually maximum speed based on a review of pump curves and discussions with manufacturers). If variable- speed pumps are required, specify an operating speed range. III.A.1.4.f Sanitary codes. Provide information necessary for the pump to be constructed to meet applicable code requirements. III.A.1.5 Performance requirements. Refer to Section 3 of this standard for definition of terms. III.A.1.5.a At rated condition point. 1. Rate of flow. 2. Total head or bowl assembly total head. Note: Total head must be used for horizontal pumps. Either total head or bowl assembly total head can be used for vertical pumps. The latter is used when the purchaser Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 15. xv accounts for andis responsible for head losses in the strainer, suction pipe (if used), suc- tion vessel (can pumps), column, and discharge head. 3. Minimum efficiency: a. Pump efficiency, or b. Bowl assembly efficiency, if bowl assembly total head is specified, or c. Overall (wire-to-water) efficiency. Note: This can be specified only if the drive is supplied by the pump manufacturer. 4. Net positive suction head available (NPSHA) range. III.A.1.5.b At other condition points. Pumps are usually required to provide a minimum rate of flow under high head conditions, which may exist when multiple pumps operate, when the discharge gradient is at a maximum, or when the suction gra- dient is at a minimum. Pumps are also required to operate under minimum head con- ditions, which may exist when only one pump operates in a station that has multiple pumps, when the discharge gradient is at a minimum, or when the suction gradient is at a maximum. Including a system head curve, especially on multiple-pump installa- tions and variable-speed systems, will allow the pump supplier to select the most suit- able pump curve shape for the application. 1. Maximum head condition. Include data listed above for the rated condition point except: a. Instead of rate of flow, specify minimum rate of flow. b. Instead of total head or bowl assembly total head, specify maximum total head or maximum bowl assembly total head. 2. Minimum head condition. Include data listed above for the rated condition point except: a. Instead of rate of flow, specify maximum rate of flow. b. Instead of total head or bowl assembly total head, specify minimum total head or minimum bowl assembly total head. c. Instead of NPSHA, specify a maximum NPSHR. III.A.1.5.c Allowable suction specific speed (maximum or range). III.A.1.5.d Pump input power (brake horsepower). Specify the maximum input power required for the pump assembly over the required pump operating range. Note 1: Thrust-bearing power requirements must be considered by the purchaser and added to the pump input horsepower when pump thrust bearings are provided in the driver and the driver is not part of the pump assembly. Gear drive power require- ments must also be considered if the gear drive is not part of the pump assembly. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 16. xvi Note 2: Verticalturbine pump line-shaft bearing losses must also be considered by the purchaser and added to pump input horsepower when bowl assembly performance has been specified. III.A.1.5.e Best efficiency point (BEP). 1. Specify the minimum efficiency required at the BEP. 2. Flow at BEP. Pumps should be selected for maximum efficiency at the nor- mal condition point. Constant-speed pumps in a multiple-pump system normally operate at a higher flow rate when not operating in parallel with other pumps. Variable- speed pumps normally operate at a lower flow rate than the flow at the rated condition point, when the rated condition point is based on the maximum speed. Specify a range of flows or heads that the BEP must fall within. III.A.1.6 Construction requirements. III.A.1.6.a Impeller type: open, semi-open, or enclosed. III.A.1.6.b Impeller wear rings. Wear rings can be specified for enclosed impel- lers. Thrust-balance–type rings can be specified for both semi-open, and enclosed impellers. III.A.1.7 Stuffing box arrangement. Specify the type of sealing required. Select packing, single mechanical seal, or double mechanical seal. III.A.1.8 Packing or mechanical seal cooling and lubricating water requirements. III.A.1.8.a Water must be supplied to the packing or seal when the shaft is rotat- ing. Water suitable for this purpose may be available from the fluid being pumped. It may also be desirable to provide water to packing when the shaft is not rotating, to prevent loss of prime (pumps with suction lifts) or prevent packing from drying out. III.A.1.8.b If the water contains materials that can cause rapid packing wear or seal wear, suitable clean water at the appropriate pressure from an external source should be applied to the lantern ring of the packing. If a mechanical seal is used, it should be a double seal with clean water applied between the seal elements. III.A.1.8.c If the pressure of the pumped fluid at the upstream face of the pack- ing or seal is less than 10 psig (69 kPa), which may be the case with horizontal double- suction and end-suction pumps, clean water should be supplied from a connection to the pump volute. III.A.1.8.d If water at a pressure of 10 psig (69 kPa) or greater is not available for a period exceeding the pump manufacturer’s recommendations during startup (as may be the case with vertical pumps having deep settings or slowly rising water columns), clean water should be supplied from an external source during the startup period. III.A.1.8.e Specify cooling and lubricating water arrangement and requirements. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 17. xvii III.A.1.9 Column pipingfor vertical turbine pumps. Sizing of the column pipe and minimum column pipe wall thickness shall be the responsibility of the pump manu- facturer. The column pipe serves as a pressurized discharge pipe between the pump bowl assembly and the discharge head and is subject to the effects of internal pressure, com- bined weight of the bowl assembly and column piping including the pumped liquid, hydraulic thrust loads developed during pump operation, and vibration. When required by the purchaser, the pump manufacturer should provide information on the flow velo- city and friction loss in the column pipe. III.A.1.10 Shaft critical speed. This standard provides requirements for operat- ing speed locations of the shaft lateral and shaft torsional critical speeds for horizontal centrifugal and vertical line-shaft pumps. The shaft critical speeds have a significant relationship to potential vibration and shaft stress issues with a pump, especially with pumps having adjustable speed drives. It is recommended that users of this standard review the operating speed range of the pump and identify additional critical speed criteria in the purchase documents. III.A.2 Materials. III.A.2.1 Drinking water requirements. Refer to Sec. 4.1. The purchaser should state whether compliance with NSF/ANSI 61, Drinking Water System Components— Health Effects, and/or NSF/ANSI 372, Drinking Water System Components—Lead Content, is required. If compliance is required, the purchase documents should note, “This product shall be certified as suitable for contact with drinking water by an accred- ited certification organization in accordance with NSF/ANSI 61, Drinking Water Sys- tem Components—Health Effects, and/or NSF/ANSI 372, Drinking Water System Components—Lead Content.” Purchasers should be aware that the availability of NSF/ANSI 61–certified pumps may be very limited, and this requirement may limit competition and add to the cost and delivery time of the pumps. Purchasers should also be aware that some states may allow installation of noncertified pumps, based on submittal and acceptance of materi- als used to construct the pump, especially if suitable certified pumps are not available. Compliance with NSF/ANSI 372 meets the new low lead requirements of the US Safe Drinking Water Act, which went into effect January 2014. Most pump manufac- turers are able to certify compliance with NSF/ANSI 372. III.A.2.2 Alternative materials. Purchase documents may require alternative materials or limit manufacturer’s choices of materials listed in this standard. For example, this standard lists silicon bronze, aluminum bronze, and stainless steel as impeller materi- als. Silicon bronze may not be suitable if the water contains a significant concentration of Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 18. xviii chlorine or chloramine.Aluminum bronze and stainless-steel components may be more costly and difficult to fabricate than silicon bronze components. Purchasers should be aware that alternatives to or limitations on manufacturer’s selections may increase costs and delivery time. III.A.3 Flanges. This standard requires flat-faced flanges. If other facing is required, it must be specified by the purchaser. III.A.4 Factory tests. III.A.4.1 Tests other than the hydrostatic tests described in Section 5 may be desired. Purchasers can specify the following additional tests in accordance with current ANSI/HI standards: 1. Performance. 2. NPSHR. 3. Mechanical. 4. Prime time for self-priming pumps. 5. Airborne sound. III.A.4.2 Witnessed testing. Purchase documents may specify optional wit- nessed testing for all or some of the factory tests. III.A.4.3 Special testing. Purchase documents may specify variations from the ANSI/HI standard tests. These variations may include duplication of field conditions. III.A.4.4 Other testing. Purchase documents may specify testing a sample pump selected at random for any test other than the prescribed hydrostatic tests. III.A.5 Submittals. This standard includes minimum requirements for submit- tals. If additional submittals (including affidavits of compliance) are required, they should be provided by the purchase documents. Additional submittal data that may be required include: welding procedures and welder qualification requirements associated with column piping and discharge head assemblies, repair procedures for castings, tor- sional shaft stress analysis, lateral and torsional shaft vibration analysis, and structural dynamic analysis. The purchase documents should describe the desired submittals and analyses including the acceptance criteria. III.A.6 Shop inspections. This standard does not provide for inspections at the manufacturer’s facility either during or after the pumps are constructed. If inspections are required, the extent should be defined by the purchase documents. III.A.7 Installation and alignment. This standard does not contain requirements or recommendations regarding pump and driver installation or alignment of components and piping. Further, this standard does not contain requirements or recommendations regarding suction and discharge piping stiffness requirements for maintaining pump and Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 19. xix driver alignment. Itis not possible for pump manufacturers to make more than general recommendations regarding installation and alignment. This is due to many factors that can affect installation, some of which are beyond the control of the pump manufac- turer. Additionally, the degree of installation and alignment precision desired on the part of purchasers may vary significantly. Users of this standard should review the various Hydraulic Institute standards and other standards regarding these subjects and provide additional requirements in the purchase documents regarding installation and alignment of the pump and driver system. III.B. Basic Data for Vertical Pumps. III.B.1 Construction requirements. III.B.1.1 Specify type. Refer to ANSI/HI 2.1-2.2, Rotodynamic Vertical Pumps or Radial, Mixed, and Axial Flow Types for Nomenclature and Definitions, for a description of types. Select: 1. Barrel (can) pump with suction nozzle in discharge head or in barrel. 2. Deep well. 3. Wet pit with above-floor or below-floor discharge. III.B.1.2 Specify line-shaft details and bearing details. 1. Open or enclosed line shaft. 2. For open line shaft specify bearing material (bronze or rubber). 3. For enclosed line shaft specify lubrication (water or oil). III.B.1.3 Specify column pipe details. 1. Refer to appendix E for recommendations. 2. Specify nominal size, wall thickness, and material. III.B.2 Driver details. Although drivers are not included in this standard, they are an important component of a vertical pump. Refer to appendix E for recommendations. III.C. Basic Data for Horizontal Pumps. III.C.1 Construction requirements. III.C.1.1 Specify type. Refer to ANSI/HI 1.1-1.2, Rotodynamic Centrifugal Pumps for Nomenclature and Definitions, for a description of types. Select: 1. Separately coupled, single-stage, inline, flexible coupling. 2. Separately coupled, single-stage, inline, rigid coupling. 3. Separately coupled, single-stage, end suction. 4. Separately coupled, single-stage, horizontal, axial, or mixed flow. 5. Single-stage, horizontal, double- or single-suction split case. 6. Vertically mounted, horizontal, double- or single-suction split case. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 20. xx IV. Modification toStandard. Any modification of the provisions, definitions, or terminology in this standard must be provided by the purchaser. V. Major Revisions. Major changes made to the standard in this revision include the following: 1. Most sections of the standard underwent extensive revision. 2. Purchaser defined options are to be called out in the purchase documents. 3. A flow range requirement was added (Sec. 4.2.2). 4. New requirements were added for: castings (Sec. 4.2.1.6), impellers (Sec. 4.2.1.8), shafts (Sec. 4.2.3), vibration limits (Sec. 4.6 and Sec. II.D), casings and wear rings (Sec. 4.3.1.7), bowls (Sec. 4.4.3.1), and coatings (Sec. 4.5.5). VI. Comments. If you have any comments or questions about this standard, please contact Engineering and Technical Services at 303.794.7711, FAX at 303.795.7603; write to the department at 6666 West Quincy Avenue, Denver, CO 80235-3098; or email at standards@awwa.org. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 21. 1 AWWA Standard ® ANSI/AWWA E103-15 (Revisionof ANSI/AWWA E103-07) Horizontal and Vertical Line-Shaft Pumps SECTION 1: GENERAL Sec. 1.1 Scope This standard provides minimum requirements for horizontal centrifugal pumps and for vertical line-shaft pumps for installation in wells, water treatment plants, water transmission systems, and water distribution systems. 1.1.1 Service. Pumps described in this standard are intended for pump- ing freshwater having a pH range between 5.5 and 10.0, a temperature range from 33°F to 125°F (14°C to 37°C), a maximum chloride content of 250 mg/L, and a maximum suspended solids content of 1,000 mg/L, and that is either potable or will be treated to become potable. 1.1.2 Pumps covered by this standard. 1.1.2.1 Driver power range: 10 hp to 1,500 hp (7 kW to 1,100 kW). 1.1.2.2 Rate of flow (at BEP): 100 gpm to 40,000 gpm (23 m3/hr to 9,100 m3/hr). 1.1.2.3 Maximum discharge pressure ratings. The maximum steady-state pressure at the pump discharge (which considers the suction pressure, possible operation for short periods at shutoff head, and the elevation of the discharge) is limited to the pressure rating for the ANSI/AWWA C207 class of flange shown for the pump types described below. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 22. 2 AWWA E103-15 1.For horizontal pumps: • Discharge 42 in. (1,067 mm) and larger: Class E (275 psig, 1,900 kPa). • Discharge smaller than 42 in.: Class F (300 psig, 2,100 kPa). 2. For vertical line-shaft pumps: Class F (300 psig, 2,100 kPa). 1.1.2.4 Maximum steady-state suction pressure ratings. 1. For horizontal pumps: 50 psig (340 kPa). 2. For vertical line-shaft pumps: 100 psig (700 kPa). 1.1.3 Pump types included in this standard. 1.1.3.1 Horizontal pumps. Refer to Hydraulic Institute (HI) Standard ANSI/HI 1.1-1.2 for a description of types: 1. Separately coupled, single-stage, inline, flexible coupling. 2. Separately coupled, single-stage, inline, rigid coupling. 3. Separately coupled, single-stage, end suction. 4. Separately coupled, single-stage, horizontal, axial, or mixed flow. 5. Single-stage, horizontal, double- or single-suction split case. 6. Vertically mounted, horizontal, double- or single-suction split case. 1.1.3.2 Vertical pumps. Refer to ANSI/HI 2.1-2.2 for a description of types: 1. Barrel (can) pump with suction nozzle in discharge head or in barrel. 2. Deep well. 3. Wet pit with above-floor or below-floor discharge. 1.1.4 Drivers. This standard does not include drivers. 1.1.5 Conditions not covered by this standard. 1. Conditions resulting from water hammer, cavitation, and hydraulic pulsations. 2. Excessive installed operating noise and vibrations, which may require special design, construction, and installation. Sec. 1.2 Purpose The purpose of this standard is to provide minimum requirements for water system pumps of the types identified in Sec. 1.1. Sec. 1.3 Application This standard can be referenced by the purchaser for pumps described in Sec. 1.1. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 23. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 3 SECTION 2: REFERENCES This standard references the following documents. In their latest editions, they form a part of this standard to the extent specified within the standard. In any case of conflict, the requirements of this standard shall prevail. ANSI*/AWWA C207—Steel Pipe Flanges for Waterworks Service—Sizes 4 In. Through 144 In. (100 mm Through 3,600 mm). ANSI/AWWA C210—Liquid-Epoxy Coating Systems for the Interior and Exterior of Steel Water Pipelines. ANSI/AWWA C550—Protective Interior Coatings for Valves and Hydrants. ANSI/HI† 1.1-1.2—Rotodynamic Centrifugal Pumps for Nomenclature and Definitions. ANSI HI 1.4—Rotodynamic Centrifugal Pumps for Manuals Describing Installation, Operation, and Maintenance. ANSI/HI 2.1-2.2—Rotodynamic Vertical Pumps or Radial, Mixed, and Axial Flow Types for Nomenclature and Definitions. ANSI/HI 9.6.3—Rotodynamic (Centrifugal and Vertical) Pumps—Guide- line for Allowable Operating Region. ANSI/HI 9.6.4—Rotodynamic Pumps for Vibration Measurements and Allowable Values. ANSI/HI 9.8—Rotodynamic Pumps for Pump Intake Design. ANSI/HI 14.6—Rotodynamic Pumps for Hydraulic Performance Accep- tance Tests. ASME Boiler and Pressure Vessel Code, Sections VIII and IX. ASME‡ B1.20.1—Pipe Threads, General Purpose, Inch. ASME B4.1—Preferred Limits and Fits for Cylindrical Parts. ASME B16.1—Gray Iron Pipe Flanges and Flanged Fittings: Classes 25, 125, and 250. ASME B46.1—Surface Texture (Surface Roughness, Waviness, and Lay). ASTM A27/A27M-13—Standard Specification for Steel Castings, Carbon for General Application. * American National Standards Institute, 25 West 43rd Street, Fourth Floor, New York, NY 10036. †Hydraulic Institute, 9 Sylvan Way, Parsippany, NJ 07054. ‡ASME International, 3 Park Avenue, New York, NY 10016. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 24. 4 AWWA E103-15 ASTM*A36/A36M-14—Standard Specification for Carbon Structural Steel. ASTM A47/A47M-99—Standard Specification for Ferritic Malleable Iron Castings. ASTM A48/A48M-03—Standard Specification for Gray Iron Castings. ASTM A53/A53M-12—Standard Specification for Pipe, Steel, Black and Hot-Dipped, Zinc-Coated, Welded and Seamless. ASTM A108-13—Standard Specification for Steel Bar, Carbon and Alloy, Cold-Finished. ASTM A193/A193M-15—Standard Specification for Alloy-Steel and Stain- less Steel Bolting for High Temperature or High Pressure Service and Other Spe- cial Purpose Applications. ASTM A194/A194M-15—Standard Specification for Carbon Steel, Alloy Steel, and Stainless Steel Nuts for Bolts for High Pressure or High Temperature Service, or Both. ASTM A276/A276M-15—Standard Specification for Stainless Steel Bars and Shapes. ASTM A307-14—Standard Specification for Carbon Steel Bolts, Studs, and Threaded Rod 60,000 PSI Tensile Strength. ASTM A351/A351M-15—Standard Specification for Castings, Austenitic, for Pressure Containing Parts. ASTM A439-83—Standard Specification for Austenitic Ductile Iron Castings. ASTM A536-84—Standard Specification for Ductile Iron Castings. ASTM A582/A582M-12e1—Standard Specification for Free-Machining Stainless Steel Bolts. ASTM A743/A743M-13ae1—Standard Specification for Castings, Iron- Chromium, Iron-Chromium-Nickel, Corrosion Resistant, for General Application. ASTM B16/B16M-10—Standard Specification for Free-Cutting Brass Rod, Bar, and Shapes for Use in Screw Machines. ASTM B148-14—Standard Specification for Aluminum-Bronze Sand Castings. ASTM B505/B505M-14—Standard Specification for Copper Alloy Continu- ous Castings. ASTM B584-14—Standard Specification for Copper Alloy Sand Castings for General Applications. * ASTM International, 100 Barr Harbor Drive, West Conshohocken, PA 19428. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 25. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 5 ASTM F593-13a—Standard Specification for Stainless Steel Bolts, Hex Cap Screws, and Studs. AWWA Manual M11—Steel Pipe—A Guide for Design and Installation. ISO 1940-1—Mechanical Vibration—Balance Quality Requirements for Rotors in a Constant (Rigid) State—Part 1: Specification and Verification of Bal- ance Tolerances. MSS* SP-55—Quality Standard for Steel Castings for Valves, Flanges, Fit- tings, and Other Piping Components—Visual Method for Evaluation of Surface Irregularities. NEMA† MG 1—Motors and Generators. NSF/ANSI 61—Drinking Water System Components—Health Effects. NSF/ANSI 372—Drinking Water System Components—Lead Content. SSPC‡-SP6—Commercial Blast Cleaning. SSPC-SP10—Near-White Metal Blast Cleaning. SECTION 3: DEFINITIONS The following definitions shall apply in this standard. Definitions of pump components are included in Sec. 4.3. 1. Allowable operating range: Flow range at specified speeds with the impel- ler supplied, as limited by cavitation, heating, vibration, noise, shaft deflection, fatigue, and other similar criteria. This range is to be specified by the manufacturer. 2. Atmospheric head (hatm): Local atmospheric pressure expressed in ft (m). 3. Best efficiency point (BEP): The rate of flow and corresponding head condition at which maximum pump efficiency is achieved. 4. Bowl assembly efficiency (hba): This is the efficiency obtained from the bowl assembly, excluding hydraulic and mechanical losses within other pump components. 5. Bowl assembly input power (Pba): The power delivered to the bowl assem- bly shaft, expressed in hp (kW). * Manufacturers Standardization Society, 127 Park Street, NE, Vienna, VA 22180. †National Electrical Manufacturers Association, 1300 North 17th Street, Suite 900, Arlington, VA 22209. ‡SSPC: The Society for Protective Coatings, 40 24th Street, 6th Floor, Pittsburgh, PA 15222. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 26. 6 AWWA E103-15 6.Condition point, normal: The point at which the pump will normally operate. It may be the same as the rated condition point. 7. Condition point, rated: The rate of flow, head, net positive suction head required (NPSHR), and speed of the pump, as required in the purchase documents. 8. Condition point, specified: Synonymous with rated condition point. 9. Cosmetic defect: A blemish that has no effect on the ability of the com- ponent to meet the structural design and test requirements of this standard. Should the blemish or the activity of plugging, welding, grinding, or repairing of the blem- ish cause the component to fail these requirements, the blemish shall be considered a structural defect. 10. Datum: A horizontal plane that serves as the reference for head mea- surements taken during test. Vertical pumps are usually tested in an open pit with the suction flooded. The datum is then the eye of the first-stage impeller. Optional tests can be performed with the pump mounted in a suction can. Irrespective of pump mounting, the pump’s datum is maintained at the eye of the first stage impeller. For horizontal pump units, the pump’s datum shall be referenced from the centerline of the shaft. For vertical double-suction pumps, the pump’s datum shall be referenced from the center of the first/lowest impeller. 11. Electric motor input power (Pmot): The electrical input power to the motor, expressed in hp (kW). 12. Elevation head (Z): The potential energy of the liquid because of its elevation relative to datum level, measured to the center of the pressure gauge or liquid level. 13. Field test pressure: The maximum static test pressure used for leak test- ing a closed pumping system in the field if the pumps are not isolated. Gener- ally, it is 125 percent of the maximum allowable casing working pressure. Where mechanical seals are used, this pressure may be limited by the pressure-containing capabilities of the seal. Note: See definition for maximum allowable casing working pressure. Con- sideration may limit the field-test pressure of the pump to 125 percent of the maximum allowable casing working pressure on the suction side of double-casing can-type pumps and certain other pump types. 14. Friction head (hf): The hydraulic energy required to overcome fric- tional resistance of a piping system to liquid flow, expressed in ft (m). Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 27. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 7 15. Gauge head (hg ): The energy of the liquid because of its pressure rela- tive to atmospheric pressure, as determined by a pressure gauge or other pressure- measuring device. Gauge head is positive when the reading is above atmospheric pressure and negative when below. Gauge head is measured in ft (m). 16. Head (h): The expression of the energy content of the liquid referred to any arbitrary datum. It is expressed in units of energy per unit weight of liquid. The measuring unit for head is ft (m) of liquid. 17. Manufacturer: The party that manufactures, fabricates, or produces materials or products. 18. Maximum allowable casing working pressure: The highest pressure at the specified pumping temperature for which the pump casing is designed. This pressure shall be equal to or greater than the maximum discharge pressure. In the case of double-casing can pumps, the maximum allowable casing working pressure on the suction side may be different from that on the discharge side. Maximum allowable casing working pressure is expressed in psi (kPa). 19. Maximum discharge pressure: The highest discharge pressure to which the pump will be subjected during operation, which is expressed in psi (kPa). 20. Maximum suction pressure: The highest suction pressure to which the pump will be subjected during operation. 21. Net positive suction head available (NPSHA): The total suction head in ft (m) of water absolute, determined at the first-stage impeller datum, less the absolute vapor pressure of the water in ft (m): NPSHA = hsa – hvp (Eq 1) Where: hsa = total suction head absolute = hatm + hs (Eq 2) or NPSHA = hatm + hs – hvp (Eq 3) In can pumps, NPSHA is often determined at the suction flange. Since NPSHR is determined at the first-stage impeller, the NPSHA value must be adjusted to the first-stage impeller by adding the difference in elevation and sub- tracting the losses in the can. 22. Net positive suction head required (NPSHR): A minimum net positive suction head given by the manufacturer/supplier for a pump achieving a specified performance at the specified rate of flow, speed, and pumped liquid (occurrence of visible cavitation, increase of noise and vibration due to cavitation, beginning Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 28. 8 AWWA E103-15 ofhead or efficiency drop, head or efficiency drop of a given amount, limitation of cavitation erosion). Unless otherwise required in the purchase documents, a 3 percent drop in head (the accepted industry practice) will be used to determine NPSHR and is defined as NPSH3. 23. Overall efficiency (hOA): Also referred to as wire-to-water efficiency, this is the ratio of the power imparted to the liquid (Pw) by the pump to the power supplied to the motor (Pmot); that is, the ratio of the water horsepower to the power input to the motor, expressed in percent. 24. Pump efficiency (hp): The ratio of the pump output power (Pw) to the pump input power (Pp); that is, the ratio of the water horsepower to the brake horsepower, expressed in percent. 25. Pump input power (Pp): The power needed to drive the complete pump assembly, including bowl assembly input power, line-shaft power loss, stuffing box loss, and thrust-bearing loss. With pumps that have built-in thrust bearing, the power delivered to the pump shaft coupling is equal to the pump input power. With pumps that rely on the driver thrust-bearing, the thrust-bearing loss shall be added to the power delivered to the pump shaft. It is also called brake horsepower (bhp). Pump input power is expressed in hp (kW). 26. Pump output power (Pw): The power imparted to the liquid by the pump. It is also called water horsepower, and is expressed in hp (kW). 27. Pump total discharge head (hd): The sum of the discharge gauge head (hg) measured after the discharge elbow, plus the velocity head (hv) at the point of gauge attachment, plus the elevation (Zd) from the discharge gauge centerline to the pump datum. Pump total discharge head is measured in ft (m). hd = hg + hv + Zd (Eq 4) 28. Pump total head (H): The measure of energy increase per unit weight of the liquid, imparted to the liquid by the pump, expressed as the difference between the total discharge head and the total suction head. Total head is normally specified for pumping applications, since the complete characteristics of a system determine the total head required. Total head is some- times called total dynamic head (TDH). 29. Purchaser: The person, company, or organization that purchases prod- ucts, materials, or work to be performed. 30. Rate of flow (capacity) (Q): The total volume throughput per unit of time at the suction inlet. It includes both water and any dissolved or entrained gases existing at the stated operating conditions. Rate of flow is measured in gpm (m3/hr). Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 29. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 9 31. Shutoff: The condition of zero flow when no water is flowing from the pump during pump operation. 32. Single-plane balancing (also called static balancing): Correction of residual imbalance to a specified maximum limit by removing or adding weight in one correction plane only. Can be accomplished statically using balance rails or by spinning. 33. Speed (n): The number of revolutions of the shaft in a given unit of time. Speed is expressed as rpm. 34. Static suction lift (Zs): A hydraulic pressure below atmospheric at the intake port of the pump, expressed in ft (m). 35. Structural defect: A flaw that causes the component to fail the struc- tural design requirements or test requirements of this standard. This includes but is not limited to imperfections that result in leakage through the walls of a casting and failure to meet the minimum wall-thickness requirement. 36. Submerged suction: When the centerline of the pump inlet is below the level of the liquid in the supply source. 37. Supplier: The party that supplies material or services. A supplier may or may not be the manufacturer. 38. Total suction head (hs), closed suction: For closed suction installations, the pump suction nozzle may be located either above or below water level. The total suction head (hs), referred to the eye of the first-stage impeller, is the algebraic sum of the suction gauge head (hg), plus the velocity head (hvs) at point of gauge attachment, plus the elevation (Zs) from the suction gauge centerline (or manometer zero) to the pump datum: hs = hgs + hvs + Zs (Eq 5) The elevation (Zs) is positive when the suction gauge is located above the datum and negative when below. 39. Total suction head (hs), open suction: For open (wet pit) installations, the first-stage impeller of the bowl assembly is submerged in a pit. The submer- gence is expressed in ft (m) of water (Zw). Total suction head is measured in ft (m). The average velocity head of the flow in the pit is small enough to be neglected: hs = Zw (Eq 6) Where: Zw = vertical distance in ft (m) from free water surface to datum Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 30. 10 AWWA E103-15 40.Two-plane balancing (also called dynamic balancing): Correction of residual imbalance to a specified limit by removing or adding weight in two cor- rection planes. Accomplished by spinning on appropriate balancing machines. 41. Velocity head (hv): The kinetic energy of the liquid at a given cross section. Velocity head is measured in ft (m). Velocity head is expressed by the fol- lowing equation: hv = v2 (Eq 7) 2g Where: v = rate of flow divided by the cross-section area at the point of gauge connection; average velocity is expressed in ft/sec (m/sec) g = 32.2 ft/sec2 (9.81 m/sec2) 42. Vertical pump bowl assembly total head (Hba): The sum of gauge head (hg) measured at a gauge connection located on the column pipe downstream from the bowl assembly, plus the velocity head (hv) at point of gauge connection, plus the vertical distance (Zd) from datum to the pressure gauge centerline, minus the submergence (Zw), which is the vertical distance from datum to the water level, plus the friction loss between the bowl exit and point of gauge connection and in the suction pipe and strainer, if used (hf ). These friction losses are usually very small. Bowl assembly total head is measured in ft (m). Hba = hgd + hv + Zd – Zw + hf (Eq 8) 43. Working pressure (Pd): The maximum discharge pressure that occurs in the pump when it is operated at rated speed and suction pressure for the given application. Working pressure is expressed in psi (kPa). SECTION 4: REQUIREMENTS Sec. 4.1 Materials 4.1.1 Regulations. Materials shall comply with the requirements of the Safe Drinking Water Act and other federal regulations for potable water, waste- water, and reclaimed water systems as applicable. 4.1.2 Coatings, lubricants, and temporary corrosion prevention com- pounds. These materials shall comply with NSF/ANSI 61 or NSF/ANSI 372 when applied to surfaces that include but are not limited to interior pump surfaces, Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 31. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 11 interior pump column surfaces, and the exterior surfaces of pumps or pump com- ponents (usually vertical pump columns) immersed in water. 4.1.3 Pumpcomponents. Partnames,itemnumbers,anddefinitionsshown on Tables 1 through 3 are copied from ANSI/HI 1.1-1.2, Rotodynamic Centrifugal Pumps for Nomenclature and Definitions, and ANSI/HI 2.1-2.2, Roto-dynamic Vertical Pumps or Radial, Mixed, and Axial Flow Types for Nomenclature and Definitions. Item numbers refer to pump component locations as shown on draw- ings located in the referenced ANSI/HI standards and shown in appendix A. If a component does not have an item number, it is defined in this standard and not the ANSI/HI standard. Materials listed are requirements for pumps meeting this standard. If no material is listed, manufacturers may provide their standard mate- rial, unless requirements are described in subsequent sections of this standard or in the purchase documents. The following are abbreviations used in the tables and elsewhere in this standard: • CRM: corrosion-resistant material • CA: copper alloy Additional requirements for materials are also defined in Sec. 4.1.4. 4.1.3.1 Alternative materials. Materials shown in Tables 1 through 3 are suit- able for most applications with water meeting the conditions described in Sec. 1.1.1. However, materials shown may not be appropriate for all applications, water quali- ties, and jurisdictions. 1. Corrosion potential. Water may not be as corrosive as described in Sec. 1.1.1, or a long service life may not be required. In this case, materials such as cast- iron or ductile-iron impellers may be appropriate. 2. Water quality. Some waters promote dealloying corrosion of some cop- per alloys in the form of dezincification or dealuminization, particularly when the material is exposed to water at high velocity. In this case, appropriate cast iron, ductile iron, or stainless steel may also be required instead of the listed materials. 3. Regulatory requirements. Materials selected for components shown in Tables 1 through 3, which are in contact with the pumped fluid, do not have a lead content in excess of 1 percent except for bearings, which may contain as much as 8 percent. Specific materials or alternative materials may be required to meet regulatory requirements in some jurisdictions. The calculated weighted lead requirements of NSF/ANSI 372 must be met in all circumstances. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 32. 12 AWWA E103-15 Table1 Pump (horizontal or vertical) parts, materials, and definitions*† Part Name Item Number† Definition Materials List by AWWA Base plate 23 A member on which the pump and its driver are mounted. Cast Iron, Steel 4 Bushing, stuffing box 63 A replaceable sleeve or ring placed in the end of the stuffing box opposite the gland. CA 3 Coupling half, driver 42 The coupling half mounted on the driver shaft. Steel 4 Coupling half, pump 44 The coupling half mounted on the pump shaft. Steel 4 Deflector 40 A flange or collar around a shaft and rotating with it to prevent passage of liquid, grease, oil, or heat along the shaft. Steel 4 Rubber Gasket 73 Resilient material used to seal joints between parts to prevent leakage. Gland 17 A follower that compresses packing in a stuffing box or retains the stationary element of a mechanical seal. Cast Iron Stainless Steel 2 CA 4 Guard, coupling 131 A protective shield over a shaft coupling. Steel Impeller 2 A bladed member of the rotating assembly of the pump, which imparts the principal force to the liquid. Also called a propeller for axial flow pumps. CA 1 or 3 Stainless Steel 1 or 2 Key, impeller 32 A parallel-sided piece used to prevent the impeller from rotating relative to the shaft. Stainless Steel 1, 2, 3, or 4 Packing 13 A pliable lubricated material used to provide a seal around that portion of the shaft located in the stuffing box. Pressure bolting Fasteners used to assemble pump components, which can be pressurized. Use stainless steel 5 or 6 for pressure bolting that is wetted. Steel 5 can be used for nonwetted bolting. Stainless Steel 5 or 6 Ring, bowl (or case) 213 A stationary replaceable ring to protect the bowl (or case) at the running fit with the impeller ring or the impeller. CA 3 Stainless Steel 3 or 4 Ring, impeller 8 Provides water seal at impeller. CA 3 Stainless Steel 3 or 4 Ring, lantern 29 Spaces out packing to allow for injection of lubricant. CA 4 PTFE Seal, mechanical, rotating element 80 A device flexibly mounted on the shaft in or on the stuffing box having a smooth, flat-sealing face held against the stationary sealing face. Seal, mechanical, stationary element 65 A subassembly consisting of one or more parts mounted in or on a stuffing box and having a smooth flat-sealing face. Spacer, coupling 88 A cylindrical piece used to provide axial space for the removal of the rotating assembly or mechanical seal without removing the driver. Steel 3 Strainer 209 A device used to prevent large objects from entering the pump. Steel 4 CA 1, 2, or 3 Stainless Steel 1 or 2 Stuffing box 83 A portion of the casing through which the shaft extends and in which packing or a mechanical seal is placed to prevent or minimize leakage. Cast Iron *Part name, item number, and definition courtesy of Hydraulic Institute, ANSI/HI standards 1.1-1.2 and 2.1-2.2. †Refer to Appendix A of this standard for illustration of pumps with numbered parts. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 33. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 13 Table 2 Horizontal pump parts, materials, and definitions*† (continued) Part Name Item Number† Definition Materials List by AWWA Base 53 A pedestal to support a pump. Cast Iron Steel Bearing, inboard 16 The bearing nearest the coupling of a double-suction pump but farthest from the coupling of an end-suction pump. Bearing, outboard 18 The bearing most distant from the coupling of a double- suction pump but nearest to the coupling of an end- suction pump. Bracket, bearing 125 Detachable bracket that contains a bearing. Bushing, bearing 39 The removable portion of a sleeve bearing in contact with the journal. Bushing, interstage diaphragm 113 A tubular-shaped replaceable piece mounted in the interstage diaphragm. Bushing, pressure reducing 117 A replaceable piece used to reduce the liquid pressure at the reducing stuffing box by throttling the flow. Bushing, throttle, auxiliary 171 A stationary ring or sleeve placed in the gland of a mechanical seal subassembly to restrict leakage in the event of seal failure. Cap, bearing, inboard 41 The removable upper portion of the inboard bearing housing. Cap, bearing, outboard 43 The removable upper portion of the outboard bearing housing. Casing 1 The portion of the pump that includes the impeller chamber and volute or diffuser. Cast Iron Ductile Iron 1 or 2 Steel 6 Collar, shaft 68 A ring used on a shaft to establish a shoulder for a ball bearing. Collar, thrust 72 A circular collar mounted on a shaft to absorb the unbalanced axial thrust in the pump. Coupling, oil pump 120 A means of connecting the driver shaft to the oil pump shaft. Coupling, shaft 70 A mechanism used to transmit power from the drive shaft to the pump shaft, or to connect two pieces of shaft. Cover, bearing end 123 A plate closing the tachometer port in the end of the outboard bearing housing. Cover, bearing, inboard 35 An enclosing plate for either end of an inboard bearing of double-suction or multistage pumps, or for the impeller end inboard of the bearing of end-suction pumps. Cover, bearing, outboard 37 An enclosing plate for either end of the outboard bearing of double-suction or multistage pumps, or for the coupling end of the bearing of end-suction pumps. Cover, oil bearing cap 45 A lid or plate over an oil filler hole or inspection hole in a bearing cap. Cover, suction 9 A removable piece, with which the inlet nozzle may be integral, used to enclose the suction side of the casing of end-suction pumps. (Table continued next page) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 34. 14 AWWA E103-15 Table2 Horizontal pump parts, materials, and definitions*† (continued) Part Name Item Number† Definition Materials List by AWWA Diffuser 5 A piece, adjacent to the impeller exit, that has multiple passages of increasing area for converting velocity to pressure. Elbow, suction 57 A curved water passage, usually 90 degrees, attached to the pump inlet. Frame 19 A member of an end-suction pump to which are assembled the liquid end and rotating element. Cast Iron Ductile Iron 1 or 2 Gasket, impeller screw 28 Resilient material used to seal joint between hub of impeller and the impeller screw. Gasket, shaft sleeve 38 Resilient material used to provide a seal between the shaft sleeve and the impeller. Gauge, sight, oil 143 A device for the visual determination of the oil level. Gland, stuffing box, auxiliary 133 A follower provided for compression of packing in an auxiliary stuffing box. Guard, coupling 131 A protective shield over a shaft coupling. Housing, bearing 99 A body in which the bearing is mounted. Journal, thrust- bearing 74 A removable cylindrical piece mounted on the shaft that turns in the bearing. It may have an integral thrust collar. Key, bearing journal 76 A parallel-sided piece used for preventing the bearing journal from rotating relative to the shaft. Key, coupling 46 A parallel-sided piece used to prevent the shaft from turning in a coupling half. Locknut, bearing 22 A fastener that positions an antifriction bearing on the shaft. Locknut, coupling 50 A fastener holding a coupling half in position on a tapered shaft. Lockwasher 69 A device to prevent loosening of a nut. Nut, impeller 24 A threaded piece used to fasten the impeller on the shaft. Nut, shaft-adjusting 66 A threaded piece for altering the axial position of the rotating assembly. Nut, shaft sleeve 20 A threaded piece used to locate the shaft sleeve on the shaft. Retainer, grease 51 A contact seal or cover to retain grease. Ring, balancing 115 The stationary number of a hydraulic balancing device. Ring, casing 7 A stationary replaceable ring to protect the casing at the running fit with the impeller ring or the impeller. Seal 89 A device to prevent the flow of a liquid or gas into or out of a cavity. Shaft 6 The cylindrical member on which the impeller is mounted and through which power is transmitted to the impeller. Shim 67 A piece of material that is placed between two members to adjust their position. Sleeve, shaft 14 A cylindrical piece fitted over the shaft to protect the shaft through the stuffing box, and which may also serve to locate the impeller on the shaft. *Part name, item number, and definition courtesy of Hydraulic Institute, ANSI/HI standards 1.1-1.2 and 2.1-2.2. †Refer to Appendix A of this standard for illustration of pumps with numbered parts. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 35. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 15 Table 3 Vertical pump parts, materials, and definitions*† (continued) Part Name Item Number† Definition Materials List by AWWA Adapter, tube 195 A cylindrical piece used to connect discharge case to enclosing tube. Steel 3 Barrel or can, suction 205 A receptacle for conveying the liquid to the pump. Steel 4 CA 4 (for grease lubricated only) Bearing, line shaft enclosed 103 A bearing that also serves to couple portions of the shaft enclosing tube. CA 3 (for water flush applications) Bearing, sleeve 39 A replaceable, cylindrical bearing secured within a stationary member. Rubber CA 3 Bell, suction 55 A device used to receive the liquid and guide it to the first impeller. A flared tubular section for directing the flow of liquid into the pump. Cast Iron Steel 6 Ductile Iron 1 or 2 Bowl, intermediate 199 An enclosure within which the impeller rotates and that serves as a guide for the flow from one impeller to the next. Cast Iron Steel 6 Ductile Iron 1 or 2 Case, discharge 197 Aid flow from bowl to pump column. Cast Iron Steel 6 Ductile Iron 1 or 2 Case, suction 203 A device used to receive the liquid and guide it to the first impeller. Differs from a suction bell in that it allows for the attachment of suction piping. Cast Iron Steel 6 Ductile Iron 1 or 2 Collar, protecting 64 A rotating member for preventing the entrance of contaminating material. CA 2 or 3 Collet, impeller lock 84 A tapered collar used to secure the impeller to the pump shaft. Steel 3 Stainless Steel 4 Coupling, column pipe 191 A threaded sleeve used to couple sections of column pipe. Cast Iron Ductile Iron Steel 3 Coupling shaft 70 A mechanism used to transmit power from the line shaft to the pump shaft, or to connect two pieces of shaft. Steel 3 Stainless Steel 3 Elbow 57 A curved water passage, usually 90 degrees, attached to the pump inlet or discharge. Cast Iron, Steel Elbow, discharge 105 An elbow in an axial flow, mixed flow, or turbine pump by which the liquid leaves the pump. Cast Iron Flange, top column 189 A device used to couple column to discharge head. Cast Iron Steel 4 Head, surface discharge 187 A support for driver and pump column, and a means by which the liquid leaves the pump. Cast Iron Steel 4 Luricator 77 A device for applying a lubricant to the point of use. Nut, shaft-adjusting 66 A threaded piece for altering the axial position of the rotating assembly. CA 4 Steel 4 Ductile Iron Nut, tube 183 A device for sealing and locking the shaft-enclosing tube. Cast Iron (Table continued next page) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 36. 16 AWWA E103-15 Asnoted in Sec. III.A.2.2 in the foreword, purchasers can require alternative materials or limit manufacturer’s choices of material listed in this standard. 4.1.4 Physical and chemical properties. Materials shall conform to the requirements of this subsection (see Table 4). Sec. 4.2 General Design: Common to Horizontal and Vertical Pumps 4.2.1 Construction requirements. 4.2.1.1 Corrosion allowance. Iron and steel components subject to corro- sion or erosion shall have an allowance of 1/8 in. (3.2 mm). 4.2.1.2 Machined joints. Component parts that are assembled together shall have machined joints. Mating faces of bowls, bells, and casings shall allow the parallelism of the assembled joint to be gauged. Components that require accurate alignment when reassembled shall be designed with shoulders and rabbeted-fits. 4.2.1.3 Threading. Metric fine and unified fine (UNF) thread shall not be used. Table 3 Vertical pump parts, materials, and definitions*† (continued) Part Name Item Number† Definition Materials List by AWWA Pedestal, driver 81 A metal support for the driver of a vertical pump. Cast Iron Steel 4 Pipe, column 101 A vertical pipe by which the pumping element is suspended. Steel 2 Pipe, suction 211 A device for conveying the liquid to the pump’s suction. Steel 2 Plate, tension, tube 185 A device for maintaining tension on shaft-enclosing tube. Cast Iron CA 4 Shaft, head 10 The upper shaft in a vertical pump that transmits power from the driver to the line shaft. Steel 1 Stainless Steel 3 or 4 Shaft, line 12 The shaft that transmits power from the head shaft or driver to the pump shaft. Steel 1 Stainless Steel 3 or 4 Shaft, pump 6 The shaft on which the impeller is mounted and through which power is transmitted to the impeller. Steel 1 Stainless Steel 3 or 4 Sole plate 129 A metal pad, usually imbedded in concrete, on which the pump base is mounted. Cast Iron Steel 4 Tube, shaft-enclosing 85 A cylinder used to protect the drive shaft and to provide a means for mounting bearings. Steel 2 Umbrella, suction 95 A formed piece attached to the suction bowl to reduce disturbance at pump inlet and reduce submergence required. Cast Iron Steel 4 *Part name, item number, and definition courtesy of Hydraulic Institute, ANSI/HI standards 1.1-1.2 and 2.1-2.2. †Refer to Appendix A of this standard for illustration of pumps with numbered parts. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 37. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 17 4.2.1.4 Wrench clearances. Adequate clearance shall be provided at bolt locations to permit use of socket or box wrenches. 4.2.1.5 Structural defects. Components shall be free from structural defects. Table 4 Materials Material Type Referenced Designation Cast iron ASTM A48, Class 30 Copper alloy Type 1 (aluminum bronze) ASTM B148 or ASTM 505 alloys UNS C95200, C95300, C95400, C95500, C95600, or C95800 Type 2 (silicon bronze) ASTM B584 alloy UNS C87600 Type 3 ASTM B505, ASTM B584 alloys UNS C90300, C90700 and C89940; CDA C89835 Type 4 Alloys listed for “Type 3,” plus ASTM B505, ASTM B584 alloys UNS C83600, C83800, C84400, C93200 Type 5 (for fasteners) ASTM B16 Ductile iron Type 1 ASTM A536 Gr. 65-45-12 Type 2 (austenitic) ASTM A439 Gr. D-2 Malleable iron ASTM A47 Steel Type 1 ASTM A108, Gr. 1045 Type 2 ASTM A53 Gr. A Type 3 ASTM A108 Gr. 1213, 1113, 1144, 1020 Type 4 ASTM A36, A283 Type 5 (for fasteners) ASTM A307 Type 6 ASTM A27 Gr. U-60-30, ASTM A 216 Gr. WCB Stainless steel Type 1 ASTM A276, UNS S30400 Type 304, UNS S30403 Type 304L, ASTM A351, UNS J92700 Type CF3, UNS J92600 Type CF8, ASTM A743, UNS CF8M Type 2 ASTM A276, Type 316L, ASTM A351, UNS J92900 Type CF8M, UNS J92800 Type CF3M, ASTM A743, UNS CF8M Type 3 ASTM A276, UNS S41000 (Type 410 ) Type 4 ASTM A582, UNS S42000 (Type 416 ) Type 5 (for fasteners) ASTM A193 (or A194), Gr. 8 UNS S30400 Type 304, ASTM F593 UNS S30400 Type 304 Type 6 (for fasteners) ASTM A193 (or A194), Gr. 8M UNS SS31600 Type 316, ASTM F593 UNS SS31600 Type 316 Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 38. 18 AWWA E103-15 4.2.1.6Castings. Castings shall be clean, sound, and without defects that will weaken their structure or impair their service. 4.2.1.6.1 Surfaces of steel, stainless-steel, iron, and bronze castings shall be free of adhering sand, scale, cracks, and hot tears as determined by visual exami- nation. Other surface discontinuities shall meet the requirements of MSS SP-55, Table 1 and Annex A. Mould-parting fins and remains of gates and risers shall be chipped, filed, or ground flush. 4.2.1.6.2 If visual examination reveals defects, repair the castings or pro- vide new castings. Defects may be repaired by welding, provided the welder quali- fications and welding procedures are in accordance with the ASME Boiler and Pressure Vessel Code, Section IX. Provide postweld heat treatment per the cited material specification or in accordance with the ASME Boiler and Pressure Vessel Code, Section VIII. 4.2.1.6.3 Unless otherwise allowed in the purchase documents, structural defects may not be repaired. 4.2.1.6.4 Repairs within the bolt circle of any flange face shall not be allowed. 4.2.1.7 Flanges. 4.2.1.7.1 Suction and discharge nozzles shall be supplied with flange dimensions conforming to ASME B16.1 Class 125 cast iron, including bolt circle, number, and size of bolt holes. Flanges shall be flat-faced with the minimum thickness and diameter speci- fied in ANSI Class 125. Flanges 12 in. (305 mm) and smaller subject to a pressure exceeding 200 psig (1,400 kPa) and flanges larger than 14 in. (360 mm) subject to a pressure exceeding 150 psig (1,030 kPa) shall conform to ASME B16.1 Class 250 cast-iron dimensions. 4.2.1.7.2 Steel flanges for suction and discharge nozzles shall conform to ANSI/AWWA C207. Flange class shall be suitable for continuous service at the maximum required pressure rating. 4.2.1.8 Impellers. 4.2.1.8.1 Impellers shall be cast in one piece. 4.2.1.8.2 Impellers having a ratio of diameter versus width less than or equal to 6 shall receive a dynamic balance (a two-plane spin balance) to Grade G6.3 of ISO 1940 as a minimum. Impellers having a ratio of diameter versus width greater than 6 shall receive a static balance (a single-plane spin balance) to Grade G6.3 of ISO 1940 as a minimum. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 39. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 19 4.2.1.8.3 Unless otherwise required in the purchase documents, enclosed impellers with diameters larger than 10 in. (250 mm) shall have replaceable wear rings at wear surfaces or shall be designed to be machined to allow future ring installation. 4.2.1.8.3.1 Enclosed impellers shall have radial wear surfaces on the front (eye side) and, when balance holes are provided, on the back (hub side) as well. 4.2.1.8.3.2 When open or semi-open impellers are utilized, no wear sur- face can be supplied on impellers. Refer to Sec. 4.3, General Design: Horizontal Pumps, and Sec. 4.4, General Design: Vertical Pumps, for casing or bowl options for wear surfaces. 4.2.1.8.4 Hardness of the impeller or impeller wear rings shall be a mini- mum of 50 BHN (Brinell Hardness Number) less than that of the casing, bowl, or casing wear rings, unless nongalling metals or galling clearances are used. 4.2.1.8.5 When installed, wear rings shall be held in place by rabbet-fit and locked with screws, pins, anaerobic adhesives, or tack welded at three or more points. 4.2.1.8.6 Replaceable wear rings of special gall-resistant materials may be employed that would permit reduced running clearances. For materials with high galling tendencies, such as 300 series stainless steels, 0.005 in. shall be added to the above minimum clearances. High galling tendencies are typically observed in materials that have nickel as a subcomponent. 4.2.1.9 Stuffing box. 4.2.1.9.1 The stuffing box shall accommodate five rings of packing, sized from 3/8 in. (9.5 mm) to 1/7 in. (3.6 mm) of the shaft diameter, including any sleeve, plus a lantern ring or a mechanical seal, split or solid, balanced or unbalanced, with or without a throat bushing. 4.2.1.9.2 Construction details. 4.2.1.9.2.1 Packing or mechanical seals shall be replaceable without a requirement to remove the driver. 4.2.1.9.2.2 Glands shall be held in place by a minimum of two bolts having a minimum diameter of 3/8 in. (9.5 mm). Bolts shall be bronze (CA 4) or stainless steel 2. 4.2.1.9.3 Packing details. 4.2.1.9.3.1 Provide an extra ring of packing and delete the lantern ring if pumped fluid is clear and the pressure at the upstream face of the packing exceeds 10 psig (70 kPa). Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 40. 20 AWWA E103-15 4.2.1.9.3.2Cooling and lubricating water shall be supplied to the stuffing box from an external source or from a connection to the pump discharge volute (horizontal pumps only). Connecting piping, fittings, and valves shall be of CRM and shall include a throttling valve. Provide a minimum ¼-in. (6.3-mm) NPT (national pipe thread taper) connection for an external source. 4.2.1.9.4 Mechanical seals. Mechanical seals are a purchaser option. 4.2.1.9.5 Maximum stuffing box leakage. 1. Mechanical seal: 2 drops per minute. 2. Packing: 60 drops per minute, or as recommended by the pump manu- facturer for the shaft size furnished. 4.2.1.9.6 Packing shall not contain asbestos. 4.2.2 Flow Range Requirement. Unless otherwise required in the pur- chase documents, the pump shall be designed and constructed to operate over a flow range of 70 percent to 120 percent of the flow at the BEP. 4.2.3 Shaft. 4.2.3.1 The first lateral and torsional critical speeds of the shaft shall be no less than 120 percent of the maximum pump operating speed. 4.2.3.2 Shaft diameter selection shall be determined by the pump manu- facturer based on the specified conditions of service. The shaft shall be designed such that the steady-state and transient dynamic shaft stresses and coupling torque shall be below the calculated shaft endurance limits and within the allowable cou- pling torque limits throughout the specified conditions operation. Sec. 4.3 General Design: Horizontal Pumps 4.3.1 Casing. 4.3.1.1 Casing shall be designed to produce a smooth flow with gradual changes in velocity. 4.3.1.2 Casing, cover, and gland shall have a corrosion allowance of at least 1/8 in. 4.3.1.3 Suction and discharge nozzles shall be integrally cast into casing. 4.3.1.4 Casing shall be constructed to permit examination and removal of impellers and other rotating elements without disturbing suction and discharge piping connections or the pump driver. Provide jackscrews to facilitate disassembly of the casing. 4.3.1.5 Casing shall include the means to facilitate disassembly without requiring the use of wedges or prying elements, such as provision of tapped holes for jackscrews. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 41. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 21 4.3.1.6 The upper and lower casing halves for between bearings pumps shall be flanged, bolted, and doweled together. The internal wall of the casing halves shall match with not more than 1/16-in. overhang or underhang between the two casing halves. Machined surfaces shall be provided where the upper casing mates with the lower casing. Casings shall be designed and constructed complete with integral supports that are adequate to withstand hydrostatic and dynamic forces generated by the operation of the pump. Design of support connections between the casing and the base shall consider the hydrostatic and dynamic forces between the pump and connecting piping systems based on installation, in accor- dance with the recommendation of ANSI/HI 1.4. Casings shall be provided with lifting lugs or similar removable lift devices such as eye bolts on the upper casing. 4.3.1.7 4.3.1.7. The casing shall be provided with threaded (ASME B1.20.0) drain connections in the bottom casing and threaded (ASME B1.20.1) vent connections in the upper casing and suction chambers. Plugs in each of the connections shall be provided. Minimum connection or outlet size shall be ½-in. (12.7-mm) NPT. 4.3.1.7.1 When enclosed impellers are used, the casing shall be provided with replaceable wear rings, which are held in place by rabbet-fit and locked with screws, pins, anaerobic adhesives, or tack welded at three or more points. 4.3.1.7.2 When installed, wear rings shall be held in place by rabbet-fit and locked with screws, pins, anaerobic adhesives, or tack welded at three or more points. 4.3.1.7.3 Hardness of the casing ring shall be a minimum of 50 BHN greater than the impeller or impeller wear rings (if furnished) unless nongalling metals or galling clearances are used. 4.3.1.7.4 Replaceable wear rings of special gall-resistant materials may be employed that would permit reduced running clearances. For materials with high galling tendencies, such as 300 series stainless steels, 0.005 in. shall be added to the above minimum clearances. High galling tendencies are typically observed in materials that have nickel as a subcomponent. 4.3.1.8 When open or semi-open impellers are used, no casing ring is required. Optionally the use of a wear plate on the suction side of the impeller in the casing would aid in maintaining pump performance. 4.3.2 Shaft. 4.3.2.1 Shaft runout on the stuffing box or seal chamber face and at the impeller shall not exceed 0.002-in. full indication movement. The shaft stiffness Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 42. 22 AWWA E103-15 shalllimit the total deflection under the most severe dynamic conditions over the specified operating range of the pump, with the maximum impeller diameter installed, to 0.002 in. at the primary seal faces or at the stuffing box faces. 4.3.2.2 Shafts and sleeves shall be machined and finished so that the sur- face finish of the shafts or sleeves through the stuffing box and at the rubbing contact-bearing housing seals shall not exceed a roughness of 32-µin. total indica- tor reading (TIR). Sec. 4.4 General Design: Vertical Pumps 4.4.1 Discharge head assembly. 4.4.1.1 Head. Head shall be an iron casting or a steel fabrication. It shall be designed to mount the driver and support the pump column. Design shall con- sider the dynamic forces and vibrations transmitted both by the driver and by the pump. Openings covered by removable corrosion-resistant screens shall be pro- vided for access to any seals, packing, tension devices, or line-shaft couplings. To aid in alignment of the driver or other accessories, such as gears, to line shafting, the head shall be designed with alignment registers with sufficient movement to prevent binding of the device. 4.4.1.2 Discharge elbow. The discharge elbow may be located on the dis- charge head assembly (usual for above-grade discharge) or on the pump column (usual for below-grade discharge). If located on a cast discharge head, it shall be an integral part of the discharge head casting. Fabricated elbows 12 in. (305 mm) and larger shall be of the segmented design, using a minimum of three sections. The discharge end of the elbow shall be flanged or plain end. Plain ends shall have a minimum of three thrust lugs equally placed and of sufficient height to allow installation of a sleeve coupling in accordance with AWWA Manual M11. Note that thrust rods, which are not included in this standard, should be designed to limit axial deflection to 0.005 in. (0.13 mm) when subject to the maximum pressure that occurs in the pipe adjacent to the thrust rods at any time during operation. 4.4.1.3 Sole plate. An opening in the plate shall allow removal of compo- nents below the sole plate. 4.4.1.4 Tension nut. For pumps with an enclosed line shaft, a tubing ten- sion nut shall be installed in the head to allow tension to be placed on the shaft enclosing tube. Provision shall be made for sealing off the thread at the tension nut. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 43. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 23 4.4.1.5 Line-shaft lubrication system. 4.4.1.5.1 Enclosed line-shaft pumps shall be provided with a manually oper- ated sight-feed drip lubricator and an oil reservoir. Food-grade oil approved by the Food and Drug Administration (FDA) shall be used. Pressurized lubrication systems using food-grade oil, water, or grease may be used instead of drip lubricators. 4.4.1.5.2 Open line-shaft pumps shall have fittings to allow prelubricating water to impinge on the line shaft. 4.4.2 Column assembly. 4.4.2.1 Column pipe. Except for the top and bottom column sections on water-lubricated open line-shaft pumps, column pipe shall be furnished in interchangeable sections having a maximum length of 10 ft (3 m). Column pipe over 12 in. (300 mm) in diameter shall be flanged. The length of the top and bottom connections on open line-shaft water-lubricated pumps shall not exceed 10 ft (3 m). 4.4.2.1.1 On enclosed line-shaft columns, 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 fixed with ASME B1.20.1 standard tapered pipe threads. 4.4.2.1.2 On open line-shaft columns, the ends of each section of column pipe shall be faced parallel, and the threads machined or flanged so that the ends will butt against the bearing retainer shoulder to ensure proper alignment and to secure the bearing retainers when assembled. 4.4.2.2 Line shaft. Line shafts shall not be less than 1 in. (25.4 mm) in diameter. Line shaft may be threaded up to 215/16-in. (75-mm) diameter. The thread will be designed to tighten during normal pump operation. Larger than 215/16-in. (75-mm) diameter will be keyed construction. The line shaft shall have a surface finish at bearing locations not to exceed 40 Ra per ASME B46.1. The shaft shall be furnished in interchangeable sections having a length not to exceed 20 ft (6 m) for an enclosed line shaft and 10 ft (3 m) for an open line shaft. They shall be straightened to within 0.005-in. TIR per 10-ft section. For sections less than 10 ft, shafts shall be straightened to 0.002-in. TIR or 0.0005-in. per foot, which- ever is greater. 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. per 6 in. (0.05 mm per 150 mm). The minimum size of the shaft shall be designed for the maximum power defined on the pump performance curve and as determined by the following Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 44. 24 AWWA E103-15 formulafor steady loads of diffuser-type pumps with the shaft in tension because of hydraulic thrust plus suspended weight: S = √ 2F 2 + 321,000P 2 (Eq 9) pD2 nD3 or P = nD3 √ S2 – 2F 2 (Eq 10) 321,000 pD2 Where: S = combined shear stress (psi) F = total axial load acting on the shaft, including hydraulic thrust plus the weight of the shaft and all rotating parts supported by it (lb) D = minimum shaft diameter at the root of the threads or the minimum diameter of any undercut or keyway (in.) P = power transmitted by the shaft (hp) n = rotational speed of the shaft (rpm) Note: in. × 25.4 = mm; lb × 0.454 = kg; psi × 6.895 = kPa; hp × 0.746 = kW; rpm × 0.0167 = rps. The maximum combined shear stress, S, shall not exceed 30 percent of the elastic limit in tension or be more than 18 percent of the ultimate tensile strength of the material used. Additional stress concentration factors due to geometric dis- continuities in the shaft such as keyways, steps, grooves, or radial holes shall be included in the pump manufacturer’s shaft stress calculations. 4.4.2.2.1 When required in the purchase documents, provide line shafting with hardened sleeves under bearings. 4.4.2.3 Shaft couplings. The maximum combined shear stress, determined by the following formula, shall not exceed 20 percent of the elastic limit in ten- sion, nor be more than 12 percent of the ultimate tensile strength of the coupling material used. S = √ 2F 2 + 321,000P 2 (Eq 11) p(D2 – d2) n(D3 – d3) Where: S = combined shear stress (psi) F = total axial load acting on the shaft, including hydraulic thrust plus the weight of the shaft and all rotating parts supported by it (lb) D = outside diameter of the coupling (in.) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 45. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 25 d = inside diameter of the coupling at the root of the threads (in.) P = power transmitted by the shaft (hp) n = rotational speed of the shaft (rpm) Note: in. × 25.4 = mm; lb × 0.454 = kg; psi × 6.895 = kPa; hp × 0.746 = kW; rpm × 0.0167 = rps. 4.4.2.4 Line-shaft bearings. 4.4.2.4.1 For enclosed line shafts, the shaft bearings, which are also inte- gral enclosing tube couplings, shall be spaced not more than 5 ft (1.5 m) 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 lubricant grooves or a separate bypass hole that will read- ily allow the lubricant to flow through and lubricate the bearings below. 4.4.2.4.2 For open line shafts, the shaft bearings shall be designed to be lubricated by the liquid pumped. They shall be mounted in bearing retainers that shall be held in position in the column 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 m). The shaft shall be provided with a noncorroding wearing surface at the loca- tion of each guide bearing. Shafts passing through stuffing boxes shall be stainless steel or fitted with a stainless-steel sleeve. 4.4.2.5 Shaft-enclosing tube. The shaft-enclosing tube shall be made of Schedule 80 steel pipe in interchangeable sections not more than 10 ft (3 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 supported in the column pipe by stabilizers. 4.4.3 Bowl assembly. 4.4.3.1 General. 4.4.3.1.1 Major components shall be designed with shoulders and rabbeted- fits to ensure accurate alignment during repeated disassembly and reassembly. Mat- ing faces of bowls, bells, and cases shall be fully machined to allow the parallelism of the assembled joint to be gauged. Each bowl assembly shall allow the impeller setting to accommodate the shaft stretching or elongation that occurs at and between the shutoff head (zero flow) condition and the maximum runout (maximum flow) condi- tion, throughout the specified operating speed range of the pump. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 46. 26 AWWA E103-15 4.4.3.1.2Bowl, discharge case, and suction case/bell shall be constructed as one-piece castings or fabricated from carbon steel plate. 4.4.3.1.2.1 When enclosed impellers are used and the nominal outside diameter of the intermediate bowl is equal to or greater than 10 in. (250 mm), the intermediate bowls and suction case/bell shall have replaceable wear rings or be designed to be machined to allow future ring installation. 4.4.3.1.2.2 When installed, wear rings shall be held in place by rabbet-fit and locked with screws, pins, anaerobic adhesives, or tack welded at three or more points. 4.4.3.1.2.3 Hardness of the wear rings shall be a minimum of 50 BHN greater than that of the impeller or impeller wear ring (if furnished), unless non- galling metals or galling clearances are used. 4.4.3.1.2.4 Replaceable wear rings of special gall-resistant materials may be employed that would permit reduced running clearances. For materials with high galling tendencies, such as 300 series stainless steels, 0.005-in. shall be added to the above minimum clearances. High galling tendencies are typically observed in materials that have nickel as a subcomponent. 4.4.3.1.2.5 When an open or semi-open impeller is used, no wear ring is required. Optionally the use of a bowl liner on the suction side of the impeller in the bowl would aid in maintaining pump performance. 4.4.3.1.3 Similar bowls and the discharge case shall be designed for the maximum discharge pressure of the bowl assembly. 4.4.3.1.4 Adequate clearance shall be provided at bolt locations to permit the use of socket or box wrenches. 4.4.3.2 Suction bells and suction cases. 4.4.3.2.1 Suction cases shall be used when suction pipes are required for submergence in well applications. Suction bells are preferred for open-pit applications. 4.4.3.2.2 Suction case connections shall be threaded or flanged to accom- modate the connections on the bowl and suction pipe. The suction case inlet con- nection shall be a nominal pipe size, which is larger in diameter than the impeller eye diameter. 4.4.3.2.3 Suction cases and bells shall have a grease-packed CA bearing with a grease fitting and be protected from sand intrusion. Alternative designs (i.e., water-lubricated rubber bearings) may be used if stated in the purchase documents. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 47. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 27 4.4.3.2.4 Suction strainer. Strainers may be cone-type or basket-type and shall have a net inlet area equal to at least three times the impeller inlet area. The maximum opening shall not be more than 75 percent of the maximum opening of the water passage through the bowl or impeller. 4.4.3.3 Intermediate bowls. 4.4.3.3.1 Bowl connections shall be threaded or flanged for bowl sizes 8 in. (200 mm) and smaller. Bowl connections shall be flanged for sizes greater than 8 in. (200 mm). 4.4.3.4 Discharge cases. 4.4.3.4.1 Discharge cases for enclosed line-shaft construction shall have two bearings with bypass ports between them. 4.4.3.4.2 Discharge case connections shall be threaded and/or flanged design to accommodate the connections on the bowl and column pipe. 4.4.3.5 Impellers. 4.4.3.5.1 Impellers shall be enclosed or semi-open configurations. 4.4.3.5.2 Impellers shall be attached to the shaft with either impeller lock collets or keys and thrust-ring retainers. Keys and thrust-ring retainers shall be used exclusively for shaft diameters 2.50 in. (64 mm) and larger. 4.4.3.5.3 Minimum diametrical running clearances of radial wear surfaces shall be 1.5 times the clearance of the bowl bearings employed, 0.002 times the diameter of the wear surface, or 0.010 in. (0.25 mm), whichever is greater. 4.4.3.6 Pump shafts. The shaft shall have a surface finish not to exceed 40 Ra per ASME B46.1. The straightness of the shaft shall be 0.0005 in. (0.012 mm) per foot of length or better. Bowl shaft stress calculations and limitations shall be in accordance with the line-shaft requirements of this standard. 4.4.3.7 Bowl bearings. Bowl bearings shall be cylindrical sleeve type and shall be force-fitted to their larger components (bowls) with ASME B4.1 Class FN1 interference or greater. One bearing shall be located in each bowl and in the suction bell or suction case so that impellers, including the first-stage impellers, are between bearings. The discharge cases may have one or two bearings. Sec. 4.5 Coatings 4.5.1 Ferrous surfaces (except stainless steel) shall receive a factory-applied coat- ing. Other surfaces shall not be coated. 4.5.2 Materials. 4.5.2.1 Bearing housings. Internal surfaces of oil-lubricated bearing housings shall be coated with an oil-soluble rust preventive. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 48. 28 AWWA E103-15 4.5.2.2Machined surfaces. Machined surfaces shall be coated with an NSF/ANSI 61–certified rust preventive. 4.5.2.3 Surfaces not in contact with water. Unless otherwise required in the purchase documents, surfaces not in contact with the water shall be primed with one coat of paint to a minimum dry film thickness of 3 mil. The paint coating shall be compatible with the field top-coatings when the field coatings are identi- fied in the purchase documents. 4.5.2.4 Surfaces in contact with water. Unless otherwise required in the purchase documents, interior surfaces of pump casings shall be coated with mate- rials meeting the requirements of ANSI/AWWA C550 to a minimum dry film thickness of 8 mil. Interior surfaces of vertical pump discharge heads and inte- rior and exterior surfaces of columns shall be coated with materials meeting the requirements of ANSI/AWWA C550 or ANSI/AWWA C210 to a minimum dry film thickness of 8 mil. Products shall be formulated from materials certified as suitable for contact with drinking water by an accredited certification organization in accordance with NSF/ANSI 61 on the date of the purchase document. 4.5.3 Surface preparation. Surfaces to be coated shall be cleaned prior to coating. The cleaning and surface preparation shall meet or exceed the coating manufacturer requirements for the selected coating. As a minimum, the following surface cleaning shall be done: 4.5.3.1 Exterior surfaces. Exterior surfaces not in contact with the water surfaces shall be cleaned to meet the requirements of SSPC-SP6. 4.5.3.2 Other surfaces. Other surfaces shall be cleaned to meet the requirements of SSPC-SP10. 4.5.4 Application. 4.5.4.1 Application of coatings. The application method and conditions for coatings (i.e., surface temperature, humidity restrictions, mixing instructions, pot life, wet and dry film thickness, etc.) shall meet the coating manufacturer’s requirements for the coating being applied. 4.5.4.2 Noncoated surfaces. Surfaces not to be coated or cleaned shall be protected from contamination and damage. Metalwork shall not be welded after coating unless the coating can be inspected and repaired. 4.5.4.3 Coatings shall be applied after hydrostatic testing for leakage and at such time that subsequent welding and assembly procedures will not damage the coating. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 49. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 29 4.5.5 Holiday testing. When required in the purchase documents, the coated surfaces of the pump shall be holiday tested and shall be holiday free in accordance with ANSI/AWWA C550. Sec. 4.6 Vibration Limits Unless otherwise required in the purchase documents, the maximum vibra- tion limits shall be in accordance with ANSI/HI 9.6.4. SECTION 5: VERIFICATION Sec. 5.1 Factory Tests 5.1.1 General. Pumps shall receive a hydrostatic test in accordance with the applicable ANSI/HI standard. 5.1.2 Horizontal pumps. The assembled pump shall be tested in accor- dance with the requirements of ANSI/HI 14.6. 5.1.3 Vertical pumps. The bowl assembly and discharge head shall be tested in accordance with the requirements of ANSI/HI 14.6. Sec. 5.2 Submittals 5.2.1 General. Following are minimum submittal requirements required for each pump prior to delivery. 5.2.2 Anticipated performance data. For horizontal pumps, performance shall be measured from the suction to the discharge. For vertical pumps, perfor- mance shall be measured from the inlet or free water surface to the outlet of the bowl assembly. Data shall include 1. Operating speed. 2. Head versus capacity curve from shutoff to runout. 3. NPSHR curve for the operating range. 4. BHP requirements from shutoff to runout. 5. Specific speed. 6. Suction specific speed. 7. Efficiency from shutoff to runout. 5.2.3 Mechanical data. 1. Maximum allowable casing discharge pressure. 2. Maximum allowable casing suction pressure (for horizontal pumps only). 3. Weight of the pump or bowl assembly. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 50. 30 AWWA E103-15 SECTION6: MARKING, PREPARATION FOR SHIPMENT, AND AFFIDAVIT Sec. 6.1 Marking 6.1.1 Pump nameplate. A corrosion-resistant nameplate containing the following information shall be permanently affixed to the pump: 1. Manufacturer’s name. 2. Year of manufacture. 3. Identifying serial number. 4. Model. 5. Design flow. 6. Design head. 7. Rotational speed. 8. Maximum casing or bowl assembly allowable pressure. Sec. 6.2 Packaging and Shipping 6.2.1 General. 6.2.1.1 The manufacturer shall carefully prepare the pump for shipment to minimize the likelihood of damage during shipment. Cavities shall be drained of water. Equipment shall be properly supported and securely attached to skids. Openings shall be covered in a manner to protect both the opening and interior. 6.2.1.2 The interior of the equipment shall be clean and free from scale, welding spatter, and foreign objects. 6.2.1.3 Prepare equipment for shipment including blocking of the rotor when necessary. Identify blocked rotors by means of corrosion-resistant tags attached with stainless-steel wire. 6.2.1.4 When required in the purchase documents, the shipping prepara- tion shall make the equipment suitable for six months of outdoor storage from the time of shipment, with no disassembly required before operation, except for inspection of bearings and seals. 6.2.1.5 Pack and ship one copy of the manufacturer’s standard unloading, storage, and installation instructions with the equipment. Provide the instructions necessary to preserve the integrity of the storage preparation after the equipment arrives at the jobsite and before startup. 6.2.1.6 Coat exterior machined surfaces with rust preventative. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 51. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 31 6.2.1.7 Provide flanged openings with metal closures at least 3/16-in. thick, with elastomer gaskets and at least four full-diameter bolts. Install closures at place of pump manufacture prior to shipping. For studded openings, use all the nuts needed for the intended service to secure closures. 6.2.1.8 Provide threaded openings with steel caps or solid-shank steel plugs. Do not use nonmetallic (such as plastic) plugs or caps. Install plugs at place of pump manufacture prior to shipping. 6.2.1.9 Clearly identify lifting points and lifting lugs on the equipment or equipment package. Identify the recommended lifting arrangement on boxed equipment. Sec. 6.3 Affidavit of Compliance The purchaser may require an affidavit from the manufacturer that the mate- rial provided complies with applicable requirements of this standard. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 52. This page intentionallyblank. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 53. 33 APPENDIX A Pump CrossSections This appendix is for information only and is not a part of ANSI/AWWA E103. This appendix is not part of this standard but is presented to help the user identify specific part numbers of several types of pumps. Item numbers shown on the drawings that follow correspond to the numbers of the components or parts described in Tables 1–3 of this standard. The drawings contained in this appendix have been provided courtesy of the Hydraulic Institute, 9 Sylvan Way, Parsippany, NJ 07054-3802, www.pumps.org, and are drawn from the following standards: Figures A.1, A.2, A.3, and A.4 are contained in Rotodynamic Centrifugal Pumps for Nomenclature and Definitions, ANSI/HI 1.1-1.2-2000. Figure A.5 is contained in Rotodynamic Vertical Pumps or Radial, Mixed, Axial Flow Types for Nomenclature and Definitions, ANSI/HI 2.1-2.2-2000. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 54. 34 AWWA E103-15 Courtesyof Hydraulic Institute, www.Pumps.org, Parsippany, NY 07054. Figure A.1 Separately coupled, single-stage, inline, flexible coupling pump with overhung impeller Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 55. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 35 Courtesy of Hydraulic Institute, www.Pumps.org, Parsippany, NY 07054. Figure A.2 Separately coupled, single-stage, inline, rigid coupling pump with overhung impeller Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 56. 36 AWWA E103-15 Courtesyof Hydraulic Institute, www.Pumps.org, Parsippany, NY 07054. Figure A.3 Separately coupled, single-stage, frame-mounted pump with overhung impeller Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 57. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 37 Courtesy of Hydraulic Institute, www.Pumps.org, Parsippany, NY 07054. Figure A.4 Separately coupled, single-stage, axial (horizontal) split-case pump with impeller between bearings Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 58. 38 AWWA E103-15 Courtesyof Hydraulic Institute, www.Pumps.org, Parsippany, NY 07054. Figure A.5 Deep-well pumps Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 59. 39 APPENDIX B Field Testingof Pumps This appendix is for information only and is not a part of ANSI/AWWA E103. SECTION B.1: PURPOSE OF FIELD TESTS A field test gives an indication of the performance of a pump when it is oper- ating under actual field conditions. Such a test indicates the operation of the pump assembly, the vibration and noise levels, and the operation of the driver and control equipment. Additionally, on vertical turbine pumps, the test indicates the friction loss in the column pipe and discharge elbow, the bearing losses in the line-shaft assembly, the well or system characteristics, and the air content or sand content of the water. Although these items are important, they are normally judged on a qualitative basis, as compared to what is considered to be good engineering prac- tice, unless specific requirements are provided by the purchase documents. 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. 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 equip- ment employed should be taken into account. Data to help determine the best pos- sible accuracy obtainable with various instruments are included in this standard. 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 con- trolled 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. Field performance tests (in addition to the factory tests) are usually run to ensure that the pump is properly installed and that there are not unanticipated field conditions that impede performance. If there are discrepancies between factory performance and field performance, they need to be understood, evaluated, and if necessary dealt with. Possible explanations may include 1. Incorrect rotation of pump. 2. Incorrect impellers or bowl assemblies may have been shipped. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 60. 40 AWWA E103-15 3.Improper installation: There may be leaks in the column joints (vertical pumps) or blockage of internal components. 4. Motor full load rpm may be lower than anticipated because of bearing binding or electrical problems. 5. Submerged or surface vortices may be forming in the sump. 6. Field equipment, including level and pressure gauges and flowmeters, may be faulty, improperly calibrated, or improperly located. 7. The factory test report may be incorrect. 8. Air may be present in the water or may have been introduced through suction piping, packing, or seals. 9. The piping arrangement may produce a prerotation or nonuniform veloc- ity at the inlet (suction) to the pump. 10. Setting of semi-open impellers on vertical line-shaft pumps may be incorrect. 11. The NPSH margin, equal to NPSHA minus NPSHR, is 5 ft or less, causing cavitation. 12. Ensure balanced voltage is supplied to the motor and within 5 percent of rated motor nameplate voltage if efficiency and load discrepancies are observed. It is desirable to field test new or reconditioned pumps to provide a compari- son for future tests. Thus, pump wear and changing operating conditions may be indicated. Periodic tests should be made using the same procedure and an accurate record kept to give a complete and comparable history and as a guide to determine if an internal inspection or repair is required. SECTION B.2: 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 personnel. If accurate field tests are required, it is necessary to design the complete pump installation with this testing 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 results of field tests. Table B.1 gives an indication of the best possible accuracy that can be expected for the various instruments that may be used for a field test. The values given assume that each instrument is properly installed, is the correct size for the values to be measured, and is used by experienced engineers. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 61. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 41 Table B.1 Limits of accuracy of pump test measuring devices in field use Test Variable Measuring Device Calibrated Limit of Accuracy (%) Capacity Venturi meter ± 0.75 Nozzle ± 1.00 Pitot tube ± 1.50 Orifice ± 1.25 Disc ± 2.00 Piston ± 0.25 Volume or weight tank ± 1.00 Propeller meter ± 4.00 Magnetic meter ± 1.00 Head Electric sounding line ± 0.25 Air line ± 0.50 Liquid manometer (3- to 5-in. deflections) ± 0.75 Liquid manometer (over 5-in. deflections) ± 0.50 Bourdon gauge, 5-in. minimum dial ¼ to ½ full scale ± 1.00 5/8 to ¾ full scale ± 0.75 Over ¾ scale ± 0.50 Power input Watt-hour meter and stopwatch ± 1.50 Portable recording watt meter ± 1.50 Test type precision watt meter ¼ to 1/2 full scale ± 0.75 5/8 to 3/4 full scale ± 0.50 Over 3/4 scale ± 0.25 Clamp-on ammeter ± 4.00 Speed Revolution counter and stopwatch ± 1.25 Hand-held tachometer ± 1.25 Stroboscope ± 1.50 Automatic counter and stopwatch ± 0.50 Voltage Test meter ¼ to ½ full scale ± 1.00 5/8 to ¾ full scale ± 0.75 Over ¾ scale ± 0.50 Rectifier voltmeter ± 5.00 Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 62. 42 AWWA E103-15 Amethod of estimating the probable combined accuracy that will be obtained with the instruments selected is illustrated in the following examples: Example 1: Vertical Turbine Pump Pump conditions: head, 500 ft (152 m); setting, 450 ft (137 m). Instrumenta- tion is shown in the following chart. Line Number (Field Test Report Form)* Instrument Accuracy† (%) 3 Electronic sounding line ± 0.25 7 Bourdon gauge, 5-in. (130-mm) dial, ¾ scale ± 0.75 14 Venturi meter ± 0.75 19 Watt meter, over ¾ scale ± 0.25 22 Hand-held tachometer ± 1.25 16 Voltage meter, over ¾ full scale ± 0.50 *From Figure B.6. †From Table B.1. First, the head accuracy is weighted. Weighted accuracy of the electric sound- ing line is 450/500 × 0.25 = 0.225 percent; weighted accuracy of the bourdon gauge is 50/500 × 0.50 = 0.050 percent; and the sum, or weighted-average head accuracy, is 0.275 percent. The combined accuracy of the efficiency (Ac) is the square root of the quantity of the square of the weighted-average head accuracy, plus the square of the venturi-meter accuracy, plus the square of the watt-meter accuracy. Pump speed and voltage are not necessary in determining efficiency, so the values for the tachometer and the voltage meter are not included under the radical. Ac = √ 0.2752 + 0.752 + 0.252 = √ 0.700 (Eq B.1) = ±0.84 percent Example 2: Vertical Turbine Pump Pump conditions: head, 500 ft (152 m); setting, 450 ft (137 m). Instrumenta- tion is shown in the following chart. Line Number (Field Test Report Form)* Instrument Accuracy† (%) 3 Air line ± 0.50 7 Bourdon gauge, 5-in. (130-mm) dial, ½ scale ± 1.00 14 Pitot tube ± 1.50 19 Watt-hour meter and stopwatch ± 1.50 22 Stroboscope ± 1.50 16 Rectifier voltmeter ± 5.00 *From Figure B.6. †From Table B.1. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 63. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 43 The head accuracy is weighted in the same way as in Example 1. Air line: 450 ft (137 m) × 0.5 percent = 0.45 percent (Eq B.2) 500 ft (152 m) Bourdon gauge: 50 ft (15 m) × 1.0 percent = 0.10 percent (Eq B.3) 500 ft (152 m) Weighted-average head accuracy: 0.45 + 0.10 = 0.55 percent The Ac is the square root of the quantity of the square of the weighted-average head accuracy, plus the square of the pitot-tube accuracy, plus the square of the watt-hour meter accuracy. Ac = √ 0.552 + 1.52 + 1.52 = √ 4.8 (Eq B.4) = ±2.19 percent Example 3: Vertical Turbine Pump Pump conditions: head 500 ft (152 m); setting, 20 ft (6 m). Instrumentation is shown in the following chart. Line Number (Field Test Report Form)* Instrument Accuracy† (%) 3 Air line ± 0.50 7 Bourdon gauge, 5-in. (130-mm) dial, full scale ± 0.75 14 Venturi meter ± 0.75 19 Watt meter over ¾ scale ± 0.25 22 Automatic counter and stopwatch ± 0.50 16 Voltage test meter, full scale ± 0.50 *From Figure B.6. †From Table B.1. Weighted head accuracy is Air line: 20 ft (6 m) × 0.50 percent = 0.02 percent (Eq B.5) 500 ft (152 m) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 64. 44 AWWA E103-15 Bourdongauge: 480 ft (146 m) × 0.50 percent = 0.42 percent (Eq B.6) 500 ft (152 m) Weighted-average head accuracy: 0.02 + 0.48 = 0.50 percent (Eq B.7) The combined accuracy of the efficiency is Ac = √ 0.52 + 0.752 + 0.252 = √ 1.06 (Eq B.8) = ±1.03 percent The recommended procedure for conducting pump acceptance tests is out- lined in Sec. B.5 of this standard. It will be apparent that if the accuracy of all instrumentation is not taken into account, the final result will appear more accurate than it actually is. Individual errors in reading the instruments are not accounted for, so the final combined accuracy may be considered an optimistic figure at best. Example 4: Horizontal Pump Pump conditions: total head, 500 ft (152 m), suction head, 20 ft (6 m), dis- charge head, 520 ft (158 m). Instrumentation is shown in the following chart. Line Number (Field Test Report Form)* Instrument Accuracy† (%) 6 Bourdon gauge, 5-in. (130-mm) dial, ½ scale ± 1.00 7 Bourdon gauge, 5-in. (130-mm) dial, ¾ scale ± 0.75 14 Venturi meter ± 0.75 19 Watt meter over ¾ scale ± 0.25 22 Hand-held tachometer ± 1.25 16 Voltage meter, ¾ full scale ± 0.50 *From Figure B.6. †From Table B.1. First, the head accuracy needs to be weighted between both the suction gauge and discharge gauge. Suction bourdon gauge: 20 ft (6 m) × 1 percent = 0.04 percent (Eq B.9) 520 ft (158 m) Discharge bourdon gauge: 500 ft (152 m) × 0.75 percent = 0.072 percent (Eq B.10) 520 ft (158 m) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 65. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 45 Weighted-average head accuracy: 0.4 + 0.72 = 0.76 percent (Eq B.11) The combined accuracy of the efficiency is Ac = √ (0.76)2 + (0.75)2 + (0.25)2 = ±1.10 percent (Eq B.12) SECTION B.3: DEFINITIONS AND SYMBOLS 1. Datum: The elevation of the 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. 2. Driver efficiency (Ed): The ratio of the driver output to the driver input, expressed in percent. 3. Driver power input: The power input to the driver, expressed in horse- power. 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 kilo- watt input measured at the conduit box on the discharge head divided by 0.746. No satisfactory evaluation of this term for engine-driven pumps is available. 4. Head above datum (ha): The head measured above the datum, expressed in feet (meters) of liquid, plus the velocity head at the point of pressure measurement. 5. Head below datum (hb): The vertical distance, in feet (meters), from the datum to the pumping level. 6. Overall efficiency (E): The ratio of pump output, in horsepower, to motor power input. 7. Pump output, in horsepower (hp) [water hb (WHP)]: Calculated from the following expression: hp = QH × specific gravity of liquid pumped (Eq B.13) 3,960 Where: Q = rate of flow, in gpm H = pump total head, in ft 8. 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. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 66. 46 AWWA E103-15 9.Pump total head (H): The sum of the heads above and below datum (ha + hb). 10. Rate of flow (Q): Flow expressed in gallons per minute (cubic meters per hour). 11. Velocity head (hvs or hvd): The kinetic energy per unit weight of the liquid at the point of measurement, expressed in feet (meters) of liquid. Using the average velocity in feet per second (meters per second) at the point of measurement, it is calculated from the following expression: hv = v2/2g (Eq. B.14) Where: v = velocity, in ft/sec (m/sec) g = 32.2 ft/sec2 (9.81 m/sec2) SECTION B.4: INSTRUMENTATION Sec. B.4.1 General 1. Measuring instrument placement. Figures B.1, B.2, B.3, and B.4 show the placement of instruments and the dimensions for four types of pump installa- tion. Figure B.5 shows piping requirements for orifices, flow nozzles, and venturi tubes. 2. Clamp-on electrical measuring devices. Except for rough checks on motor loading, these devices are deemed not acceptable for pump field tests. Note: Numbers in parentheses refer to item numbers in report form (Fig- ure B.6). Minimum dimensions are the lengths of straight pipe required in Figure B.5 for the particular type of capacity-measuring device used. Sec. B.4.2 Evaluation of Various Methods of Flow Measurement 1. General evaluation. It is impossible to extend flow measurement beyond that corresponding to the system head, which equals the pump total head, unless the head above datum can be lowered for the test. More often 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 the design rate cannot be reached if the method of flow measurement introduces friction head loss, thereby raising the system head. On the one hand, 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 Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 67. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 47 Note: Numbers in parentheses refer to item numbers in report form (Figure B.6). Minimum dimensions are the lengths of straight pipe required in Figure B.5 for the particular type of capacity-measuring device used. Figure B.1 Field-test diagram for line-shaft vertical turbine well pump Note: Numbers in parentheses refer to item numbers in report form (Figure B.6). Minimum dimensions are the lengths of straight pipe required in Figure B.5 for the particular type of capacity-measuring device used. Figure B.2 Field-test diagram for vertical turbine pump for booster service Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 68. 48 AWWA E103-15 Note:Numbers in parentheses refer to item numbers in report form (Figure B.6). Minimum dimensions are the lengths of straight pipe required in Figure B.5 for the particular type of capacity-measuring device used. Figure B.3 Field-test diagram for horizontal split-case pump Note: Numbers in parentheses refer to item numbers in report form (Figure B.6). Minimum dimensions are the lengths of straight pipe required in Figure B.5 for the particular type of capacity-measuring device used. Figure B.4 Field-test diagram for end-suction pump Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 69. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 49 Source: Reprinted from ASME PTC 19.5, Flow Measurement; 4-1959, by permission of the American Society of Mechanical Engineers. All rights reserved. Figure B.5 Pipe requirements for orifice, flow nozzles, and venturi tubes (Figure continued next page) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 70. 50 AWWA E103-15 Source:Reprinted from ASME PTC 19.5, Flow Measurement; 4-1959, by permission of the American Society of Mechanical Engineers. All rights reserved. Figure B.5 Pipe requirements for orifice, flow nozzles, and venturi tubes (continued) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 71. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 51 insertion of a pitot-static tube, on the other hand, can generally be neglected. Ven- turis 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 part of the installation). 2. 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 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 ft (0.6 m). The duration of any test run shall not be less than 1 minute 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. 3. 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 dis- tance 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 (avoiding the use of mercury) or an appropriate differential pressure device. The choice of manometer fluid should produce manometer deflections of at least 6 in. (150 mm). 4. 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 water- proof 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 surface. The elevation of the pumping water level can be determined by the air-line gauge method, by subtracting the calibrated bourdon-tube gauge reading (converted 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 must exceed the head below datum. In the air-line gauge method, the gauge accuracy tolerance must be included (dependent on gauge quality and the portion of the gauge range in use), unless the gauge is calibrated before and after the test. 5. Pitot-static tube. This instrument, available in several forms, correlates velocity head with rate of flow. Velocity head distribution in pipe flow is nonuniform, and for acceptable accuracy, a multiple-point traverse of the pipe cross section is Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 72. 52 AWWA E103-15 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. Pitot-static tubes cannot be presumed to measure average velocity head, unless the velocity profile in the pipe flow under test agrees exactly with that prevail- ing in the pipe in which the instrument was calibrated. Consequently, these devices are not deemed acceptable. Complete details on construction, formulas, and use of acceptable types have been published. 6. Thin-plate square-edged orifice plate. The orifice plate correlates static head difference, measured upstream and downstream, with rate of flow. Data on dimensions, limitations, installation effects, and formulas have been published (Fluid Meters—Their Theory and Application. Report ASME Res. Comm. on Fluid Meters, American Society of Mechanical Engineers, New York). 7. 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. Sec. B.4.3 Other Considerations 1. Power measurement. Although not impossible, it is generally considered impractical 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 direct-drive electric motor, this standard deals with the measurement of electric power only. 2. Portable watt meters. Used with or without portable current and poten- tial transformer(s), portable watt meters are available in varying degrees of preci- sion. They may be used with the manufacturer’s statement of accuracy tolerance if they are in good condition. 3. Pump-speed measurement. Hand-held tachometers are the preferred method of obtaining speed, which is read directly at revolutions per minute or revolutions per second. 4. Watt-hour meters. These devices measure total energy but may be used for measuring power by introducing the time factor in the following formula: driver power input = 4.826 KMR (Eq B.15) t Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 73. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 53 Where: K = disc constant, representing watt-hours per revolution M = product of current and potential transformer ratios (if not used, omit from formula) R = total revolutions of watt-hour meter disc t = time for total revolutions of disc, in seconds The duration of this measurement shall not be less than 1 minute. Commer- cial watt-hour meter power measurements are expected to be within 0.5 percent, unless specifically calibrated and used with a calibration chart. In this case, the stated accuracy of the calibration shall prevail. SECTION B.5: PROCEDURE Sec. B.5.1 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 points for 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 tests must take strict account of the accuracy limitations inherent in field testing. Choice of instru- mentation and installation effects shall be considered to avoid an unrealistic toler- ance requirement. The following points for mechanical performance are also desirable: 1. Acceptable vibration limits specifying point of measurement and maxi- mum total indicator reading in mils (mm). 2. Noise-level limits above specified ambient noise level, also specifying location at which noise level is to be measured. Sec. B.5.2 Instrumentation Choice, installation location, accuracy tolerances, and requirements for cali- bration curves shall be mutually agreed on. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 74. 54 AWWA E103-15 Sec.B.5.3 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. Wear varies within wide limits, so as much preliminary information as is possible to obtain shall be made available to contracting parties, for the purpose of agreement on the time of test or for allow- ances that shall be made for undue wear before the test is run. Sec. B.5.4 Inspection and Preliminary Operation Contracting parties shall make as complete an inspection as possible of the installation to determine compliance with installation requirements and to correct connection of the instrumentation. On satisfactory completion of this require- ment, 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 to the satisfaction of the parties. Any evidence of cascading within the well or the presence of gas or abrasive material shall also be collected at this time. A preliminary check of the test values can then be made for stability of reading, and a final check can be made on any possible malfunction. Sec. B.5.5 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 are not specifically listed in this standard; liquid temperature at pump discharge and pump submergence; and 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 the contracting parties. If several test runs are made at different rates of flow, a performance curve can be drawn and shall become a part of the recorded data. An example of a satisfactory field test report form is shown in Figure B.7. Sec. B.5.6 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, if the instrument locations permit, to record each reading as a matter of mutual agreement. The practice of making simultaneous and instantaneous Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 75. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 55 Expected Accuracy of Field Test Measurement Instrument Accuracy Accuracy Squared Head above datum — Head below datum — Weighted-average head accuracy* Capacity Power Combined accuracy √ (Sum of accuracy squared (from above) *Average is weighted according to the proportion of head above datum and head below datum to total head: (Accuracy of hb) × hb + (Accuracy of ha) × hb = weighted average head accuracy H H Test Readings and Calculations All readings except No. 1 are taken when pumping. No. Symbol Units 1 2 3 1 Head below datum when not pumping ft (m) 2 Drawdown ft (m) 3 hb Head below datum ft (m) 4 Zs Datum to centerline suction gauge ft (m) 5 Zd Datum to centerline discharge gauge ft (m) 6 hgs Suction pressure head reading ft or psi (m or kg/cm2) 7 hgd Discharge pressure head reading ft or psi (m or kg/cm2) 8 Suction pressure head above datam = (4)+(6) ft (m) 9 Discharge pressure head above datum = (5)+(7) ft (m) 10 hvs Velocity head in suction pipe* ft (m) 11 hvd Velocity head in discharge pipe* ft (m) 12 ha Head above datum* = [(11)+(9)] – [(10)+(8)] ft (m) 13 h Total head* = (3)+(12) ft (m) 14 Q Capacity gpm (m3/h) Current Line A amps 15 Current Line B amps Current Line C amps 16 Voltage Phase AB V Voltage Phase BC V Voltage Phase AC V 17 Revolutions of watt-hour meter disc (constant) 18 Time sec 19 Watt meter reading 20 Electrical input* from (17) and (18) or (19) kW 21 Horsepower input* = (16)/0.746 hp 22 Pump speed rpm 23 Pump output = (13) × (14) × sp gr/3,960 hp† 24 Pump efficiency* = (23)/(21) percent 25 Motor efficiency* (source) percent 26 Overall field efficiency* = (24) × (25) percent *Calculated. †Results will be in horsepower only if head measurements are in feet of liquid (hp × 0.746 = kW). Figure B.6 Expected accuracy of field test Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 76. 56 AWWA E103-15 readingsof all instruments must be avoided. For example, the transient response of a bourdon-tube gauge is much faster than that of a manometer. The recommended procedure is to make a continuous observation of at least one minute of the instru- mentation showing rate (or instantaneous values). During the prescribed observation period (if possible), the totaling instruments are read against time to determine rate. With some experience, it is possible to observe rate (instantaneous reading) instru- ments, mentally rejecting random fluctuations and selecting the value that represents that value 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 pitot-static tube, for example) may cause error in the process of obtaining a time- weighted average, if the fluctuation is appreciable. Notwithstanding any skill that may be obtained with experience, it must be recognized that a considerable obser- vational error can still exist. If possible, readings should be repeated and different observers should be employed to ensure complete agreement among the 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 to increase damping of instrument readings, as it is occasionally possible for some of these methods to superimpose a rectifying effect or asymmetrical response on the instrument reading when sub- jected 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. Sec. B.5.7 Adjustment of Field-Test Results Occasionally the pump-driver speeds will deviate slightly from the nominal value on which the pump performance guarantee is based. In such cases, the appli- cation of the following hydraulic affinity relationships should be made to adjust the test values to the design operating speed: Q = Qt(n/nt) (Eq B.16) H = Ht(n/nt)2 (Eq B.17) P = Pt(n/nt)3 (Eq B.18) Where: Q = pump capacity, gpm (m3/hr) t = indicated test values Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 77. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 57 Test Instruments Pump Field-Test Report Discharge Type and Make of Power-Measuring Device Used: Type Capacity-Measuring Device Used: Measured Pipe Inside Diameter at Pressure Tap: Suction Test Date Pump Serial No.: Witnesssed by Test Conducted by: Discharge Size Suction Size: or Length Pipe Size Shaft Size Column: (Valve, Elbow, or Other Fixture) ft Downstream From (Valve, Elbow, or Other Fixture) ft Downstream From Chart No. by Calibration: Date Poor Good Excellent Condition of Pipe Upstream: Measured Diameter of Pipe at Instrument Serial No. Serial No. Type Serial No. Type by Date Chart No. Calibration of Meter No. Potential Transformers Ratio No. Current Transformers Ratio No. Watt Meter Multiplier No. Watt-Hour Meter Disc Constant Make Size Chart No. by Gauge Calibration: Date Specific Gravity Manometer Fluid Serial No. Size Face Make Gauge Speed-Measuring Device: Ammeter: Voltmeter: Discharge Pressure: Chart No. by Gauge Calibration: Date Specific Gravity Manometer Fluid Serial No. Size Face Make Gauge Nominal Voltage Serial No. subm vhs vss Make rpm Rated hp Motor: Serial No. Stages Size Make Frequency Type Location Address Name Power Supply: Pump: Owner: Length Air Line (if used) Suction Pressure: Head Below Datum Measured With (if applicable) Test No. Date Figure B.7 Pump field-test report Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 78. 58 AWWA E103-15 n= design operating speed, rpm nt = test operating speed, rpm H = head, ft (m) P = power, hp (kW) Sec. B.5.8 Evaluation of Accuracy Tolerances Observation errors do not necessarily follow the law of probability. If agree- ment on instrument readings cannot be reached before recording, the arithmetic average shall be used. Instrumentation accuracy tolerances for individual measurements are given in Table B.1. The value of the overall efficiency 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 be assumed that the most probable value of the overall efficiency accuracy tolerance is the square root of the sum of the squares of the individual tolerances. In the computation of test data, the final values obtained from head, capac- ity, driver power input, overall efficiency, and pump speed shall be shown with the appropriate tolerance following each value. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 79. 59 APPENDIX C Suggested DataForm for the Purchase of Horizontal Pumps This appendix is for information only and is not a part of ANSI/AWWA E103. Horizontal Pump Data Sheet 1. Purchaser_______________________________________________________________ 2. Address________________________________________________________________ 3. Installation site___________________________________________________________ 4. Job reference number _________________ Item no. ____________________________ 5. No. required _________________________ Date required ________________________ 6. Prime mover: Electric motor ____________ Engine _____________________________ Other __________________ 7. Prime mover data: Motor: Voltage _____ Frequency ____Phase _______ rpm ______ Engine (type): Gas ________ Gasoline ______Diesel ______ Other _____ Maximum operating rpm _______________________________________ 8. Driver: Horizontal solid-shaft motor drive ________________________________ Horizontal hollow-shaft right-angle gear drive _______________________ Horizontal hollow-shaft belted drive ______________________________ Combination drive ____________________________________________ Speed: Variable (Range) ___________ Constant ______________ Other ______________________________________________________ 9. Bearing lubrication required: Oil ______________________ Other _________________ 10. Discharge nozzle position: Horizontal ________________Vertical ________________ Suction nozzle position: Horizontal ________________Vertical ________________ If below base: Distance from datum to centerline of flange ________ft (m)* 11. Type of pump: Horizontal split case _____________________No. of stages ____________ Radial or vertical split case__________________________________________________ End suction_____________________________________________________________ 12. Type of seal: Packing __________ Single inside mechanical seal ________ Other _____ 13. Coatings:_______________________________________________________________ 14. Other requirements a. ANSI/NSF 61 certification (Y/N) b. ANSI/NSF 372 certification (Y/N) c. Certificate of compliance (Y/N) * See datum definition in Section 3. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 80. 60 AWWA E103-15 15.Design rate of flow_____________________________________________ gpm (m3/hr) 16. Datum evaluation_____________________________ ft (m) (datum centerline of pump) 17. Pumping level below datum at design rate of flow___________________________ ft (m) 18. Total head above datum (static plus system friction) at design rate of flow_________ ft (m) 19. Total pump head at design rate of flow____________________________________ ft (m) 20. Suction Pressure: Minimum __________________________________ ft (m) Maximum __________________________________ ft (m) 21. Operating Range: Minimum total pump head ____________________ ft (m) Maximum total pump head ____________________ ft (m) 22. Other operating conditions_________________________________________________ Description of Installation 23. Type of installation: Horizontal ________________Vertical ________________ 24. Other conditions: ________________________________________________________ 25. Special materials required to resist corrosion and/or erosion: ________________________ Connections and Accessories 26. Discharge flange: ______________________________________ in. (mm), 125-lb ANSI 27. Strainer required: Yes ________ No _________ 28. Lubricant: Oil ________ Water _______ 29. Gauge required: Yes ________ No _________ Pumps are to be furnished in accordance with ANSI/AWWA E103 with the following exceptions: Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 81. 61 APPENDIX D Suggested DataForm for the Purchase of Vertical Line-Shaft Pumps This appendix is for information only and is not a part of ANSI/AWWA E103. Vertical Pump Data Sheet 1. Purchaser_______________________________________________________________ 2. Address________________________________________________________________ 3. Installation site___________________________________________________________ 4. Job reference number _________________ Item no. ____________________________ 5. No. required _________________________ Date required ________________________ 6. Prime mover: Electric motor ____________ Engine _____________________________ Other __________________ 7. Prime mover data: Motor: Voltage _____ Frequency ____Phase _______ rpm ______ Engine (type): Gas ________ Gasoline ______Diesel ______ Other _____ Maximum operating rpm _______________________________________ 8. Driver: Vertical solid-shaft motor drive ___________________________________ Vertical hollow-shaft right-angle gear drive __________________________ Vertical hollow-shaft belted drive _________________________________ Combination drive ____________________________________________ Speed: Variable (Range) ___________ Constant ______________ Other ______________________________________________________ 9. Line-shaft lubrication required: Open ____________________ Enclosed _______________ 10. Line-shaft lubrication required: Oil ______________________ Water __________________ 11. Type of discharge: Surface ____________________ Below Base ______________ If below base: Distance from datum to centerline of flange ________ft (m)* 12. Coatings:_______________________________________________________________ 13. Other requirements a. ANSI/NSF 61 certification (Y/N) b. Certificate of compliance (Y/N) Vertical Pump Operating Conditions 14. Design rate of flow_____________________________________________ gpm (m3/hr) 15. Datum evaluation_____________________________ ft (m) (datum centerline of pump) 16. Pumping level below datum at design rate of flow___________________________ ft (m) * See datum definition in Section 3. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 82. 62 AWWA E103-15 17.Total head above datum (static plus system friction) at design rate of flow_________ ft (m) 18. Total pump head at design rate of flow (line 14 plus line 15) ___________________ ft (m) 19. Operating range: Minimum total pump head ____________________ ft (m) Maximum total pump head ____________________ ft (m) 20. Other operating conditions_________________________________________________ 21. Overall length (datum to inlet of pump suction case)______________________________ 22. Length of suction pipe required______________________________________________ Description of Installation 23. Type of installation: Well ______ Can ______ Sump ______ Other _________________ 24. Minimum inside diameter of well or casing to pump setting ________________ in. (mm) 25. Maximum permissible outside diameter of pump: ________________________ in. (mm) 26. Total depth of well/case or sump________________________________________ ft (m) Note: A well is considered straight if a 20-ft (6-m) long cylinder equal to the maximum permissible outside diameter of the pump will not bind when lowered to a depth equal to the pump setting. 27. Static water level below datum__________________________________________ ft (m) 28. Sand in water: (after 15-minute pumping interval) Concentration—ppm (mg/L)_________ 29. Gas in water: (type, if known) Concentration—ppm (mg/L)________________________ 30. Other conditions:_________________________________________________________ 31. Special materials required to resist corrosion and/or erosion:_________________________ Connections and Accessories 32. Discharge flange: ______________________________________ in. (mm), 125-lb ANSI 33. Companion flange required: Yes _____No ______ __________in. (mm), 125-lb ANSI 34. Column pipe: Threaded sleeve coupling _____ Flanged ______________ 35. Column pipe: Diameter _____________________________ in. (mm) Thickness _____________________________in. (mm) 36. Shaft Size: Diameter _________ in. (mm) Coupling Threaded _____ Keyed ________________ 37. Enclosing tube (if used) nominal pipe size: 38. Strainer required: Yes _____ No ______ 39. Lubricator required: Yes _____ No ______ Voltage ______ Frequency _______ 40. Prelube water tank required: Yes _____ No ______ Capacity ______ Gallons _______ 41. Automatic lubrication controls required: Time delay relay ______Float switch ______ 42. Air line and gauge required: Yes _____ No ______ Pumps are to be furnished in accordance with ASNI/AWWA E103 with the following exceptions: __________________________________________________________________________ __________________________________________________________________________ Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 83. 63 APPENDIX E Engineering Informationand Recommendations This appendix is for information only and is not a part of ANSI/AWWA E103. SECTION E.1: COMMON FOR HORIZONTAL AND VERTICAL PUMPS Sec. E.1.1 Engineering Information Information not currently available. Sec. E.1.2 Recommendations Recommendations not currently available. SECTION E.2: HORIZONTAL PUMPS Sec. E.2.1 Engineering Information Information not currently available. Sec. E.2.2 Recommendations E.2.2.1 Wear ring clearances. Wearing rings are fitted in the casing and sometimes on the impeller. These wear rings provide a close running clearance, to reduce the quantity of liquid leaking from the high-pressure side to the suction side. These rings depend on the liquid in the pump for lubrication. They will even- tually wear so that the clearance becomes greater and more liquid recirculates back to the suction. This rate of wear depends on the character of the liquid pumped. Figure E.1 shows recommended clearances between the fixed and rotating surfaces. These clearances are for dissimilar metals that have a low tendency to gall. However, wear rings that are of the same material must have more clearance than recommended. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 84. 64 AWWA E103-15 SECTIONE.3: VERTICAL PUMPS Sec. E.3.1 Engineering Information E.3.1.1 Diameters and weights of standard steel discharge column pipe are shown in Table E.1. Heavier-weight pipe and lighter-weight pipe are available. E.3.1.2 Friction loss charts. E.3.1.2.1 Discharge head. Figure E.2 can be used as a general design guide. Friction loss will vary depending on the design of the discharge elbow, shaft or enclosing tube size, and column size. E.3.1.2.2 Column. The column friction chart (Figure E.3) can be used as a design guide to determine the loss of head because of column friction. This chart was compiled from head loss data where the flow is between the inside diam- eter of the column pipe and the outside diameter of the shaft-enclosing tube or, in the case of open line-shafting, the outside diameter of the shaft itself. E.3.1.2.3 Mechanical friction. The mechanical friction chart (Figure E.4) can 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 indi- vidual manufacturers may affect the figures slightly. Added horsepower will also be Figure E.1 Horizontal pump nominal impeller-ring diametrical clearance (1 in. = 25.4 mm) Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 85. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 65 Table E.1 Diameters and weights of standard discharge column pipe sizes Nominal Size (ID) OD Weight (Plain Ends) in. (mm) in. (mm) lb/ft (kg/m) 2½ (65) 2.875 (73.0) 5.79 (8.62) 3 (75) 3.500 (88.9) 7.58 (11.28) 4 (100) 4.500 (114.3) 10.79 (16.06) 5 (125) 5.563 (141.3) 14.62 (21.76) 6 (150) 6.625 (168.3) 18.97 (28.23) 8 (200) 8.625 (219.1) 24.70 (36.76) 10 (255) 10.750 (273.0) 34.24 (50.96) 12 (305) 12.750 (323.8) 43.77 (65.14) 14* (355) 14.000 (355.6) 54.57 (81.21) 16* (405) 16.000 (406.4) 62.58 (93.13) * OD Conversion factors: in. × 25.40 mm ft × 0.3048 = m Figure E.2 Friction loss in discharge heads Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 86. 66 AWWA E103-15 requiredto overcome the mechanical friction at the shaft seal (packing or mechani- cal) and in the motor thrust bearing. The values of these losses can be obtained from the pump manufacturer. Sec. E.3.2 Recommendations E.3.2.1 Drivers. E.3.2.1.1 Rotation. Shaft rotation may be counterclockwise or clockwise when viewed from the driven end. Note: Friction loss determined by laboratory tests on new pipe (C = 140). Diagonals are labeled to show nominal diameters (in inches) of outer pipe column and inner shaft- enclosing tube, or if an open shaft, the shaft itself. For the outer pipe columns, the calculations used in constructing the chart were based on inside diameters, which are close to the nominal sizes for pipe up to and including 12 in. (for example, 10 in. Sch 30 pipe = 101/5 in. ID). For pipe sizes in 12 in. and larger, the diameters shown are equivalent to the outside diameter of pipe with 3/8-in. wall thickness (for example, 16 in. = 151/4 in. ID). For the inner columns (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 × 23/8, and “16 × 3” is 151/4 × 31/2. Conversion factors: 1 ft = 0.30 m 1 in. = 25.40 mm Figure E.3 Friction loss for standard pipe column Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 87. HORIZONTAL AND VERTICALLINE-SHAFT PUMPS 67 E.3.2.1.2 Thrust bearing. Provide a thrust bearing of ample capacity to carry the weight of rotating parts plus the hydraulic thrust at operating conditions. For antifriction bearings, the bearings shall be of such capacity that the AFBMA (Anti-Friction Bearing Manufacturers Association, 1101 Connecticut Avenue, NW, Suite 70, Washington, DC 20036) calculated rating life (L10) should be based on the duty cycle but not less than 8,800 hours when operating at the design point. If the Note: The chart shows values for enclosed shaft with oil or water lubrication and drip feed, or for open shaft with water lubrication. For enclosed shaft with flooded tube, read two times the value of friction shown on the chart. Figure E.4 Mechanical friction in line shafts Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 88. 68 AWWA E103-15 designand operating conditions are such that upthrust can occur, provisions should be made to accommodate the upthrust. Minimum upthrust capacity of roller bear- ings should be equal to one quarter of the downthrust capacity. E.3.2.1.3 Ratchets. It is recommended that the purchaser evaluate reverse speed operating conditions (associated with pump shutdown) with the pump manu- facturer and specify the maximum overspeed in reverse for the pump and driver including additional requirements to protect line-shaft bearings in the purchase documents. If reverse rotation of the pump is not permitted, the purchaser should require a nonreverse ratchet be provided in the driver. E.3.2.1.4 Steady bushing. For vertical hollow-shaft motors used on pumps equipped with mechanical seals and also for pumps with packed stuffing boxes operating at speeds greater than 2,900 rpm, a steady bushing should be provided. E.3.2.2 Prelubrication. Prelubrication of line-shaft bearings for water- lubricated open line-shaft pumps having settings greater than 50 ft (15 m) should be provided. Bearing should be thoroughly wetted before pump startup. E.3.2.3 Seals. E.3.2.3.1 Mechanical seals. Mechanical seals should be considered for pressurized can pumps to avoid seal leakage during periods in which the pump is not operating. E.3.2.4 Column pipe corrosion. It may be advisable not to apply a coat- ing to threaded column pipe exposed to waters having high conductivity levels. The higher electrical potentials in this water are attracted to uncoated surfaces to concen- trate corrosion. Uncoated pipe provides a much larger surface area for the electrical potentials to dissipate, and eliminates the concentration at the uncoated threaded surfaces of the column pipe joints. Most product-lubricated pumps have bronze bear- ing retainers, which are located in the center of the threaded pipe coupling where the threaded column pipe ends are located. The bronze alloy is more cathodic than the adjoining sacrificial steel-column pipe. This results in electrolysis at the interface of the two dissimilar materials, and accelerated corrosion of the steel pipe threads. Dissimilar materials also add to the rate of corrosion when elevated conductivity and higher concentrations of chlorides in the water exist. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 89. This page intentionallyblank. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 90. This page intentionallyblank. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 91. This page intentionallyblank. Copyright © 2016 American Water Works Association. All Rights Reserved. ©
- 92. 6666 West QuincyAvenue Denver, CO 80235-3098 T 800.926.7337 www.awwa.org 1P–2M 45103-2015 (03/16) IW Printed on Recycled Paper Dedicated to the world’s most important resource, AWWA sets the standard for water knowledge, management, and informed public policy. AWWA members provide solutions to improve public health, protect the environment, strengthen the economy, and enhance our quality of life. Copyright © 2016 American Water Works Association. All Rights Reserved. ©