data for pump users spp pumps

Contents 4

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ContaCts

sales and administration 1420 Lakeview Arlington Business Park Theale, Reading Berkshire RG7 4SA Tel: +44 (0) 118 932 3123 Fax: +44 (0) 118 932 3302

Manufacturing Centre Crucible Close Mushet Industrial Park Coleford Gloucestershire GL16 8PS Email: [email protected] Tel: +44(0)1594 832701 Fax: +44(0)1594 836300

UK service Centre Contact Directory

Western service Centre Tufthorn Avenue, Coleford Gloucestershire England GL16 8PJ Email: [email protected] Tel: +44 (0) 1594 832701 Fax: +44 (0) 1594 810043

north West service Centre Metrology House Dukinfield Road Hyde England SK14 4PD Email: [email protected] Tel: +44 (0) 161 366 7309 Fax: +44 (0) 161 366 8849

scottish service Centre 137 Deerdykes View Cumbernauld G68 9HN Email: [email protected] Tel: +44 (0) 1236 455035 Fax: +44 (0) 1236 455036

southern service Centre Unit 1 Stanstead Road Boyatt Wood Industrial Estate Eastleigh, Hampshire England SO50 4RZ Email: [email protected] Tel: +44 (0) 2380 616004 Fax: +44 (0) 2380 614522

northern Ireland service Centre Unit 2 Oak Bank Channel Commercial Park Queens Road, Queens Island Belfast Northern Ireland BT3 9DT Email: [email protected] Tel: +44 (0) 2890 469802 Fax: +44 (0) 2890 466152

For Service support outside of office hours please call +44 (0) 8443 759662

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France SPP Pumps 2 rue du Chateau d’eau 95450 US France Email: [email protected] Tel: +33 (0) 1 30 27 96 96 Fax: +33 (0) 1 34 66 07 33

north and south america 2905 Pacific Drive Norcross GA 30071 U.S.A. Email: [email protected] Tel: +1(770) 409 3280 Fax: +1(770) 409 3290 www.spppumpsusa.com

Middle East SPP Pumps Limited (Middle East) P O Box 61491, Jebel Ali Dubai United Arab Emirates Email: [email protected] Tel: +971 (0) 4 8838 733 Fax: +971 (0) 4 8838 735

asia SPP Pumps Limited (Asia) 152 Beach Road Gateway East #05 - 01 to 04 Singapore 189721 Email: [email protected] Tel: +(65) 6576 5725 Fax: +(65) 6576 5701

south africa SPP Pumps (South Africa) Cnr Horne St & Brine Ave Chloorkop Ext 23 Kemptonpark Gauteng R.S.A 1619 Email: [email protected] Tel: +27(0)11 393 7177 / 71792

Italy SPP Italy Via Watt, 13/A 20143 Milano Email: [email protected] Tel: +(0039) 02 58111782 Fax: +(0039) 02 58111782 Mobile: +(0039) 346 3204457

Poland Email: [email protected]

netherlands SPP Pumps Limited Klerkenveld 7 NL-4704 SV Roosendaal The Netherlands E-mail: [email protected] Tel: +31(0)165743053

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Czech Republic Email: [email protected] Tel: +420 775 656 110

Russia Email: [email protected] Tel: +420 775 656 110

Parent Company Kirloskar Brothers Limited “YAMUNA” Plot No 98 (3-17), Baner 411045 Pune India Tel: +91 20 2721 4444 www.kirloskarpumps.com

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UsEFUl WEbsItEs

tRaDE assoCIatIons:British Pump Manufacturers Association (BPMA) www.bpma.org.uk

Construction Equipment Association (CEA) www.coneq.org.uk

Fire Protection Association (FPA) www.thefpa.co.uk

British Automatic Sprinkler Association www.basa.org.uk

European Fire Sprinkler Network www.eurosprinkler.org

Energy Industries Council www.the-eic.com

Pump Centre www.pumpcentre.com

REgUlatoRy aUthoRItIEs:Factory Mutual (FM) www.fmglobal.com

Underwriters Laboratories www.ul.com

Loss Prevention Certification Board www.brecertification.co.uk

National Fire Protection Association www.nfpa.org

Pump Distributors Association www.the-pda.com

Pumps-Directory www.pumps-directory.com

UsefUl Web

sitesUsefUl W

bsites

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ContEnts

Introduction to sPP .................................8 -15

Manufacturing .................................................. 9 Test Facility ....................................................... 9 SPP Divisions .................................................. 10 SPP International ............................................ 15 Fire Protection and Approval Standards ........... 16

Pump specification & operation ..... 17 – 42

Data Required When Buying Pumps ................ 19 Dimensions of Cast Iron Flanges to BS EN 109221 ................................................ 21 Dimensions of Cast Iron Flanges to ASME/ANSI B16.1 ........................................... 24 Dimensions of Steel Flanges to ASME/ANSI B16.5 ........................................... 26 Pump Installation ............................................ 28 Pump Operation .............................................. 28 Faults and Remedial Action ............................. 29 Vibration Tolerance ......................................... 31 Condition Monitoring ....................................... 33 Flow Estimation Methods ................................ 34 Application Do’s and Don’ts ............................ 39

hydraulic Design Data ........................ 43 – 68

Pressure (bar) vs Head (m of Water) ................ 44 Calculation of Head for Pump Selection ........... 46 Autoprime Pumping Terms .............................. 49 Friction Loss for Water Hazen-Williams Formula, C=140) .................... 51 Resistance in Fittings ...................................... 54 Quantities Passed by Pipes at different Velocities .......................................... 55 Recommended Maximum Flow through Valves (l/s) ......................................... 55 Water Discharged by Round Spray Holes in thin walled Pipes Under Different Pressures ........... 56 Net Positive Suction Head (NPSH) .................... 57 Maximum Suction Lift with Barometric Pressure at Different Altitudes ....................................... 59 Liquid Viscosity and its Effect on Pump Performance ......................................... 60 Approximate Viscosity Conversion Schedule .... 62 Test Tolerances and Different Standards ......... 64

Velocity head Correction ................... 69 – 78

Electrical Design Data ........................ 79 – 84

Average Efficiencies and Power Factors of Electric Motors ............................................ 80 Approximate Full Load Speeds (RPM) of AC Motors ................................................... 82 Starting AC Motors .......................................... 83

Whole life Cost ..................................... 85 – 90

Whole Life Cost Principles and Pump Design ... 86 Features of a Low Life-Cycle cost centrifugal pumps ........................................... 88

Energy ..................................................... 91 – 94

Conversion Factors ............................ 95 – 105 Conversion Factor Tables ................................ 96 Vacuum Technical Data ................................. 100 Product / Application Charts .......................... 101

notes .............................................................. 106

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“For Where it Really Matters”

For more than 130 years SPP Pumps has been a leading manufacturer of centrifugal pumps and associated systems. A global principal in design, supply and servicing of pumps, pump packages and equipment for a wide range of applications and industry sectors.

SPP pumps and systems are installed on all continents providing valuable high integrity services for diverse industries, such as oil and gas production, water and waste water treatment, power generation, construction, mines and for large industrial plants.

Major applications include water treatment & supply, sewage & waste water treatment, fire protection, and mobile pumps for rental sectors, for which our low life cost and environmental considerations are fundamental design priorities.

Assessed toOHSAS 18001:2007

LPCB reg. no 111

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ManUFaCtURIngSPP requires the highest standards of manufacturing excellence from its facilities around the world. This is crucial to the on-going growth and development of the company. At the main manufacturing facility located in the UK, SPP set the highest standards attainable in the industry for quality and reliability.

SPP distinguishes its product split between pre-engineered standard products and fully customised equipment engineered and packaged to order. The extensive manufacturing and testing capabilities reflect this wide and diverse product range.

To ensure efficient use of production resources, an ERP manufacturing planning system is utilised. Assembly areas are segregated into the main product groups; standard pumps, industrial fire pumps, contractors pumps and engineered products. The machine shop is planned in cell layout with individual cells specialising in types, or ranges of components. CNC machines are linked by a DNC system allowing programming to be carried out on the machine or offline.

Lean manufacturing principles ensure that SPP are always focused on continuous improvement to support their ‘Right First Time’ philosophy. Customers are always welcome to visit the facility, either during manufacturing or when equipment is on test.

tEst FaCIlItyTesting, including witness testing, of all SPP’s range of pumps is performed at SPP’s own extensive in-house test facility. The main test area has a 1.4 million litre test tank with a depth of 6 metres. It can test pressures up to 50 bar, flows up to 2000 l/s and powers up to 800kW at 6.6kV, 400kW at 415V and 400kW at 60Hz. Generators can be used for higher powers or voltages.

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Pumps for water supply, water/waste water treatment, industrial processes and general pumping service.

SPP has an extensive range of products suitable for a variety of applications. From end suction DIN24255 (EN 733:1995) through to vertical turbine, split case and sewage pumps, SPP has reliable and well proven products to offer.

lowest life Cycle Cost series

SPP’s recognises the increasing emphasis on whole life cost when evaluating pumping schemes, for the twenty-first century. This has lead to the development of their Lowest Life-Cycle Cost Series of split case, vertical turbine, dry well sewage pumps and solides diverters.

SPP is the world’s leading specialist manufacturer of quality fire protection pump packages. Unrivalled experience in design and manufacture together with advanced testing and accreditation ensures the utmost in equipment reliability.

SPP fire pumps comply with the demanding requirements of the LPCB, FM and UL approval standards and meet all the requirements of NFPA 20.

WatER

FIRE

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SPP is a world leader in the design and manufacture of pumping equipment for both onshore and offshore applications. In-house expertise ensures compliance with all applicable specifications and regulations. SPP has also established quality assurance and document control business systems allied to the needs of the major oil and gas contractors and end users.

SPP is the packager as well as the pump manufacturer and takes full unit responsibility for the complete scope of supply.

The SPP Autoprime range is a proven, versatile and comprehensive product range suitable for use in a variety of applications worldwide. The Autoprime pumps are primarily sold to rental organisations, contractors, utility companies, open cast mining companies and municipalities providing a durable solution. Continual investment in market-led research and development ensure that the products are designed to meet market requirements and legislation, providing significant benefits and solutions to owners and users alike.

oIl & gas

DEWatERIng

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stanDaRD PRoDUCts

The SPP standard pump product range has been expertly designed to enable you to fit them to any of your existing DIN Standard Pump Applications. SPP’s excellent modular pump design allows interchangeability across the range and with the ability to use standard shaft motors, gives much more flexibility in terms of maintenance, stock holding and material options. SPP Standard pumps can also be used for a variety of new pump application needs.

InDUstRy

This is the largest market sector spanning chemical, pharmaceutical, power and general industry, including manufacturing processes such as foundries, rolling mills, boiler houses and water reclamation.

The main pumping equipment is largely electrically driven such as:

• End suction / SH & SHL non clog along with current distribution offering

• KPD for chemical process

• Split case units

• RKB multistage

• Vertical turbines

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tRansFoRMER oIl PUMPs

SPP’s transformer oil pump range is designed and manufactured to the highest quality standards. SPP have been producing transformer oil pumps for more than sixty years. Life expectancy in many cases has exceeded forty years. Applications include oil circulation in the following: power transmission, distribution and electric traction locomotive transformers.

EnERgy

Through the use of proven systems and techniques, the Energy Division offers a complete energy saving package that can be applied equally to new projects and existing installations. The new division offers the following services: Energy Audits, Customer Training, Energy Management, Surveys/reports/analysis and recommendations. By monitoring and/or analysing the actual requirement of the installation and comparing this with the specifications of the equipment installed, SPP can make recommendations that can reduce running costs (eg: power requirements), minimise maintenance costs (eg: parts/servicing and downtime) and improve plant reliability (eg: upgraded material specifications).

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EngInEERIng sERVICEs

At SPP we are committed to providing the very best in customer support. We have built our reputation by providing a fast, cost effective service whilst maintaining continually high standards of workmanship and quality. With strategically located service centres in the UK and around the world, help is never far away. Each service centre is fully equipped to offer a comprehensive range of equipment repair and refurbishment techniques. Our support is available 24 hours a day, and is only ever a phone call away.

SPP supports our customers around the globe through our extensive network of field service engineers. SPP field service engineers have thousands of hours of experience, backed by intensive product and applications training. Whatever your technical support requirement, we can help you get the best performance from our equipment in your application. Field service engineers can provide:

• Equipment installation and commissioning

• Preventative maintenance

• Equipment repair and upgrades

• Product training

On SPP and other manufacturers’ pumps.

SPP are proud to be a chosen partner by SKF Bearings in the UK. This has led to all SPP service centres being the only UK approved SKF Certified Rebuilder of pumps. SPP also works with SKF globally and is the first port of call for SKF customers needing pump repairs and services.

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sPP IntERnatIonal

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FIRE PRotECtIon aPPRoVal stanDaRDsSPP has one of the widest ranges of approved and listed equipment in the world complying with the demanding requirements of the UL and FM approval standards and meeting all the requirements of NFPA 20. Along with these approvals, SPP’s fire products are also approved for use in many other markets such as Europe, The Far East, The Middle East and Africa. Although many pump companies can offer equipment ‘designed to’ the various locally applicable fire rules and regulations, only a very select few have had their pumps subjected to the stringent performance and reliability tests of specialist fire approval laboratories.

Being the first to achieve fire pump approval and listing by the internationally recognised Loss Prevention Certification Board the company today has more pumps approved by the LPCB than any other manufacturer.

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PUMP sPECIFICatIon anD oPERatIon

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sECtIon 1

Data REQUIRED WhEn bUyIng PUMPs

Fundamentalsnumber required.

nature of service.

Whether continuous or intermittent.

PerformanceCapacity (State whether total or per unit).

total head or pressure to be developed.

suction lift (including friction), inlet pressure or head, or nPsh available.

(State range of any variation in above items. Otherwise, send sketch or give full details of lifts and pipe runs including lengths, bores, materials and class of pipes and number and nature of bends, valves etc.).

Pumped Mediumnature of liquid (if other than cold, clean water).

Values or ranges of actual pumping temperature with corresponding specific gravities, viscosities (if greater than for water) and vapour pressures.

Any corrosive and/or abrasive properties.

Nature, proportion and maximum size of any solids content.

Drivernature of driver.

If driver to be supplied, give full specification.

If electric motor, state electricity supply details, any speed restriction.

Whether lining-up and connecting free issue driver required.

Details of starting equipment and/or other accessories required

system of control if automatic.


seCtiON 1

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other DataIf required to run in parallel with other units.

Is it to be self-priming with suction lift.

Pump type and arrangement.

Fixed or portable.

Horizontal or vertical shaft.

Whether close-coupled, dry well, wet well or borehole (if vertical).

Borehole diameter or any other space restrictions.

If baseplate and coupling required.

Constructional / material specification required.

Site conditions:

If altitude above 150m.

If ambient temperature above 30º C.

If to work outdoors.

Type of drive:

Direct or indirect (i.e. coupling, gearbox or V belt).

Direction of rotation (if restricted).

Official tests/inspection, packing and shipping requirements.

Tender receipt/material despatch date required.

Any other significant information.

Items printed in bold are minimum requirements for quotation of any standard horizontal pump. All other items, so far as they apply, are necessary for the correct execution of all orders and quotations other than standard horizontal pumps.

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sECtIon 2

DIMEnsIons oF Cast IRon FlangEs to bs En 1092Pumps and Fittings

noM.

DIa.

FlangE RaIsED FaCE bolts DRIllIng nECK

D b d4 Fmax DIa. no d2 k d3 r

10 75 12 33 2 M10 4 11 50 20 315 80 12 38 2 M10 4 11 55 26 320 90 14 48 2 M10 4 11 65 34 425 100 14 58 3 M10 4 11 75 44 4 32 120 16 69 3 M12 4 14 90 54 5 40 130 16 78 3 M12 4 14 100 64 5 50 140 16 88 3 M12 4 14 110 74 5 65 160 16 108 3 M12 4 14 130 94 6 80 190 18 128 3 M16 4 19 150 110 6 100 210 18 144 3 M16 4 19 170 130 6 125 240 20 174 3 M16 8 19 200 160 6 150 265 20 199 3 M16 8 19 225 182 8 200 320 22 254 3 M16 8 19 280 238 8 250 375 24 309 3 M16 12 19 335 284 10 300 440 24 363 4 M20 12 23 395 342 10 350 490 24 415 4 M20 12 23 445 392 10 400 540 24 463 4 M20 16 23 495 442 10 450 595 24 518 4 M20 16 23 550 494 12 500 645 24 568 4 M20 20 23 600 544 12 600 755 24 667 5 M24 20 28 705 642 12 700 860 24 772 5 M24 24 28 810 746 12 800 975 24 878 5 M27 24 31 920 850 12 900 1075 24 978 5 M27 24 31 1020 950 12 1000 1175 24 1078 5 M27 28 31 1120 1050 12

BS EN 1092 TABLE PN6

notE - All dimensions listed below are in millimetres

seCtiON 2


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noM.

DIa.


D b d4 Fmx DIa. no d2 k d3 r

notE: FoR noMInal sIZEs 10 - 150 UsE Pn16 tablE200 340 26 266 3 M20 8 23 295 246 8 250 395 28 319 3 M20 12 23 350 298 10 300 445 28 370 4 M20 12 23 400 348 10 350 505 30 429 4 M20 16 23 460 408 10 400 565 32 480 4 M24 16 28 515 456 10 450 615 32 530 4 M24 20 28 565 502 12 500 670 34 582 4 M24 20 28 620 559 12 600 780 36 682 5 M27 20 31 725 658 12 700 895 40 794 5 M27 24 31 840 772 12 800 1015 44 901 5 M30 24 34 950 876 12 900 1115 46 1001 5 M30 28 34 1050 976 12 1000 1230 50 1112 5 M33 28 37 1160 1080 12 1200 1455 56 1328 5 M36 32 41 1380 1292 12 1400 1675 62 1530 5 M39 36 44 1590 1496 12 1600 1915 68 1750 5 M45 40 50 1820 1712 12 1800 2115 70 1950 5 M45 44 50 2020 1910 15 2000 2325 74 2150 5 M45 48 50 2230 2120 15 2200 2550 78 - - M52 52 56 2440 2320 20


noM.

DIa.



10 90 14 41 2 M12 4 14 60 28 315 95 14 46 2 M12 4 14 65 32 320 105 16 56 2 M12 4 14 75 40 425 115 16 65 3 M12 4 14 85 50 4 32 140 18 76 3 M16 4 19 100 60 5 40 150 18 84 3 M16 4 19 110 70 5 50 165 20 99 3 M16 4 19 125 84 5 65 185 20 118 3 M16 4 19 145 104 6 80 200 22 132 3 M16 8 19 160 120 6 100 220 24 156 3 M16 8 19 180 140 6 125 250 26 186 3 M16 8 19 210 170 6 150 285 26 211 3 M20 8 23 240 190 8 200 340 30 266 3 M20 12 23 295 246 8 250 405 32 319 3 M24 12 28 355 296 10 300 460 32 370 4 M24 12 28 410 350 10 350 520 36 429 4 M24 16 28 470 410 10 400 580 38 480 4 M27 16 31 525 458 10 450 640 40 548 4 M27 20 31 585 516 12 500 715 42 609 4 M30 20 34 650 576 12 600 840 48 720 5 M33 20 37 770 690 12 700 910 54 794 5 M33 24 37 840 760 12 800 1025 58 901 5 M36 24 41 950 862 12

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noM.

DIa.



10 90 16 41 2 M12 4 14 60 28 315 95 16 46 2 M12 4 14 65 32 320 105 18 56 2 M12 4 14 75 40 425 115 18 65 3 M12 4 14 85 50 4 32 140 20 76 3 M16 4 19 100 60 5 40 150 20 84 3 M16 4 19 110 70 5 50 165 22 99 3 M16 4 19 125 84 5 65 185 24 118 3 M16 8 19 145 104 6 80 200 26 132 3 M16 8 19 160 120 6 100 235 28 156 3 M20 8 23 190 142 6 125 270 30 186 3 M24 8 28 220 162 6 150 300 34 211 3 M24 8 28 250 192 8 200 360 34 274 3 M24 12 28 310 252 8 250 425 36 330 3 M27 12 31 370 304 10 300 485 40 389 4 M27 16 31 430 364 10 350 555 44 448 4 M30 16 34 490 418 10 400 620 48 403 4 M33 16 37 550 472 10 450 670 50 548 4 M33 20 37 600 520 12 500 730 52 609 4 M33 20 37 660 580 12 600 845 56 720 5 M36 20 41 770 684 12 700 960 56 820 5 M39 24 44 875 780 12 800 1085 56 928 5 M45 24 50 990 882 12

seCtiON 2



noM.

DIa.



10 90 16 41 2 M12 4 14 60 28 315 95 16 46 2 M12 4 14 65 32 320 105 18 56 2 M12 4 14 75 40 425 115 18 65 3 M12 4 14 85 50 4 32 140 20 76 3 M16 4 19 100 60 5 40 150 20 84 3 M16 4 19 110 70 5 50 165 22 99 3 M16 4 19 125 84 5 65 185 24 118 3 M16 8 19 145 104 6 80 200 26 132 3 M16 8 19 160 120 6 100 235 28 156 3 M20 8 23 190 142 6 125 270 30 186 3 M24 8 28 220 162 6 150 300 34 211 3 M24 8 28 250 192 8 200 375 40 284 3 M27 12 31 320 254 8 250 450 46 345 3 M30 12 34 385 312 10 300 515 50 409 4 M30 16 34 450 378 10 350 580 54 465 4 M33 16 37 510 432 10 400 660 62 535 4 M36 16 41 585 498 10 450 685 62 560 4 M36 20 41 610 522 12500 755 62 615 4 M39 20 44 670 576 12

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asME/ansI b16.1 – 125lb – RATING – CAST IRON 250lb – RATING – CAST IRON

notE - All dimensions listed below are in inches

DIMEnsIons oF Cast IRon FlangEs to asME/ansI b16.1


noM.

DIa.



40 170 28 84 3 M20 4 23 125 77 5 50 180 28 99 3 M20 4 23 135 87 5 65 205 28 118 3 M20 8 23 160 112 6 80 215 31 132 3 M20 8 23 170 122 6 100 250 33 156 3 M24 8 28 200 142 6 125 295 37 184 3 M27 8 31 240 174 6 150 345 39 211 3 M30 8 34 280 208 8 200 415 46 284 3 M33 12 37 345 267 8 250 470 50 345 3 M33 12 37 400 322 10 300 530 57 409 4 M33 16 37 460 382 10 350 600 61 465 4 M36 16 41 525 438 10 400 670 65 535 4 M39 16 44 585 490 10 200 360 34 274 3 M24 12 28 310 252 8 250 425 36 330 3 M27 12 31 370 304 10 300 485 40 389 4 M27 16 31 430 364 10 350 555 44 448 4 M30 16 34 490 418 10 400 620 48 403 4 M33 16 37 550 472 10

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asME/ansI b16.1 – 250lb RATING – CAST IRON

noM.

DIa.

FlangE bolts DRIllIng sPotFaCE

DIaMEtER

hUb

D b DIa. no d2 k d3 r

1 4.88 0.69 0.62 4 0.75 3.50 1.25 2.06 0.131 1/4 5.25 0.75 0.62 4 0.75 3.88 1.25 2.50 0.131 1/2 6.12 0.81 0.75 4 0.88 4.50 1.50 2.75 0.13

2 6.50 0.88 0.62 8 0.75 5.00 1.25 3.31 0.252 1/2 7.50 1.00 0.75 8 0.88 5.88 1.50 3.94 0.25

3 8.25 1.12 0.75 8 0.88 6.62 1.50 4.62 0.253 1/2 9.00 1.19 0.75 8 0.88 7.25 1.50 5.25 0.25

4 10.00 1.25 0.75 8 0.88 7.88 1.50 5.75 0.255 11.00 1.38 0.75 8 0.88 9.25 1.50 7.00 0.256 12.50 1.44 0.75 12 0.88 10.62 1.50 8.12 0.258 15.00 1.62 0.88 12 1.00 13.00 1.63 10.25 0.2510 17.50 1.88 1.00 16 1.12 15.25 1.88 12.62 0.2512 20.50 2.00 1.12 16 1.25 17.75 2.13 14.75 0.2514 23.00 2.12 1.12 20 1.25 20.25 2.13 16.25 0.2516 25.50 2.25 1.25 20 1.38 22.50 2.25 18.38 0.2518 28.00 2.38 1.25 24 1.38 24.75 2.25 20.75 0.2520 30.50 2.50 1.25 24 1.38 27.00 2.25 23.00 0.3824 36.00 2.75 1.50 24 1.62 32.00 2.75 27.25 0.3830 43.00 3.00 1.75 28 2.00 39.25 34.00 34.00 0.38

seCtiON 2


ASME/ANSI B16.1 – 125lb RATING – CAST IRON

noM.

DIa.

FlangE bolts DRIllIng sPotFaCE

DIaMEtER

hUb

D b DIa. no d2 k d3 r

1 4.25 0.44 0.50 4 0.62 3.12 1.00 1.94 0.121 1/4 4.62 0.50 0.50 4 0.62 3.50 1.00 2.31 0.121 1/2 5.00 0.56 0.50 4 0.62 3.88 1.00 2.56 0.12

2 6.00 0.62 0.62 4 0.75 4.75 1.25 3.06 0.252 1/2 7.00 0.69 0.62 4 0.75 5.50 1.25 3.56 0.25

3 7.50 0.75 0.62 4 0.75 6.00 1.25 4.25 0.253 1/2 8.50 0.81 0.62 8 0.75 7.00 1.25 4.81 0.25

4 9.00 0.94 0.62 8 0.75 7.50 1.25 5.31 0.255 10.00 0.94 0.75 8 0.88 8.50 1.50 6.44 0.256 11.00 1.00 0.75 8 0.88 9.50 1.50 7.56 0.258 13.50 1.12 0.75 8 0.88 11.75 1.50 9.69 0.2510 16.00 1.19 0.88 12 1.00 14.25 1.62 11.94 0.2512 19.00 1.25 0.88 12 1.00 17.00 1.62 14.06 0.2514 21.00 1.38 1.00 12 1.12 18.75 1.88 15.38 0.2516 23.50 1.44 1.00 16 1.12 21.25 1.88 17.50 0.2518 25.00 1.56 1.12 16 1.25 22.75 2.12 19.62 0.2520 27.50 1.69 1.12 20 1.25 25.00 2.12 21.75 0.3824 32.00 1.88 1.25 20 1.38 29.50 2.25 26.00 0.3830 38.75 2.12 1.25 28 1.38 36.00 2.25 - 0.38

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26

noM.

DIa.

FlangE RaIsED FaCE bolts DRIllIng sPotFaCE

DIaMEtER

hUb

D b d4 Fmax no DIa. d2 k d3 r

1/2 3.50 0.44 - - 4 1/2 0.62 2.38 1.00 1.19 0.123/4 3.88 0.50 - - 4 1/2 0.62 2.75 1.00 1.50 0.121 4.25 0.56 2.00 1/16 4 1/2 0.62 3.12 1.00 1.94 0.12

1 1/4 4.62 0.62 2.50 1/16 4 1/2 0.62 3.50 1.00 2.31 0.121 1/2 5.00 0.69 2.88 1/16 4 1/2 0.62 3.88 1.00 2.56 0.12

2 6.00 0.75 3.62 1/16 4 5/8 0.75 4.75 1.25 3.06 0.252 1/2 7.00 0.88 4.12 1/16 4 5/8 0.75 5.50 1.25 3.56 0.25

3 7.50 0.94 5.00 1/16 4 5/8 0.75 6.00 1.25 4.25 0.253 1/2 8.50 0.94 5.50 1/16 8 5/8 0.75 7.00 1.25 4.81 0.25

4 9.00 0.94 6.19 1/16 8 5/8 0.75 7.50 1.25 5.31 0.255 10.00 0.94 7.31 1/16 8 3/4 0.88 8.50 1.50 6.44 0.256 11.00 1.00 8.50 1/16 8 3/4 0.88 9.50 1.50 7.56 0.258 13.50 1.12 10.62 1/16 8 3/4 0.88 11.75 1.50 9.69 0.25

10 16.00 1.19 12.75 1/16 12 7/8 1.00 14.25 1.62 12.00 0.2512 19.00 1.25 15.00 1/16 12 7/8 1.00 17.00 1.62 14.38 0.2514 21.00 1.38 16.25 1/16 12 1 1.12 18.75 1.88 15.75 0.2516 23.50 1.44 18.50 1/16 16 1 1.12 21.25 1.88 18.00 0.2518 25.00 1.56 21.00 1/16 16 1 1/8 1.25 22.75 2.12 19.88 0.2520 27.50 1.69 23.00 1/16 20 1 1/8 1.25 25.00 2.12 22.00 0.3824 32.00 1.88 27.25 1/16 20 1 1/4 1.38 29.50 2.25 26.12 0.38

DIMEnsIons oF stEEl FlangEs to asME/ansI b16.5

ASME/ANSI B16.5 – 150lb RATING - STEEL

notE - All dimensions listed below are in inches

asME/ansI b16.5 – 150lb – RATING - STEEL – 300lb – RATING - STEEL

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27

noM. DIa.

FlangE RaIsED FaCE bolts DRIllIng sPotFaCE DIaMEtER

hUbD b d4 Fmax no DIa. d2 k d3 r

1/2 3.75 0.56 1.38 1/16 4 1/2 0.62 2.62 1.00 1.50 0.123/4 4.62 0.62 1.69 1/16 4 5/8 0.75 3.25 1.25 1.88 0.121 4.88 0.69 2.00 1/16 4 5/8 0.75 3.50 1.25 2.12 0.12

1 1/4 5.25 0.75 2.50 1/16 4 5/8 0.75 3.88 1.25 2.50 0.121 1/2 6.12 0.81 2.88 1/16 4 3/4 0.88 4.50 1.50 2.75 0.12

2 6.50 0.88 3.62 1/16 8 5/8 0.75 5.00 1.25 3.31 0.252 1/2 7.50 1.00 4.12 1/16 8 3/4 0.88 5.88 1.50 3.94 0.25

3 8.25 1.12 5.00 1/16 8 3/4 0.88 6.62 1.50 4.62 0.253 1/2 9.00 1.19 5.50 1/16 8 3/4 0.88 7.25 1.50 5.25 0.25

4 10.00 1.25 6.19 1/16 8 3/4 0.88 7.88 1.50 5.75 0.255 11.00 1.38 7.31 1/16 8 3/4 0.88 9.25 1.50 7.00 0.256 12.50 1.44 8.50 1/16 12 3/4 0.88 10.62 1.50 8.12 0.258 15.00 1.62 10.62 1/16 12 7/8 1.00 13.00 1.62 10.25 0.25

10 17.50 1.88 12.75 1/16 16 1 1.12 15.25 1.88 12.62 0.2512 20.50 2.00 15.00 1/16 16 1 1/8 1.25 17.75 2.12 14.75 0.2514 23.00 2.12 16.25 1/16 20 1 1/8 1.25 20.25 2.12 16.75 0.2516 25.50 2.25 18.50 1/16 20 1 1/4 1.38 22.50 2.25 19.00 0.2518 28.00 2.38 21.00 1/16 24 1 1/4 1.38 24.75 2.25 21.00 0.2520 30.50 2.50 23.00 1/16 24 1 1/4 1.38 27.00 2.25 23.12 0.3824 36.00 2.75 27.25 1/16 24 1 1/2 1.62 32.00 2.75 27.62 0.38

ASME/ANSI B16.5 – 300lb RATING - STEEL

*NOTE:The standard for Ductile Iron flanges is ASME/ANSI B16.42 150lb and 300lb rating.

They are dimensionally the same as ASME/ANSI B16.5 including the raised face.

The standard for Copper Alloy flanges is ASME/ANSI B16.24 150lb and 300lb rating.

They are dimensionally the same as ASME/ANSI B16.5 except they are FLAT FACE.

seCtiON 2


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sECtIon 3

PUMP InstallatIonFixed pumps must be securely anchored to firm foundations. Pumps must be accurately levelled with shafts, coupling faces and flange faces truly horizontal or vertical (as appropriate). The pump and driver shafts should be truly in line in all senses and checks and requisite adjustments should be made by means of wedges and shims both in initial setting-up and after grouting in and tightening down.

Foreign matter must be prevented from ingress to liquid openings, bearings, etc., and external pipe-bores ensured clean before connecting. Pipework must be brought up to pump orifices, and independently supported, so as not to impose any weight or strain on the pump when connected. Make sure at all stages that the pump will turn freely. For fuller particulars see specific instructions as supplied with pumps.

sECtIon 4

PUMP oPERatIonSPP’s Field service engineers can provide a full commissioning service for a wide range of pumps. Contact your local SPP office for details• Check all guards are fitted correctly before starting the pump• Make sure pump will turn freely• Check driver and pump rotations agree, with driver uncoupled• Make sure bearings are adequately charged with clean lubricant• Check stuffing boxes are packed and correctly adjusted• Make sure any external lubricating, cooling, sealing, etc., services and

connections are turned on and operative• Make sure pump is effectively primed before starting up• Check that pump runs without undue overheating, noise or vibration:

otherwise refer to detailed operating instructions for possible defects and rectify accordingly

• On no account must a pump be allowed to continue running unprimed, or with a closed discharge valve

• On no account should a pump be regulated by closing a valve on the suction side

Contents3 4

Potential Fault or Defect:

No liquid delivered.

Insufficient liquid delivered.

Liquid delivered at low pressure.

Loss of liquid after starting.

Excessive vibration.

Motor runs hotter than normal.

PRobablE CaUsEs

• Pump not primed.

• • • Speed too low.

• • Speed too high.

• • • • • Air leak in suction pipework.

• • Air leak in mechanical seal.

• • • • Air or gas in liquid.

• • • Discharge head too high (above rating).

• Suction lift too high.

• Not enough head for hot liquid.

• • • • • Inlet pipe not submerged enough.

• • • Viscosity of liquid greater than rating.

• Liquid density higher than rating.

• • • • • Insufficient nett inlet head.

• • • Impeller blocked.

• • • Wrong direction of rotation.

• • Excessive impeller clearance.

• • • Damaged impeller.

• Rotor binding.

• Defects in motor.

• Voltage and/or frequency lower than rating.

• Lubricating grease or dirty oil or contaminated.

• Foundation not rigid.

• • • Misalignment of pump and driver.

• Bearing worn.

• • Rotor out of balance.

• • • Shaft bent.• Impeller too small.

sECtIon 5

Excessive noise from pump cavitation.

Pump bearings run hotter than normal.

29

FaUlts anD REMEDIal aCtIon

SPP’s service division can carry out fault identification and rectification on a wide range of pumps. Contact your local SPP office for details

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30

CAUSE REMEDIAL ACTIONPump not primed. Fill pump and suction pipe completely with fluid.

Speed too low.Check that the motor is correctly connected and receiving the full supply voltage also confirm that the supply frequency is correct.

Speed too high. Check the motor voltage.Air leak in suction pipework. Check each flange for suction draught, rectify as necessary.

Air leak in mechanical seal.Check all joints, plugs and flushing lines, if fitted. Note that prolonged running with air in the mechanical seal will result in damage and failure of the seal.

Air or gas in liquid.It may be possible to increase the pump performance to provide adequate pumping.

Discharge head too high (above rating).

Check that valves are fully open and for pipe friction losses. An increase in pipe diameter may reduce the discharge pressure.

Suction lift too high.Check for obstruction of pump inlet and for inlet pipe friction losses. Measure the static lift, if above rating, raise the liquid level or lower the pump.

Not enough head for hot liquid. Reduce the positive suction head by raising the liquid level.Inlet pipe not submerged enough.

If the pump inlet cannot be lowered, provide a baffle to smother the inlet vortex and prevent air entering with the liquid.

Viscosity of liquid greater than rating.

Refer to SPP Pumps Ltd for guidance to increase the size or power of the motor or engine.

Liquid density higher than rating.

Refer to SPP Pumps Ltd for guidance to increase the size or power of the motor or engine.

Insufficient nett inlet head.Increase the positive suction head by lowering the pump or raising the liquid level.

Impeller blocked. Dismantle the pump and clean the impeller.Wrong direction of rotation. Check driver rotation with the direction arrow on the pump casing.Excessive impeller clearance. Replace the impeller when clearance exceeds the maximum adjustment.Rotor binding. Check for shaft deflection, check and replace bearings if necessary.

Defects in motor.Ensure that motor is adequately ventilated. Refer to manufacturers’ instructions.

Voltage and/or frequency lower than rating.

If voltage and frequency are lower than the motor rating, arrange for provision of correct supply.

Lubricating grease or oil dirty or contaminated.

Dismantle the pump, clean the bearings, reassemble the pump and fill with new grease or oil.

Foundation not rigid.Ensure that the foundation bolts are tight, check that foundations match SPP Pumps Ltd recommendations.

Misalignment of pump and driver.

Realign the pump and driver as specified.

Bearings worn.Remove the bearings, clean and inspect for damage and wear, replace as necessary.

Rotor out of balance. Check impeller for damage, replace as necessary.Shaft bent. Check shaft run-out and replace if necessary.Impeller too small. Refer to SPP Pumps Ltd for options to fit a larger impeller.

SPP’s service division can carry out fault identification and rectification on a wide range of pumps. Contact your local SPP office for details

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sECtIon 6

VIbRatIon tolERanCE In every pump there are dynamic forces of hydraulic or mechanical origin that will inevitably lead to a certain level of vibration. To maintain the integrity of the pump unit and associated equipment the level of vibration must be kept within certain limits.

acceptance CriteriaThe following table defines the maximum allowable level of vibration measured in mm/s RMS overall velocity during a factory acceptance test. It should be noted that the factory acceptance test is not necessarily an accurate representation of the vibration on site, when the unit is grouted in with permanent pipe supports etc.

Pump ClassesClass 1 pumps will only include those that have been designed in full accordance with A.P.I. 610, for use in critical applications. None of the standard ranges of SPP fall into this class and pumps that meet it are only available on an engineered to order basis.

Class 2 pumps will include all SPP general purpose industrial designs apart from those specifically identified as class 3 below.

Class 3 pumps shall include any pumps with less than three impeller vanes, split case pumps of the “through bore” type and any unit driven by a diesel engine of four or more cylinders. (Refer to SPP Engineering for units driven by engines of three or less cylinders).

application / Class Class 1 Class 2 Class 3Continuous operation over the preferred

operating range

3.0 4.7 7.1

Continuous operation over the allowable

operating range

3.9 5.6 9.0

Intermittent operation over the allowable

operaing range

Not applicable 9.0 13.0

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MethodVibration measurements will be made on the pump bearing housings, as close as is practical to the bearing positions.

For each bearing position two measurements will be taken perpendicular to the pump rotation axis. In addition an axial measurement will be taken at the thrust bearing position.

The measurements will be of velocity, overall RMS values, in mm/s.

In order to reliably achieve the stated acceptance limits the pump must be rigidly restrained, aligned to the driver within the coupling makers recommendations, operating without cavitation or air entrainment. Pipe work must be arranged to provide straight uniform flow into the pump and be connected and anchored so as avoid strains and resonance.

SPP’s field service engineers can undertake vibration analysis. Contact your local SPP office for details

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33

sECtIon 7

ConDItIon MonItoRIngIn order to minimise the ownership costs of capital equipment, it is critical for the user to monitor and maintain the equipment once installed. Failure to do so will impact both on the mechanical integrity and economic performance of the installed equipment.

Early diagnosis of potential equipment failure can result in considerable repair cost savings and crucially a reduction in unplanned downtime. Monitoring of pump energy consumption and system efficiency will bring visibility to pump wear, operating efficiency and highlight any system irregularities. All of these factors will help minimise energy consumption and reduce operating costs.

The SPP condition monitoring systems can provide this level of security by detecting, analysing and evaluating key equipment performance. These include the following:

• Performance/Efficiency degradation

• Bearing vibration levels

• Bearing element damage

• Bearing operating temperatures

• Driver alignment condition

• Residual unbalance

• Cavitation

The system provides considerable flexibility in the display and use of the diagnostic output. The options include web based user configurable dashboard for live and trend data, automatic notification of alerts by text or email and local download of data to PC for detailed evaluation.

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sECtIon 8

FloW EstIMatIon MEthoDsMany pumping systems are fitted with permanently installed flowmeters which enable a reasonably accurate measurement of system flow to be obtained. Where permanent flowmeters are not installed, it is often possible to use external clamp-on meters, insertion meters or thermodynamic testing equipment to determine system flow. However, it is not always practical to use these devices – either for financial reasons or system layout constraints – and where this is the case, alternative indirect methods need to be used for estimating system flow.

There are a number of methods available to enable an estimation of flow to be made in the field. Each of these methods requires some form of knowledge of the system or the pump, and all have inherent inaccuracies of varying degrees. However, in the absence of any more accurate flow measuring apparatus, these can be the only alternatives available.

There are four main indirect methods of determining pump flow in the field:• Pressure method• Power method• Drop test• Suction pressure measurement

The Pressure and Power methods require the use of the pump curve, whilst the drop test requires sump geometry and level details.

PREssURE MEasUREMEnt

This is the more accurate and simplest of the four methods, requiring suction and delivery pressure gauge readings, a copy of the pump performance curve at the correct operational speed and knowledge of the impeller diameter.

Determine the differential head across the pump by subtracting the suction head from the discharge head. Then use the pump performance curve to obtain the pump flow at the measured head and impeller diameter.

For example, if the suction head is measured as 3m and the discharge head as 63m, the pump differential head is 60m. Using the pump manufacturers original test curve for the pump, the flow can be estimated as 150 l/s.

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Over time, a pump’s Flow/Head curve will change as wear occurs within the pump. Therefore, the accuracy of this method will tend to reduce as the pump gets older. However, this will remain a more accurate method than the others detailed below.

Where existing installed site gauges are used, it should be remembered that their accuracy may be far from ideal.

Remember that the pump Q/H curve is based on differential head, normally pumping water with an SG of 1. If the site liquid being pumped has an SG other than 1, SG correction should be applied to the site pressure readings to match the performance curve being used.

PoWER MEasUREMEntPower meters are rarely available on site, but amps (I) and volts (V) are commonly displayed at the control panel. These readings can be used to calculate power, although this also requires motor efficiency and power factor data - which will need to be estimated if motor manufacturers information is not available.

Power (kW) = (1.732 x I x V x eff x pf)/1000

Using this equation, the pump power can be calculated and from this, the flow can be read off the pump curve.

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36

Reading across the power scale on the pump manufacturers curve, the flow at this absorbed power can be obtained – 150 l/s in this example.

As mentioned above, a pump’s Flow/Head curve and efficiency curve will change as wear occurs within the pump. This will affect the pump’s power curve and therefore, as with the pressure measurement method, accuracy will tend to reduce as the pump gets older.

It should also be remembered that the installed instruments from which readings are taken may themselves be inaccurate, as it is unlikely that they will not have been calibrated to any significant accuracy since their original installation.

As an alternative to the above calculation, taking a simple current ratio (actual current/full load current) and applying it to the motor rated power can give a reasonable estimation of the motor output power. In the above example, assuming a 132kW motor with a full load current of 230A, this method would result in a duty power of (165/230)*132 = 95kW, and a resultant flow of around 135 l/s.

For example, if the current is read as 165A, the voltage as 400V and motor efficiency and pf from manufacturers’ data are 95% and 0.92 respectively, the calculated power becomes:

Power = (1.732 x 400 x 165 x 0.95 x 0.92)/1000 = 100kW

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Although the power method can be used very effectively in situations where a quick approximate on site estimate is required, it should not be applied to high specific speed pumps such as vertical turbine or mixed flow pumps, whose power curves can follow significantly different rules.

DRoP tEstThis is the least accurate method, and requires knowledge of sump dimensions and levels. It is often used on sewage pump installations, where sump emptying occurs over a relatively short period of time.

In this method, the time taken for a pump to lower the sump level over a known depth is recorded. The volume of liquid pumped is then calculated based on the sump level change and the sump area, and is divided by the time taken to arrive at a volume flow rate.

For example, if a sump has dimensions of 4m x 3m, and the level is reduced by 1m over a time period of 10 minutes, the average pump flow is (4 x 3 x 1)/10 = 1.2 m3/min, or 72 m3/h

This method has a number of inherent inaccuracies:

• During the drop test, it is likely that flow will continue to enter the sump. This will affect the result – the extent of the effect will depend upon the rate of inflow in proportion to the outflow.

• The sump may not have a uniform section, making volume calculation less accurate.

• As the level is lowered, the total head on the pump changes which will affect the pump output. Any resultant calculation will only give an average flow over the range of heads.

• Measurement of pumped depth may be difficult if there is no installed measuring equipment.

sUCtIon PREssURE MEasUREMEntIn most pumping stations, it is possible to obtain a pressure reading on the suction side of the pumps. The velocity and friction head components of this reading can be used to estimate the flow. To use this method, it is necessary to know the pressure drop on the pump suction (static suction pressure - operational suction pressure), the type and number of pipe fittings up to the pressure measurement point and fittings diameter. An estimation of the fittings friction (K) factor is also required.

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Convert the suction pressure drop (P in kPA) into a head drop (Zd in meters) using the equation:

Zd = P x 0.102 sg

(note that this Zd calculation will change depending on your site measured units)

Obtain a total K factor for the suction fittings up to the measurement point. Assuming there are no significant straight pipe losses in the suction, the following equation can then be used to determine the flow velocity:

Zd = V2 x (1+K) 2g

Once the velocity is known, the flow rate can be calculated using the suction diameter. This method can be adapted to suit a wide variety of suction and pump configuration and the available locations for pressure measurement.

Although there are potential inaccuracies in determining K factors and internal diameters, careful use of this method can allow the velocity to be estimated to within a few percent.

ConClUsIon

There is no single simple and accurate method of determining flow in systems where installed meters are not present, or where the use of alternative temporary flow metering equipment cannot be fitted. Instead there are a number of methods that can be utilised to obtain an approximate pumping rate, which in many cases may be sufficient for the purposes required.

All these methods have limitations and inherent inaccuracies. Where these methods need to be employed, it is worthwhile applying at least two methods to get comparative results.

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3939

sECtIon 9

aPPlICatIon Do’s anD Don’tssuction & Delivery PipingEnsure that bolt grouting or chemical anchors are allowed to dry thoroughly before connecting any pipework.

Note that fire pumpsets have regulatory requirements for piping and these must be strictly observed. Refer to the appropriate standard for details.

Both suction and discharge piping should be supported independently and close to the pump so that no strain is transmitted to the pump when the flange bolts are tightened. Use pipe hangers or other supports at intervals necessary to provide support. When expansion joints are used in the piping system, they must be installed beyond the piping supports closest to the pump.

Install piping as straight as possible, avoiding unnecessary bends. Where necessary, use 45º or long sweep 90º bends to decrease friction losses.

Eccentric Reducer on a Split Case Pump

Typical End Suction Pump Piping Installation

seCtiON 9


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40

Make sure that all piping joints are airtight. Where reducers are used, eccentric or ‘flat top’ reducers are to be fitted in suction lines and concentric or straight taper reducers in discharge lines. The length of eccentric reducers should be about four times the pump suction diameter. Undulations in the pipe runs are also to be avoided. Failure to comply with this may cause the formation of air pockets in the pipework and thus prevent the correct operation of the pump and measuring equipment.

The suction pipe should be as short and direct as possible, and should be flushed clean before connecting to the pump. For suction lift applications, it is advisable to use a foot valve. Horizontal suction lines must have a gradual rise to the pump. If the pumped fluid is likely to contain foreign matter then a filter or coarse strainer should be fitted to prevent ingress to the pump.

The discharge pipe is usually preceded by a non-return valve or check valve and a discharge gate valve. The check valve is to maintain system pressure in case of stoppage or failure of the driver. The discharge valve is used to prevent back flow when shutting down the pump for maintenance.

CoUPlIng alIgnMEntPeriodical checks of shaft alignments should be undertaken and if necessary adjusted accordingly. In order to maintain the warranty status of your SPP pump it is recommended to take out an SPP preventative maintenance contract. SPP’s field service engineers have extensive experience in pump and coupling alignment. Refer to the pump and coupling instruction manuals for details of shaft alignment procedures and tolerances or proceed generally thus:

a) Lateral Alignment

Mount a dial gauge on the motor shaft or coupling with the gauge running on the outer-machined diameter of the pump coupling. Turn the motor shaft and note the total indicator reading.

b) Angular Alignment

Mount a dial gauge on the motor shaft or coupling to run on a face of the pump coupling as near to the outside diameter as possible. Turn the motor shaft and note the total indicator reading at top & bottom and each side.

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41

c) Confirm Lateral Alignment

Mount the dial gauge on the pump shaft or coupling with the gauge running on the machined outer diameter of the motor coupling. Turn the pump shaft and note the total indicator reading.

d) Adjustment

The motor must be shimmed and re-positioned to align the shafts to the coupling manufacturer’s specifications.

note:Shaft alignment must be checked again after the final positioning of the pump unit and connection to pipework as this may have disturbed the pump or driver mounting positions.

EngInE DRIVEn PUMPsAir is required for combustion and cooling purposes, with air and radiator cooled engines in particular needing large volumes of air for cooling. Inlet and outlet apertures, suitably sized and positioned to prevent air recirculation, must be provided in the pump house structure. It is recommended that a low level vent be matched by a high level vent in the opposite wall.

Exhaust runs should be as short as possible. Small bore pipe and/or excessive length will cause backpressure on the engine, reducing engine performance and therefore pump output.

Engine driven fire pumps should not be left unattended whilst undertaking weekly test runs. The run-to-crash design of fire pump engines makes it essential to that they are commissioned by experienced personnel to avoid permanent damage. SPP offers fixed price fire pump commissioning services

PRE-CoMMIssIonIng ChECKIf SPP Pumps Ltd is contracted to carry out the commissioning, the following check list shows items to be completed before the commissioning engineer arrives.

sPP CoMMIssIonIng sERVICEsSPP use qualified engineers to maintain approved systems, warranty and approved parts.

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42

ChECK lIst

1 Installation:• Mounting plinths comply with instructions for size, construction

and location

• The baseplate has been accurately levelled and adequately supported. This prevents distortion and makes achievable the final shaft alignment to within manufacturers specification

• The fixing bolts are grouted as instructed and tightened to the required torque

• The shaft alignment has been checked and set to within the stated tolerances.

2 Suction and delivery pipework is adequately supported and NEGLIGIBLE forces are transmitted to the pump casing.

3 Where applicable, all drain, minimum flow, and test pipelines are fitted, together with valves gauges and flow meters.

4 The diesel engine exhaust has been fitted in line with recommendations.

5 The engine fuel tank is filled with sufficient fuel.

6 Batteries are filled and charged in accordance with the manufacturer’s instructions.

7 All wiring to controls and to remote alarm panels is completed in line with appropriate regulations & power supplies are connected.

8 The area is clear of all builders’ material and rubbish to allow access to the pumps.

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43

hyDRaUlIC DEsIgn Data

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44

sECtIon 10

PREssURE (bar) Vs hEaD (m oF WatER)

bar

00.

10.

20.

30.

40.

50.

60.

70.

80.

9

0.00

0.00

1.02

2.04

3.06

4.08

5.10

6.12

7.14

8.16

9.18

1.00

10.1

911

.22

12.2

413

.26

14.2

815

.30

16.3

217

.33

18.3

519

.37

2.00

20.3

921

.41

22.4

323

.45

24.4

725

.49

26.5

127

.53

28.5

529

.57

3.00

30.5

931

.61

32.6

333

.65

34.6

735

.69

36.7

137

.73

38.7

539

.77

4.00

40.7

941

.81

42.8

343

.85

44.8

745

.89

46.9

147

.93

48.9

549

.97

5.00

50.9

952

.00

53.0

254

.04

55.0

656

.08

57.1

058

.12

59.1

460

.16

6.00

61.1

862

.20

63.2

264

.24

65.2

666

.28

67.3

068

.32

69.3

470

.36

7.00

71.3

872

.40

73.4

274

.44

75.4

676

.48

77.5

078

.52

79.5

480

.56

8.00

81.5

882

.60

83.6

284

.64

85.6

586

.67

87.6

988

.71

89.7

390

.75

9.00

91.7

792

.97

93.8

194

.83

95.8

596

.87

97.8

998

.91

99.9

310

0.95

1020

3040

5060

7080

9010

0ba

r

101.

9720

3.94

305.

9140

7.88

509.

8561

1.82

713.

7981

5.76

917.

7310

19.7

0m

etre

s

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45

ExaMPlEFind the metres head of water (1.0 s.g.) equivalent of 54.76 bar

From bottom two lines: 50.00 bar = 509.85m

Select ‘4 bar’ line in first column and read along to figure under 0.7 in top line, hence:

4.70 bar = 47.93m

For 0.06 bar, read under 0.6 top line: hence 6.12m dividing both figures by 10:

0.06 bar = 0.612m

thus by addition 54.76 bar = 558.392m

note: For liquids with specific gravities differing from 1.0, answer must be divided by actual specific gravity to obtain head in metres of liquid.

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sECtIon 11

CalCUlatIon oF hEaD FoR PUMP sElECtIonTo fulfill a pumping duty a pump must develop sufficient head and meet the suction conditions. The total head of a system must take into account the difference in liquid levels at inlet and outlet, friction in the pipes, surface pressure (or in some cases vacuum) on inlet and outlet and the velocity of the fluid at discharge. The following diagram and example explains how to calculate the system head taking all these factors into account.

• hd = total discharge head

• hsd = discharge static head

• hpd = discharge surface pressure head

• hfd = discharge friction head

• hvd = discharge velocity head

System head = total discharge head - total suction head

H = hd – hs

The total discharge head is made from four separate heads:

hd = hsd + hpd + hfd + hvd

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The total suction head consists of four separate heads

hs = hss + hps - hfs - hvs

• hs = total suction head

• hss = suction static head

• hps = suction surface pressure head

• hfs = suction friction head

• hvs = suction velocity head

Example

Calculate the total head of the following pump system.

The total friction through suction pipes and fittings is equivalent to 1m head and through delivery pipes and fittings is equivalent to 10m head.

The header tank and discharge pipe is open to atmosphere at sea level.

The suction velocity head is 0.1m and the discharge velocity head is 0.5m

Pumped fluid is cold clean water.

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48

First we calculate the total delivery head, hsd and hss – from the diagram we can see that the discharge static head is 40m and the suction static head is 5m hpd –

millimeters of mercury x = meters of liquid

pressure at sea level is approx. 760mm Hg, specific gravity of cold clean water is 1, so 760 x 0.014/1 = 10.6m

so hpd is 10.6m, the header tank is also open to atmosphere so hps is also 10.6m

hd = hsd + hpd + hfd + hvd

= 40 + 10.6 + 10 + 0.5

= 61.1 m

hs = hss + hps - hfs - hvs

= 5 + 10.6 - 1 - 0.1

= 14.5 m

Total system head H = hd – hs

= 61.1 – 14.5

= 46.6 m

note:Gauge readings need correcting for height of gauge mounting. For this purpose it is important that pressure gauges should be full of liquid. Where a vacuum gauge is used for a suction lift, the gauge pipe should be left empty and correction made from the point of connection, not from the gauge itself.

0.014specific gravity

Contents3 4

49

aUtoPRIME PUMPIng tERMshead“Total Head from all Causes” is the combination of both “Total Suction Head and “Total Discharge Head”.

When static heights are kept to a minimum and pipework of the correct size for the pump is used, performance will be maintained and running costs minimised.

Suction head will be affected by changes in liquid viscosity and specific gravity and in the vapour pressure resulting from increased liquid temperature.

net Positive suction head (nPsh)NPSHr: minimum liquid head (pressure) required by the pump at the impeller to pump the liquid, this is determined by the pump design. NPSHa: minimum liquid head (pressure) available from the atmosphere to deliver the liquid to the impeller for pumping.

Example:

NPSHa (Available) 10.5 m

less Static Lift 3.0 m

Friction & Vapour Loss 1.5 m

NPSHr (Required) 2.0 m

therefore leaving for suction lift 4.0 m

seCtiON 11


Contents3 4

50

tyPICal sUCtIon lIFt ConFIgURatIon

AUTOPRIME

TOTALHEADFROMALL

CAUSES

TotalDischarge

Head

DischargeHose

Friction

StaticDelivery

Head

StaticSuction

Lift

SuctionHose

Friction

Contents3 4

51

sECtIon 12

FRICtIon loss FoR WatER (m/100m) In sMooth anD nEW UnCoatED stEEl PIPEs (haZEn-WIllIaMs FoRMUla, C=140)NB Figures assume actual bores exactly equal to nominal bores. See following notes regarding corrections for actual bores of commercial pipes differing from nominal bores.

l/s bore

20(3/4) 25(1)0.1 0.83 0.28 32(1 3/4) - -0.2 3.0 1.0 0.30 40(1 1/2) -0.5 16.4 5.5 1.66 0.56 50(2)1 65(2½) 20.0 6.0 2.0 0.68

1.5 0.4 80(3) 12.7 4.3 1.452 0.68 0.25 21.6 7.3 2.53 1.45 0.53 100(4) 15.5 5.24 2.5 0.90 0.30 26.4 8.95 3.8 1.36 0.46 125(5) 13.46 5.2 1.9 0.64 0.22 18.87 6.9 2.5 0.84 0.29 150(6)8 8.9 3.2 1.10 0.37 0.159 11.1 4.0 1.36 0.46 0.19

10 13.4 4.9 1.66 0.55 0.2312 175(7) 6.9 2.3 0.78 0.3214 0.20 9.1 3.1 1.04 0.4316 0.26 11.7 4.0 1.33 0.5518 0.32 200(8) 4.9 1.65 0.6820 0.39 0.20 6.0 2.0 0.8325 0.59 0.31 9.0 3.0 1.2530 0.83 0.43 225(9) 4.3 1.7635 1.10 0.58 0.32 5.7 2.340 1.41 0.74 0.42 7.3 3.045 1.76 0.92 0.52 250(10) 3.750 2.1 1.11 0.63 0.38 4.560 3.0 1.56 0.88 0.53 6.370 4.0 2.1 1.17 0.70 300(12)80 5.1 2.7 1.50 0.90 0.3790 6.3 3.3 1.87 1.12 0.46100 4.0 2.3 1.36 0.56120 5.6 3.2 1.90 0.78140 7.5 4.2 2.5 1.04160 5.4 3.2 1.33180 6.7 4.0 1.65

200 8.2 4.9 2.0

Nominal and actual bores of pipes in mm width with nominal inch equivalents.

seCtiON 12


Contents3 4

52

For other types of pipe, multiply foregoing figures as below, for pipes in smooth and new condition.

Galvanised iron 1.33

Uncoated cast iron 1.23

Coated cast iron, wrought iron, coated steel 1.07

Coated spun iron 1.04

Smooth pipe (lead, brass, copper, stainless steel, glass, plastic) 0.88

Friction losses are affected to an even greater degree by deviations of actual bore from the standard dimensions represented in the foregoing table.

To correct for actual bore, multiply also by

(D/d)4.87

Where D = Standard (nominal) bore.

d = Actual internal diameter.

Multiplying factors for grey iron pipes to BS 4622 (both sand mould cast and spun): ductile iron pipes to BS 4772: and uPVC pipes to BS 3505 taking into account the corrections both for type of pipe and for actual bore, are as follows on the next page.

Contents3 4

53

nom

inal

bor

e m

m20

2532

4050

6580

100

125

150

175

200

225

250

300

(in)

(¾)

(1)

(1¼

)(1

½)

(2)

(2½

)(3

)(4

)(5

)(6

)(7

)(8

)(9

)(1

0)(1

2)

grey

Iron

, bs

4622

:

Clas

s 1

(spu

n)-

--

0.84

0.90

-0.

93-

0.95

-0.

960.

97

Clas

s 2

(spu

n)-

--

0.91

0.97

-0.

99-

1.00

-1.

001.

00

Clas

s 3

(spu

n)-

--

0.99

1.04

-1.

04-

1.04

-1.

041.

04

Clas

s 4

(spu

n)-

--

1.18

1.21

-1.

16-

1.14

-1.

131.

12

For s

and

mou

ld c

ast p

ipes

mul

tiply

by

1.03

: al

so fo

r unc

oate

d bo

re p

ipes

by

1.15

Duct

ile Ir

on, b

s 47

22:

Clas

s K9

--

-0.

730.

97-

0.77

-0.

78-

0.80

0.78

Clas

s K1

2-

--

0.82

0.88

-0.

85-

0.86

-0.

870.

84

uPVC

, bs

3505

:

Clas

s b

--

-0.

780.

650.

680.

680.

730.

740.

770.

750.

80

Clas

s C

-0.

570.

680.

830.

720.

790.

790.

840.

850.

880.

860.

90

Clas

s D

0.66

0.64

0.78

0.96

0.84

0.92

0.92

0.98

0.97

1.03

0.98

1.04

Clas

s E

0.75

0.75

0.91

1.12

0.97

1.06

1.07

1.13

1.10

1.16

1.12

1.19

stee

l tub

es, b

s 13

87

med

ium

; als

o x

1.24

for g

alva

nise

d

0.79

0.75

0.64

0.90

0.84

0.85

1.06

0.87

0.92

0.93

--

--

-

seCtiON 12


Contents3 4

54

sECtIon 13

REsIstanCE In FIttIngsAs in straight pipe, having length of following multiples of pipe diameter:

Flush sharp-edged entry 22

Slightly rounded entry 11

Flush bellmouth entry 4

Sharp entry projecting into liquid 36

Bellmouth entry projecting into liquid 9

Footvalve with strainer 113

Round elbow 45

Short radius bend 34

Medium radius bend 18

Close return bend 100

Tee: straight through 11

side outlet, sharp angled 54

side outlet, radiused (swept tee) 22

Branch piece, straight through 7

Branch piece, flow to branch 45

Branch piece, flow from branch 22

Sluice (gate) valve 7

Reflux (back pressure, non-return) valve 45

Angle valve 225

Globe valve 450

Bellmouth outlet 9

Sudden enlargement 45

Taper, divergence angle above 60º 45

Taper, divergence angle 15º - 60º 22

Taper increaser or reduced with less than 15º divergence angle: Equivalent to pipe of mean diameter.

Flap 0.06m Head

note:Multiplying factor for type and class of pipe to be applied to above equivalent lengths for pipe fittings (elbows, bends, tees etc) but not to those for valves.

Contents3 4

55

sECtIon 14

QUantItIEs PassED by PIPEs at DIFFEREnt VEloCItIEs

sECtIon 15

RECoMMEnDED MaxIMUM FloW thRoUgh ValVEs (l/s)

actual bore of pipe, mm

Velocity of flow,

m/s

50 80 100 125 150 175 200 225 250 300

l/s

1 1.96 5.03 7.85 12.27 17.67 24.1 31.4 39.7 49.1 70.7

1.5 2.95 7.54 11.78 18.41 26.51 36.1 47.1 59.6 73.6 106.1

2 3.93 10.05 15.71 24.54 35.34 48.1 62.8 79.5 98.2 141.4

2.5 4.91 12.57 19.64 30.68 44.18 60.1 78.5 99.4 122.7 176.7

3 5.89 15.08 23.56 36.82 53.02 72.2 94.3 119.3 147.3 212.1

3.5 6.87 17.59 27.49 42.95 61.85 84.2 110 139.2 171.8 247.4

4 7.85 20.11 31.42 49.09 70.69 96.2 125.7 159.0 196.4 282.8

5 9.82 25.13 39.27 61.36 88.36 120.3 157.1 198.8 245.4 353.4

size of Valve, mm 50 65 80 100 125 150 175 200 250 300

Foot valve with

strainer2.2 4.0 6.0 12.0 20.0 30.0 40.0 55.0 90.0 130.0

back pressure valve 3.0 5.0 8.0 15.0 25.0 37.5 50.0 70.0 110.0 160.0

sluice valve 5.5 10.0 15.0 25.0 40.0 60.0 80.0 100.0 160.0 220.0

seCtiON 13/14/15


Contents3 4

56

sECtIon 16

QUantItIEs oF WatER DIsChaRgED by RoUnD sPRay holEs In thIn WallED PIPEs UnDER DIFFEREnt PREssUREs

Pres

sure

(b

ar)

head

(m

wat

er)

size

of h

ole

(mm

)

34

56

810

12

l/s p

er h

ole

0.5

5.1

0.04

30.

077

0.12

00.

173

0.30

70.

480.

69

1.0

10.2

0.06

10.

109

0.17

00.

245

0.43

50.

680.

98

1.5

15.3

0.07

50.

133

0.20

80.

300

0.53

20.

831.

20

2.0

20.4

0.08

60.

154

0.24

00.

346

0.61

50.

961.

38

2.5

25.5

0.09

60.

172

0.26

90.

387

0.68

81.

071.

55

3.0

30.6

0.10

60.

188

0.29

40.

424

0.75

41.

181.

70

3.5

35.7

0.11

40.

204

0.31

80.

458

0.81

41.

271.

83

4.0

40.8

0.12

20.

218

0.34

00.

489

0.87

01.

361.

96

5.0

51.0

0.13

60.

243

0.38

00.

546

0.97

21.

522.

19

6.0

61.2

0.15

00.

266

0.41

60.

600

1.06

51.

672.

40

Contents3 4

57

sECtIon 17

nEt PosItIVE sUCtIon hEaD (nPsh)For a pump to fulfil a particular duty it must first be able to get the required quantity in. For example, a pump may work satisfactorily when installed at a given height above the liquid level on the suction side, but no longer do so if it is placed higher, even though the total head remains unaltered in view of a corresponding reduction in the height of lift on the delivery side.

The criteria for this is termed NPSH, which has two aspects, the NPSH the installation and operating conditions provide (NPSH available) and the NPSH needed to get stable flow into the pump impeller (NPSH required). The installation conditions and pump selection must be reconciled so that the NPSH required does not exceed the NPSH available.

Fluid not being sensibly cohesive, it cannot be towed. To be made to flow, it must be pressed from behind. There must, therefore, be either an extraneous pressure on the liquid and/or a head of the liquid itself, which is sufficient to cover losses as far as the pump inlet and then overcome pump inlet losses and create the requisite velocity into the impeller vanes.

The pressure available behind a liquid for creating movement is the absolute pressure on the liquid free surface, less the liquid’s own pressure to move in the opposite direction, i.e. to evaporate into the spaces above the free surface – this is called vapour pressure. The head available at the pump inlet for getting the flow into the pump impeller is therefore:-

• Absolute pressure on liquid free surface Ha

• Plus height of liquid free surface above pump impeller + hs

• Less liquid vapour pressure - hv

• Less losses between liquid free surface and pump inlet - hl

(All expressed in metres head of the liquid).

seCtiON 16/17


Contents3 4

58

note: +hs becomes negative if the liquid free surface is below the pump impeller.

Care must be taken to state NPSH available taking all these factors into account, even though in particular cases the two may equalise each other, e.g. with a liquid at boiling point hv equals Ha and they thus cancel each other out. Otherwise confusion may arise through statement of NPSH, which is plainly inconsistent with the circumstances, e.g. a figure being quoted as NPSH when head over suction hs is meant.

The velocity required at inlet to the impeller vanes is a function of flow quantity, area at vane inlets and velocity induced by impeller rotation. Consequently the NPSH required varies with pump type and size, and increases with both capacity and speed.

To maintain NPSH required within given limits, the permissible speed reduces approximately as the square root of capacity increases.

The increased vapour pressure of warm water often affects suction as indicated by the following table.

Negative figures represent minimum requirement of head of liquid above impeller eye.

note: The above figures are intentionally conservative in order to cover varying suction capabilities of different pumps. Better values may be obtainable especially when the normal capacity of the pump is above the output required, but to allow investigation, full details should be submitted, and the possibility of the temperature being underestimated should not be overlooked.

temp of water oC 40 50 60 70 75 80 85 90 95 100

suction limit (m) 6.25 5.75 4.75 3.25 2.5 1.5 0.25 -1 -2 -3

Contents3 4

59

sECtIon 18

MaxIMUM sUCtIon lIFt WIth baRoMEtRIC PREssURE at DIFFEREnt altItUDEs

sECtIon 19

thERMoMEtER sCalEsTemperature Conversion Formulae:-oF = (oC x 9/5) + 32 oC = (oF – 32) x 5/9

Comparison values in oF and oC scales of temperature

altitude (m)barometric pressure Equivalent

head of water (m)

Practical maximum suction lift of pumps (m)bar mm hg

Sea level 1.013 760 10,33 6.5

500 0.954 716 9.73 6

1000 0.899 674 9.16 5.5

1500 0.846 634 8.62 5

2000 0.796 597 8.12 4.5

oF oC oF oC oF oC-40 -40 113 45 302 150-31 -35 122 50 320 160-22 -30 131 55 338 170-4 -20 140 60 356 1805 -15 149 65 374 190

14 -10 158 70 392 20023 -5 167 75 410 21032 0 176 80 428 22041 5 185 85 446 23050 10 194 90 464 24059 15 203 95 482 25068 20 212 100 500 26077 25 230 110 518 27086 30 248 120 536 28095 35 266 130 554 290

104 40 284 140 572 300

seCtiON 18/19


Contents3 4

60

sECtIon 20

lIQUID VIsCosIty anD Its EFFECts on PUMP PERFoRManCEViscosity is the property of reluctance of a liquid to flow, i.e. the opposite of fluidity.

It involves units of force, length and time and can be expressed as ‘absolute’ in regard to the internal forces in the liquid, or as ‘kinematic’ relating these forces to the liquid specific gravity. The most widely used unit of absolute viscosity is the poise (100 centipoises). However, in all considerations of liquid flow and pump performance the operative factor is the kinematic viscosity, the corresponding unit being the stokes (100 centistokes).

Poises (centipoises)stokes (centistokes) =

specific gravity

Common viscometers (Redwood, Saybold, Engler, etc) give readings having arbitrary relationship to fundamental units. Conversion figures are given in the schedule overleaf. These are approximate only as they may vary slightly with temperature and other factors, and are not universally agreed on, but they are sufficiently accurate for the purposes under consideration.

The only values of interest to the pump engineer are kinematic viscosity at actual pumping temperatures. Viscosities are frequently quoted at standard reference temperatures, commonly 100ºF (37.8ºC) or 60ºC (140ºF). If either of these does not correspond with the actual pumping temperature, the viscosity at the latter must be obtained from product data or estimated from general viscosity/temperature curves.

The performance of a centrifugal pump when handling a viscous liquid depends not only on the viscosity of the liquid but also its relative size and on whether the pump is of low or high specific speed design. The smaller the required pumping duty, the lower the viscosity for which centrifugal pumps are appropriate. For these reasons it is necessary that all enquiries for pumps to handle viscous liquids should be submitted to the pump maker for individual consideration.

In the last column of the schedule, indications have been given of the approximate minimum practical size of centrifugal pump corresponding to each viscosity. In general, for greater viscosities exceeding 25 stokes, pumps of a positive displacement type should be used.

Contents3 4

61

CEntRIFUgal PUMP aFFInIty laWsThe affinity laws can be used to show the effect of either speeding up or slowing down the rotational speed of the impeller and also how changing impeller diameter will alter the performance of a pump. The affinity laws state that:

Pump capacity increases in proportion with impeller rotational speed.Q∝N

Pump head increases in proportion to the square of rotational speed.H∝N2

Pump power increases in proportion to the cube of rotational speed.P∝N3

Where Q = Capacity, H = Head, P = Power and N= Rotational speed

This allows the change in performance to be predicted as a result of changing the pump speed.

Q2 = Q1 N2 N1

H2 = H1 N2 N12

P2 = P1 N2 N13

Where the subscript 1 indicates original condition and the subscript 2 indicates the revised condition.

Increasing either impeller diameter or rotational speed will have the same proportional effect on impeller peripheral speed. This means the same can be applied for changing impeller diameter.

Q2 = Q1 D2 D1

H2 = H1 D2 D12

P2 = P1 D2 D13

Where D = Impeller diameter

The affinity laws are proven to work more effectively for some types of pumps as opposed to others and the accuracy of them is dependent on the pump’s hydraulic design. Because of this fact and that there may be other limiting factors (eg. casing or seal pressure rating, bearing life, etc), it is strongly advised the pump manufacturer be consulted before any changes are undertaken.

seCtiON 20


Contents3 4

62

aPPRoxIMatE VIsCosIty ConVERsIon sChEDUlEKi

nem

atic

Vi

scos

ity

stok

es

Kine

mat

ic

Visc

osity

Ce

ntis

toke

s

Redw

ood

no 1

se

cond

s

sayb

olt

Univ

ersa

l se

cond

s

Engl

er

seco

nds

Engl

er

Degr

ees

Redw

ood

adm

iralty

se

cond

s

sayb

olt

Furo

l se

cond

s

barb

ey

Flui

dity

Min

imum

siz

e Ce

ntrif

ugal

Pu

mp

(mm

)

0.01

129

.031

.051

.31.

00-

-62

00

No

reas

onab

le

limita

tion

0.02

230

.933

.557

.51.

12-

-31

00

0.03

333

.036

.262

.61.

22-

-20

67

0.04

435

.339

.167

.21.

31-

-15

50

0.05

537

.942

.371

.31.

39-

-12

40

0.06

640

.545

.575

.91.

48-

-10

33

0.07

743

.248

.780

.11.

56-

-88

6

0.08

846

.052

.084

.71.

65-

-77

5

0.09

948

.855

.489

.31.

74-

-68

9

0.1

1051

.758

.693

.91.

83-

-62

0

0.2

2085

.097

.514

72.

879

15.0

310

20-2

5

0.3

3012

314

120

94.

0712

18.5

207

25-3

2

0.4

4016

318

627

45.

3316

22.2

153

32-4

0

0.5

5020

323

134

06.

6120

26.0

124

40-5

0

0.6

6024

427

740

67.

9024

30.5

103

40-5

0

0.7

7028

432

347

39.

2128

35.0

88.6

50-6

5

0.8

8032

437

055

910

.532

39.5

77.5

50-6

5

0.9

9036

441

660

611

.836

44.0

68.9

50-6

5

Contents3 4

63

Kine

mat

ic

Visc

osity

st

okes

Kine

mat

ic

Visc

osity

Ce

ntis

toke

s

Redw

ood

no 1

se

cond

s

sayb

olt

Univ

ersa

l se

cond

s

Engl

er

seco

nds

Engl

er

Degr

ees

Redw

ood

adm

iralty

se

cond

s

sayb

olt

Furo

l se

cond

s

barb

ey

Flui

dity

Min

imum

siz

e Ce

ntrif

ugal

Pu

mp

(mm

)

110

040

546

267

713

.241

48.5

62.0

50-8

0

220

081

092

413

5026

.381

94.7

31.0

80-1

00

330

012

1513

8620

3039

.512

214

120

.712

5-15

0

440

016

2018

4827

0052

.616

218

815

.515

0-17

5

550

020

2523

1035

8065

.820

323

512

.417

5-20

0

660

024

3027

7240

6078

.924

328

210

.320

0-25

0

770

028

3532

3447

3092

.128

432

98.

920

0-25

0

880

032

4036

9653

9010

532

437

67.

825

0-30

0

990

036

4541

5860

6011

836

542

36.

925

0-30

0

1010

0040

5046

2067

7013

240

547

06.

230

0-35

0

020

0081

0092

4013

500

263

810

940

3.10

400-

450

3030

0012

150

1386

020

300

395

1215

1410

2.07

Posi

tive

disp

lace

men

t pu

mp

requ

ired

4040

0016

200

1848

027

000

526

1620

1880

1.55

5050

0020

250

2310

033

800

658

2025

2350

1.24

6060

0024

300

2772

040

600

789

2430

2820

1.03

7070

0028

350

3234

047

300

921

2835

3290

8080

0032

400

3696

053

900

1050

3240

3760

9090

0036

450

4158

060

600

1180

3645

4230

100

1000

040

500

4620

067

700

1316

4050

4700

seCtiON 20


Kine

mat

ic

Visc

osity

st

okes

Kine

mat

ic

Visc

osity

Ce

ntis

toke

s

Redw

ood

no 1

se

cond

s

sayb

olt

Univ

ersa

l se

cond

s

Engl

er

seco

nds

Engl

er

Degr

ees

Redw

ood

adm

iralty

se

cond

s

sayb

olt

Furo

l se

cond

s

barb

ey

Flui

dity

Min

imum

siz

e Ce

ntrif

ugal

Pu

mp

(mm

)

0.01

129

.031

.051

.31.

00-

-62

00

No

reas

onab

le

limita

tion

0.02

230

.933

.557

.51.

12-

-31

00

0.03

333

.036

.262

.61.

22-

-20

67

0.04

435

.339

.167

.21.

31-

-15

50

0.05

537

.942

.371

.31.

39-

-12

40

0.06

640

.545

.575

.91.

48-

-10

33

0.07

743

.248

.780

.11.

56-

-88

6

0.08

846

.052

.084

.71.

65-

-77

5

0.09

948

.855

.489

.31.

74-

-68

9

0.1

1051

.758

.693

.91.

83-

-62

0

0.2

2085

.097

.514

72.

879

15.0

310

20-2

5

0.3

3012

314

120

94.

0712

18.5

207

25-3

2

0.4

4016

318

627

45.

3316

22.2

153

32-4

0

0.5

5020

323

134

06.

6120

26.0

124

40-5

0

0.6

6024

427

740

67.

9024

30.5

103

40-5

0

0.7

7028

432

347

39.

2128

35.0

88.6

50-6

5

0.8

8032

437

055

910

.532

39.5

77.5

50-6

5

0.9

9036

441

660

611

.836

44.0

68.9

50-6

5

Contents3 4

64

sECtIon 21

tEst tolERanCEs anD DIFFEREnt stanDaRDsaPI 610 11th EditionThe following tolerances shall apply: -

• Test speed shall be within ± 3.0% of rated speed shown on pump datasheet, at duty point.

• Rated differential head at duty - 0m to 75m ±3%

75m to 300m - ±3%

Over 300m - ±3%

• Rated differential head shutoff - 0m to 75m - ±10%

75m to 300m - ±8%

Over 300m - ±5%

• Rated Power at duty - +4% (Cumulative tolerances are not acceptable)

• Rated NPSH at duty - +0%

• Efficiency is not a rating value.

note: = If a rising head flow curve is specified, the negative tolerance specified here shall be allowed only if the test curve still shows a rising characteristic.

british standards – (Class C)The following tolerances shall apply at duty flow rate: -

• Rate of flow ± 3.5%

• Pump Total head ± 3.5%

• Pump Input power ± 3.5%

• Pump Efficiency ± 5.0%

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hydraulic Institute test standardsIn making tests under this standard no minus tolerance or margin shall be allowed with respect to capacity, total head or efficiency at the rated or specified conditions.

The following tolerances shall apply:

• At rated head +10% of rated capacity

OR

• At rated capacity +5% of rated head under 500 feet

+3 % of rated head 500 feet and over

Conformity with only one of the above tolerances is required. It should be noted that there might be an increase in horsepower at the rated condition when complying to plus tolerances for head or capacity.

For a fire pump the following tolerances from NFPA 20 shall also apply:

• At 150% of rated capacity, head will range from minimum of 65% to maximum of just below rated head.

• Shutoff head will range from minimum of 101% to maximum of 140% of rated head.

ExceptionIf available suction supplies do not permit the flowing of 150% of rated capacity, the fire pump shall be operated at maximum allowable discharge to determine if it is acceptable. This reduced capacity shall not constitute an unacceptable test.

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Iso 9906:2012 (grade 1) table 10The following tolerances shall apply at duty flow rate: -

• Rate of flow ± 4.5 %• Pump Total head ± 3 %• Pump Efficiency - 3 %• Speed of rotation ± 1 %

Iso 9906:2012 (grade 2) table 10The following tolerances shall apply at duty flow rate: -

• Rate of flow ± 8 %

• Pump Total head ± 5.5 %

• Pump Efficiency - 5 %

• Speed of rotation ± 1 %

Iso 9906:2012 (grade 2) annex a.1 – Pumps produced in series.The following tolerances shall apply at duty flow rate: -


• Pump Total head ± 7 %

• Pump Input Power + 9 %

• Driver Input Power + 9 %

• Pump Efficiency - 7 %

Iso 9906:2012 (grade 2) annex a.2 – Pumps with a driver power input less than 10 kW

The following tolerances shall apply at duty flow rate: -


• Pump Total head ± 8 %

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loss Prevention Council (lPC)The following tolerances shall apply: -


• Pump total head +5 %

• Pump input power within duty rating and/or driver rating + 10%

Underwrites laboratories (Ul) The following tolerances shall apply: -

• At rated head +10% of rated capacity

OR

• At rated capacity +5% of rated head under 500 feet

• At 150% of rated capacity, the pump will develop not less than 65% of rated head.

• The maximum net pressure for a fire pump shall not exceed 140% of rated head.

note: No minus tolerance or margin shall be allowed with respect to capacity, total head or efficiency at the rated or specified conditions.

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VEloCIty hEaD CoRRECtIon

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sECtIon 22 tablEs oF VEloCIty hEaD CoRRECtIon (baR)

Flow (litres/Minute)

Di Dd 1000 1100 1200 1300 1400 1500 1600 1700 1800 1900

50 80 0.305 0.369 0.440 0.516 0.598 0.687 0.782 0.882 0.989 1.102

65 80 0.071 0.086 0.102 0.120 0.139 0.160 0.182 0.206 0.231 0.257

80 100 0.032 0.039 0.047 0.055 0.064 0.073 0.083 0.094 0.105 0.117

80 150 0.051 0.061 0.073 0.085 0.099 0.114 0.129 0.146 0.164 0.182

100 125 0.013 0.016 0.019 0.022 0.026 0.030 0.034 0.038 0.043 0.048

100 150 0.018 0.022 0.026 0.031 0.035 0.041 0.046 0.052 0.059 0.065

100 200 0.021 0.026 0.030 0.036 0.041 0.047 0.054 0.061 0.068 0.076

100 250 0.022 0.027 0.032 0.037 0.043 0.049 0.056 0.063 0.071 0.079

125 150 0.005 0.006 0.007 0.008 0.009 0.011 0.012 0.014 0.015 0.017

125 200 0.008 0.009 0.011 0.013 0.015 0.018 0.020 0.023 0.025 0.028

125 250 0.009 0.010 0.012 0.015 0.017 0.019 0.022 0.025 0.028 0.031

150 175 0.002 0.002 0.003 0.003 0.004 0.005 0.005 0.006 0.007 0.007

150 200 0.003 0.004 0.004 0.005 0.006 0.007 0.008 0.009 0.010 0.011

150 250 0.004 0.005 0.006 0.007 0.008 0.009 0.010 0.011 0.013 0.014

150 300 0.004 0.005 0.006 0.007 0.008 0.009 0.011 0.012 0.014 0.015

175 200 0.001 0.001 0.001 0.002 0.002 0.002 0.003 0.003 0.003 0.004

200 225 0.001 0.001 0.001 0.001 0.001 0.001 0.001 0.002 0.002 0.002

200 250 0.001 0.001 0.001 0.001 0.002 0.002 0.002 0.002 0.003 0.003

200 300 0.001 0.001 0.002 0.002 0.002 0.003 0.003 0.003 0.004 0.004

250 300 0.000 0.000 0.000 0.001 0.001 0.001 0.001 0.001 0.001 0.001

300 350 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000

350 400 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000

Di - Smaller diameter (mm)

Dd - Larger diameter (mm)

Gauge pressure variations, where the flow is from :- the smaller diameter to the larger diameter, then VAR. is POS(+) or, the larger diameter to the smaller diameter, then VAR. is NEG(-)

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Di Dd 2000 2100 2200 2300 2400 2500 2600 2700 2800 2900

50 80 1.2211 1.3463 1.4776 1.6149 1.7584 1.9080 2.0637 2.2255 2.3934 2.5674

65 80 0.2847 0.3138 0.3444 0.3765 0.4099 0.4448 0.4811 0.5188 0.5579 0.5985

80 100 0.1298 0.1431 0.1571 0.1717 0.1869 0.2028 0.2194 0.2366 0.2544 0.2729

80 150 0.2021 0.2228 0.2445 0.2673 0.2910 0.3158 0.3415 0.3683 0.3961 0.4249

100 125 0.0532 0.0586 0.0643 0.0703 0.0766 0.0831 0.0899 0.0969 0.1042 0.1118

100 150 0.0723 0.0797 0.0874 0.0956 0.1041 0.1129 0.1221 0.1317 0.1417 0.1520

100 200 0.0844 0.0931 0.1022 0.1117 0.1216 0.1319 0.1427 0.1539 0.1655 0.1775

100 250 0.0878 0.0968 0.1062 0.1161 0.1264 0.1371 0.1483 0.1599 0.1720 0.1845

125 150 0.0191 0.0211 0.0231 0.0253 0.0275 0.0298 0.0323 0.0348 0.0374 0.0402

125 200 0.0313 0.0345 0.0378 0.0413 0.0450 0.0488 0.0528 0.0570 0.0613 0.0657

125 250 0.0346 0.0381 0.0418 0.0457 0.0498 0.0540 0.0584 0.0630 0.0678 0.0727

150 175 0.0082 0.0090 0.0099 0.0108 0.0118 0.0128 0.0138 0.0149 0.0160 0.0172

150 200 0.0122 0.0134 0.0147 0.0161 0.0175 0.0190 0.0206 0.0222 0.0238 0.0256

150 250 0.0155 0.0171 0.0187 0.0205 0.0223 0.0242 0.0262 0.0282 0.0303 0.0326

150 300 0.0167 0.0184 0.0202 0.0221 0.0240 0.0261 0.0282 0.0304 0.0327 0.0351

175 200 0.0040 0.0044 0.0048 0.0053 0.0057 0.0062 0.0067 0.0072 0.0078 0.0084

200 225 0.0021 0.0023 0.0026 0.0028 0.0030 0.0033 0.0036 0.0039 0.0041 0.0044

200 250 0.0033 0.0037 0.0040 0.0044 0.0048 0.0052 0.0056 0.0061 0.0065 0.0070

200 300 0.0045 0.0050 0.0055 0.0060 0.0065 0.0071 0.0076 0.0082 0.0089 0.0095

250 300 0.0012 0.0013 0.0014 0.0016 0.0017 0.0019 0.0020 0.0022 0.0023 0.0025

300 350 0.0005 0.0006 0.0006 0.0007 0.0007 0.0008 0.0009 0.0009 0.0010 0.0011

350 400 0.0002 0.0003 0.0003 0.0003 0.0004 0.0004 0.0004 0.0005 0.0005 0.0005

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Di Dd 3000 3100 3200 3300 3400 3500 3600 3700 3800 3900

50 80 2.7475 2.9338 3.1261 3.3245 3.5291 3.7397 3.9564 4.1793 4.4083 4.6433

65 80 0.6405 0.6839 0.7287 0.7750 0.8227 0.8718 0.9223 0.9742 1.0276 1.0824

80 100 0.2921 0.3119 0.3323 0.3534 0.3752 0.3976 0.4206 0.4443 0.4686 0.4936

80 150 0.4547 0.4855 0.5174 0.5502 0.5840 0.6189 0.6548 0.6917 0.7295 0.7684

100 125 0.1196 0.1277 0.1361 0.1448 0.1537 0.1628 0.1723 0.1820 0.1920 0.2022

100 150 0.1626 0.1736 0.1850 0.1968 0.2089 0.2213 0.2342 0.2474 0.2609 0.2748

100 200 0.1900 0.2029 0.2162 0.2299 0.2440 0.2586 0.2736 0.2890 0.3048 0.3211

100 250 0.1975 0.2108 0.2247 0.2389 0.2536 0.2688 0.2843 0.3003 0.3168 0.3337

125 150 0.0430 0.0459 0.0489 0.0520 0.0552 0.0585 0.0619 0.0654 0.0689 0.0726

125 200 0.0703 0.0751 0.0800 0.0851 0.0903 0.0957 0.1013 0.1070 0.1129 0.1189

125 250 0.0778 0.0831 0.0885 0.0942 0.0999 0.1059 0.1121 0.1184 0.1248 0.1315

150 175 0.0184 0.0197 0.0210 0.0223 0.0237 0.0251 0.0265 0.0280 0.0296 0.0311

150 200 0.0274 0.0292 0.0311 0.0331 0.0351 0.0372 0.0394 0.0416 0.0439 0.0462

150 250 0.0348 0.0372 0.0396 0.0422 0.0448 0.0474 0.0502 0.0530 0.0559 0.0589

150 300 0.0375 0.0401 0.0427 0.0454 0.0482 0.0511 0.0540 0.0571 0.0602 0.0634

175 200 0.0089 0.0095 0.0102 0.0108 0.0115 0.0122 0.0129 0.0136 0.0143 0.0151

200 225 0.0048 0.0051 0.0054 0.0058 0.0061 0.0065 0.0069 0.0072 0.0076 0.0080

200 250 0.0075 0.0080 0.0085 0.0090 0.0096 0.0102 0.0108 0.0114 0.0120 0.0126

200 300 0.0102 0.0109 0.0116 0.0123 0.0131 0.0138 0.0146 0.0155 0.0163 0.0172

250 300 0.0027 0.0029 0.0031 0.0032 0.0034 0.0037 0.0039 0.0041 0.0043 0.0045

300 350 0.0012 0.0012 0.0013 0.0014 0.0015 0.0016 0.0017 0.0018 0.0018 0.0019

350 400 0.0006 0.0006 0.0006 0.0007 0.0007 0.0008 0.0008 0.0009 0.0009 0.0009




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Di Dd 4000 4100 4200 4300 4400 4500 4600 4700 4800 4900

50 80 4.8845 5.1318 5.3852 5.6447 5.9102 6.1820 6.4598 6.7437 7.0337 7.3298

65 80 1.1386 1.1963 1.2553 1.3158 1.3777 1.4411 1.5058 1.5720 1.6396 1.7086

80 100 0.5193 0.5456 0.5725 0.6001 0.6283 0.6572 0.6867 0.7169 0.7477 0.7792

80 150 0.8084 0.8493 0.8912 0.9342 0.9781 1.0231 1.0691 1.1160 1.1640 1.2130

100 125 0.2127 0.2235 0.2345 0.2458 0.2574 0.2692 0.2813 0.2936 0.3063 0.3192

100 150 0.2891 0.3037 0.3187 0.3341 0.3498 0.3659 0.3823 0.3991 0.4163 0.4338

100 200 0.3377 0.3548 0.3724 0.3903 0.4087 0.4274 0.4467 0.4663 0.4863 0.5068

100 250 0.3510 0.3688 0.3870 0.4057 0.4247 0.4443 0.4642 0.4846 0.5055 0.5268

125 150 0.0764 0.0803 0.0842 0.0883 0.0924 0.0967 0.1010 0.1055 0.1100 0.1146

125 200 0.1250 0.1314 0.1379 0.1445 0.1513 0.1583 0.1654 0.1726 0.1801 0.1876

125 250 0.1383 0.1453 0.1525 0.1599 0.1674 0.1751 0.1830 0.1910 0.1992 0.2076

150 175 0.0327 0.0344 0.0361 0.0378 0.0396 0.0414 0.0433 0.0452 0.0472 0.0491

150 200 0.0486 0.0511 0.0536 0.0562 0.0589 0.0616 0.0643 0.0672 0.0700 0.0730

150 250 0.0619 0.0651 0.0683 0.0716 0.0749 0.0784 0.0819 0.0855 0.0892 0.0929

150 300 0.0667 0.0701 0.0736 0.0771 0.0807 0.0844 0.0882 0.0921 0.0961 0.1001

175 200 0.0159 0.0167 0.0175 0.0184 0.0192 0.0201 0.0210 0.0219 0.0229 0.0239

200 225 0.0085 0.0089 0.0093 0.0098 0.0102 0.0107 0.0112 0.0117 0.0122 0.0127

200 250 0.0133 0.0140 0.0147 0.0154 0.0161 0.0168 0.0176 0.0184 0.0191 0.0199

200 300 0.0181 0.0190 0.0199 0.0209 0.0219 0.0229 0.0239 0.0249 0.0260 0.0271

250 300 0.0048 0.0050 0.0053 0.0055 0.0058 0.0060 0.0063 0.0066 0.0069 0.0072

300 350 0.0020 0.0022 0.0023 0.0024 0.0025 0.0026 0.0027 0.0028 0.0029 0.0031

350 400 0.0010 0.0010 0.0011 0.0011 0.0012 0.0013 0.0013 0.0014 0.0014 0.0015

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Di Dd 5000 5100 5200 5300 5400 5500 5600 5700 5800 5900

50 80 7.6320 7.9404 8.2548 8.5754 8.9020 9.2348 9.5736 9.9186 10.2697 10.6268

65 80 1.7791 1.8510 1.9243 1.9990 2.0751 2.1527 2.2317 2.3121 2.3940 2.4772

80 100 0.8114 0.8441 0.8776 0.9116 0.9464 0.9817 1.0178 1.0544 1.0918 1.1297

80 150 1.2631 1.3141 1.3661 1.4192 1.4732 1.5283 1.5844 1.6415 1.6996 1.7587

100 125 0.3323 0.3458 0.3595 0.3734 0.3876 0.4021 0.4169 0.4319 0.4472 0.4627

100 150 0.4517 0.4700 0.4886 0.5075 0.5269 0.5466 0.5666 0.5870 0.6078 0.6290

100 200 0.5277 0.5490 0.5708 0.5929 0.6155 0.6385 0.6620 0.6858 0.7101 0.7348

100 250 0.5485 0.5706 0.5932 0.6163 0.6398 0.6637 0.6880 0.7128 0.7380 0.7637

125 150 0.1194 0.1242 0.1291 0.1341 0.1392 0.1444 0.1497 0.1551 0.1606 0.1662

125 200 0.1954 0.2033 0.2113 0.2195 0.2279 0.2364 0.2451 0.2539 0.2629 0.2720

125 250 0.2162 0.2249 0.2338 0.2429 0.2521 0.2615 0.2711 0.2809 0.2909 0.3010

150 175 0.0512 0.0532 0.0553 0.0575 0.0597 0.0619 0.0642 0.0665 0.0689 0.0713

150 200 0.0760 0.0791 0.0822 0.0854 0.0887 0.0920 0.0953 0.0988 0.1023 0.1058

150 250 0.0968 0.1007 0.1047 0.1087 0.1129 0.1171 0.1214 0.1258 0.1302 0.1348

150 300 0.1042 0.1085 0.1127 0.1171 0.1216 0.1261 0.1308 0.1355 0.1403 0.1451

175 200 0.0248 0.0258 0.0269 0.0279 0.0290 0.0301 0.0312 0.0323 0.0334 0.0346

200 225 0.0132 0.0138 0.0143 0.0149 0.0154 0.0160 0.0166 0.0172 0.0178 0.0184

200 250 0.0208 0.0216 0.0225 0.0233 0.0242 0.0251 0.0261 0.0270 0.0279 0.0289

200 300 0.0282 0.0294 0.0305 0.0317 0.0329 0.0342 0.0354 0.0367 0.0380 0.0393

250 300 0.0075 0.0078 0.0081 0.0084 0.0087 0.0090 0.0094 0.0097 0.0100 0.0104

300 350 0.0032 0.0033 0.0035 0.0036 0.0037 0.0039 0.0040 0.0042 0.0043 0.0045

350 400 0.0016 0.0016 0.0017 0.0017 0.0018 0.0019 0.0019 0.0020 0.0021 0.0022




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Di Dd 6000 6100 6200 6300 6400 6500 6600 6700 6800 6900

50 80 10.9901 11.3595 11.7350 12.1166 12.5043 12.8981 13.2981 13.7041 14.1162 14.5345

65 80 2.5619 2.6480 2.7355 2.8245 2.9149 3.0067 3.0999 3.1946 3.2906 3.3881

80 100 1.1684 1.2076 1.2475 1.2881 1.3293 1.3712 1.4137 1.4569 1.5007 1.5451

80 150 1.8188 1.8799 1.9421 2.0052 2.0694 2.1346 2.2008 2.2680 2.3362 2.4054

100 125 0.4786 0.4946 0.5110 0.5276 0.5445 0.5616 0.5791 0.5967 0.6147 0.6329

100 150 0.6505 0.6723 0.6945 0.7171 0.7401 0.7634 0.7870 0.8111 0.8355 0.8602

100 200 0.7599 0.7854 0.8114 0.8378 0.8646 0.8918 0.9195 0.9476 0.9761 1.0050

100 250 0.7898 0.8164 0.8433 0.8708 0.8986 0.9269 0.9557 0.9849 1.0145 1.0445

125 150 0.1719 0.1777 0.1835 0.1895 0.1956 0.2017 0.2080 0.2143 0.2208 0.2273

125 200 0.2813 0.2908 0.3004 0.3102 0.3201 0.3302 0.3404 0.3508 0.3614 0.3721

125 250 0.3113 0.3217 0.3324 0.3432 0.3541 0.3653 0.3766 0.3881 0.3998 0.4116

150 175 0.0737 0.0762 0.0787 0.0812 0.0838 0.0865 0.0892 0.0919 0.0946 0.0975

150 200 0.1095 0.1131 0.1169 0.1207 0.1245 0.1285 0.1324 0.1365 0.1406 0.1447

150 250 0.1394 0.1440 0.1488 0.1536 0.1586 0.1636 0.1686 0.1738 0.1790 0.1843

150 300 0.1501 0.1551 0.1603 0.1655 0.1708 0.1762 0.1816 0.1872 0.1928 0.1985

175 200 0.0358 0.0370 0.0382 0.0394 0.0407 0.0420 0.0433 0.0446 0.0459 0.0473

200 225 0.0190 0.0197 0.0203 0.0210 0.0217 0.0223 0.0230 0.0237 0.0244 0.0252

200 250 0.0299 0.0309 0.0319 0.0330 0.0340 0.0351 0.0362 0.0373 0.0384 0.0396

200 300 0.0407 0.0420 0.0434 0.0448 0.0463 0.0477 0.0492 0.0507 0.0522 0.0538

250 300 0.0107 0.0111 0.0115 0.0118 0.0122 0.0126 0.0130 0.0134 0.0138 0.0142

300 350 0.0046 0.0048 0.0049 0.0051 0.0052 0.0054 0.0056 0.0057 0.0059 0.0061

350 400 0.0022 0.0023 0.0024 0.0025 0.0025 0.0026 0.0027 0.0028 0.0029 0.0030

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Di Dd 7000 7100 7200 7300 7400 7500 7600 7700 7800 7900

50 80 14.9588 15.3892 15.8258 16.2685 16.7172 17.1721 17.6331 18.1001 18.5733 19.0526

65 80 3.4870 3.5874 3.6891 3.7923 3.8969 4.0030 4.1104 4.2193 4.3296 4.4413

80 100 1.5903 1.6360 1.6824 1.7295 1.7772 1.8256 1.8746 1.9242 1.9745 2.0255

80 150 2.4756 2.5468 2.6191 2.6923 2.7666 2.8419 2.9182 2.9955 3.0738 3.1531

100 125 0.6514 0.6701 0.6891 0.7084 0.7279 0.7477 0.7678 0.7882 0.8088 0.8296

100 150 0.8853 0.9108 0.9367 0.9629 0.9894 1.0163 1.0436 1.0713 1.0993 1.1276

100 200 1.0343 1.0641 1.0943 1.1249 1.1559 1.1874 1.2192 1.2515 1.2842 1.3174

100 250 1.0750 1.1060 1.1373 1.1691 1.2014 1.2341 1.2672 1.3008 1.3348 1.3692

125 150 0.2340 0.2407 0.2475 0.2545 0.2615 0.2686 0.2758 0.2831 0.2905 0.2980

125 200 0.3829 0.3940 0.4051 0.4165 0.4280 0.4396 0.4514 0.4634 0.4755 0.4877

125 250 0.4237 0.4358 0.4482 0.4607 0.4735 0.4863 0.4994 0.5126 0.5260 0.5396

150 175 0.1003 0.1032 0.1061 0.1091 0.1121 0.1151 0.1182 0.1214 0.1245 0.1277

150 200 0.1490 0.1533 0.1576 0.1620 0.1665 0.1710 0.1756 0.1803 0.1850 0.1897

150 250 0.1897 0.1951 0.2007 0.2063 0.2120 0.2178 0.2236 0.2295 0.2355 0.2416

150 300 0.2043 0.2102 0.2162 0.2222 0.2283 0.2345 0.2408 0.2472 0.2537 0.2602

175 200 0.0487 0.0501 0.0515 0.0529 0.0544 0.0559 0.0574 0.0589 0.0604 0.0620

200 225 0.0259 0.0267 0.0274 0.0282 0.0290 0.0297 0.0305 0.0313 0.0322 0.0330

200 250 0.0407 0.0419 0.0431 0.0443 0.0455 0.0467 0.0480 0.0493 0.0505 0.0519

200 300 0.0553 0.0569 0.0585 0.0602 0.0618 0.0635 0.0652 0.0670 0.0687 0.0705

250 300 0.0146 0.0150 0.0155 0.0159 0.0163 0.0168 0.0172 0.0177 0.0182 0.0186

300 350 0.0063 0.0064 0.0066 0.0068 0.0070 0.0072 0.0074 0.0076 0.0078 0.0080

350 400 0.0030 0.0031 0.0032 0.0033 0.0034 0.0035 0.0036 0.0037 0.0038 0.0039




Contents3 4

77


Di Dd 8000 8100 8200 8300 8400 8500 8600 8700 8800 8900

50 80 19.5380 20.0295 20.5271 21.0308 21.5407 22.0566 22.5786 23.1068 23.6410 24.1813

65 80 4.5545 4.6691 4.7851 4.9025 5.0213 5.1416 5.2633 5.3864 5.5109 5.6369

80 100 2.0771 2.1293 2.1822 2.2358 2.2900 2.3448 2.4003 2.4565 2.5133 2.5707

80 150 3.2334 3.3148 3.3971 3.4805 3.5649 3.6502 3.7366 3.8240 3.9125 4.0019

100 125 0.8508 0.8722 0.8938 0.9158 0.9380 0.9604 0.9832 1.0062 1.0294 1.0530

100 150 1.1564 1.1855 1.2149 1.2447 1.2749 1.3054 1.3363 1.3676 1.3992 1.4312

100 200 1.3509 1.3849 1.4193 1.4542 1.4894 1.5251 1.5612 1.5977 1.6346 1.6720

100 250 1.4041 1.4394 1.4752 1.5114 1.5480 1.5851 1.6226 1.6606 1.6990 1.7378

125 150 0.3056 0.3133 0.3211 0.3289 0.3369 0.3450 0.3532 0.3614 0.3698 0.3782

125 200 0.5002 0.5128 0.5255 0.5384 0.5514 0.5646 0.5780 0.5915 0.6052 0.6190

125 250 0.5533 0.5673 0.5814 0.5956 0.6101 0.6247 0.6395 0.6544 0.6695 0.6849

150 175 0.1310 0.1343 0.1376 0.1410 0.1444 0.1479 0.1514 0.1549 0.1585 0.1621

150 200 0.1946 0.1995 0.2044 0.2094 0.2145 0.2197 0.2249 0.2301 0.2354 0.2408

150 250 0.2478 0.2540 0.2603 0.2667 0.2731 0.2797 0.2863 0.2930 0.2998 0.3066

150 300 0.2669 0.2736 0.2804 0.2872 0.2942 0.3013 0.3084 0.3156 0.3229 0.3303

175 200 0.0636 0.0652 0.0668 0.0684 0.0701 0.0718 0.0735 0.0752 0.0769 0.0787

200 225 0.0338 0.0347 0.0356 0.0364 0.0373 0.0382 0.0391 0.0400 0.0409 0.0419

200 250 0.0532 0.0545 0.0559 0.0572 0.0586 0.0600 0.0614 0.0629 0.0643 0.0658

200 300 0.0723 0.0741 0.0759 0.0778 0.0797 0.0816 0.0835 0.0855 0.0874 0.0894

250 300 0.0191 0.0196 0.0201 0.0206 0.0211 0.0216 0.0221 0.0226 0.0231 0.0236

300 350 0.0082 0.0084 0.0086 0.0088 0.0090 0.0092 0.0095 0.0097 0.0099 0.0101

350 400 0.0040 0.0041 0.0042 0.0043 0.0044 0.0045 0.0046 0.0047 0.0048 0.0049

seCtiON 22


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78


Di Dd 9000 9100 9200 9300 9400 9500 9600 9700 9800 9900

50 80 24.7278 25.2804 25.8390 26.4038 26.9747 27.5517 28.1347 28.7239 29.3192 29.9206

65 80 5.7643 5.8931 6.0233 6.1550 6.2881 6.4226 6.5585 6.6958 6.8346 6.9748

80 100 2.6288 2.6875 2.7469 2.8070 2.8677 2.9290 2.9910 3.0536 3.1169 3.1808

80 150 4.0923 4.1838 4.2762 4.3697 4.4642 4.5597 4.6562 4.7537 4.8522 4.9517

100 125 1.0768 1.1008 1.1251 1.1497 1.1746 1.1997 1.2251 1.2508 1.2767 1.3029

100 150 1.4635 1.4962 1.5293 1.5627 1.5965 1.6307 1.6652 1.7000 1.7353 1.7709

100 200 1.7098 1.7480 1.7866 1.8257 1.8651 1.9050 1.9454 1.9861 2.0273 2.0688

100 250 1.7771 1.8168 1.8569 1.8975 1.9386 1.9800 2.0219 2.0643 2.1071 2.1503

125 150 0.3868 0.3954 0.4041 0.4130 0.4219 0.4309 0.4401 0.4493 0.4586 0.4680

125 200 0.6330 0.6472 0.6615 0.6759 0.6906 0.7053 0.7202 0.7353 0.7506 0.7660

125 250 0.7003 0.7160 0.7318 0.7478 0.7640 0.7803 0.7968 0.8135 0.8304 0.8474

150 175 0.1658 0.1695 0.1732 0.1770 0.1809 0.1847 0.1886 0.1926 0.1966 0.2006

150 200 0.2463 0.2518 0.2573 0.2630 0.2686 0.2744 0.2802 0.2861 0.2920 0.2980

150 250 0.3136 0.3206 0.3277 0.3348 0.3421 0.3494 0.3568 0.3642 0.3718 0.3794

150 300 0.3377 0.3453 0.3529 0.3606 0.3684 0.3763 0.3843 0.3923 0.4004 0.4087

175 200 0.0805 0.0823 0.0841 0.0859 0.0878 0.0897 0.0916 0.0935 0.0954 0.0974

200 225 0.0428 0.0438 0.0447 0.0457 0.0467 0.0477 0.0487 0.0497 0.0508 0.0518

200 250 0.0673 0.0688 0.0703 0.0719 0.0734 0.0750 0.0766 0.0782 0.0798 0.0814

200 300 0.0915 0.0935 0.0956 0.0977 0.0998 0.1019 0.1041 0.1063 0.1085 0.1107

250 300 0.0242 0.0247 0.0253 0.0258 0.0264 0.0269 0.0275 0.0281 0.0287 0.0292

300 350 0.0104 0.0106 0.0108 0.0111 0.0113 0.0115 0.0118 0.0120 0.0123 0.0125

350 400 0.0050 0.0051 0.0053 0.0054 0.0055 0.0056 0.0057 0.0058 0.0060 0.0061





Contents3 4

79

ElECtRCal DEsIgn Data

Contents3 4

80

sECtIon 23

aVERagE EFFICIEnCIEs anD PoWER FaCtoRs oF ElECtRIC MotoRs

note: Power factors are of importance where the current is charged on a kVA basis. The power factors of motors may be improved by the use of a suitable condenser. To find the output kw of motors when Current, Efficiency and Power Factor (PF) are known.

Direct Current kW = volts x amps x eff %

1000 x 100

alternating Current single phase – kW = volts x amps x eff % x PF

1000 x 100

Efficiency % typical PF

kW 2 Pole 4 Pole 6 Pole Full load ¾ load ½ load

0.75 77.4 79.6 79.6 0.75 0.69 0.56

1.1 79.6 81.4 78.1 0.77 0.71 0.59

1.5 81.3 82.8 79.8 0.77 0.71 0.59

3 84.5 85.5 83.3 0.82 0.77 0.67

5.5 87 87.7 86 0.82 0.77 0.67

7.5 81.1 88.7 87.2 0.84 0.8 0.71

11 89.4 89.8 88.7 0.84 0.8 0.71

18.5 90.9 91.2 90.4 0.84 0.8 0.71

22 91.3 91.6 90.9 0.84 0.8 0.71

30 92 93.2 91.7 0.84 0.8 0.71

37 92.5 92.7 92.2 0.86 0.83 0.75

45 92.9 93.1 92.7 0.86 0.83 0.75

55 93.2 93.5 93.1 0.86 0.83 0.75

75 93.8 94 93.7 0.86 0.83 0.75

90 94 94.2 94 0.86 0.83 0.75

110 94.3 94.5 94.3 0.86 0.83 0.75

132 94.6 94.7 94.6 0.87 0.84 0.76

Contents3 4

81

three phase – kW = volts x amps x eff % x PF x 1.73

1000 x 100

Kilowatt consumption of any motor

= Output kW x 100

eff %

To find amperes to be carried by cable connections to a motor when output kW, Volts, Efficiency and Power Factor (PF) are known.

Direct current

amps

= kW x 1000 x 100

volts x eff %

Alternating current

Single phase amps

= kW x 1000 x 100

volts x eff % x PF

Three phase, amps per phase

= kW x 1000 x 100

volts x eff % x PF x 1.73

seCtiON 23

ElECtRICal DEsIgn Data

Contents3 4

82

sECtIon 24

aPPRoxIMatE FUll loaD sPEEDs (RPM) oF altERnatIngCURREnt MotoRs

FrequencykW no of poles 25 30 40 50 60

0.75

to

2.2

2 Pole 1430 1716 2288 2860 3432

4 Pole 720 864 1152 1440 1728

6 Pole 475 570 760 950 1140

3

to

7.5

2 Pole 1450 1740 2320 2900 3480

4 Pole 720 864 1152 1440 1728

6 Pole 480 576 768 960 1152

11

to

22

2 Pole 1472.5 1767 2356 2945 3534

4 Pole 730 876 1168 1460 1752

6 Pole 485 582 776 970 1164

30

to

75

2 Pole 1485 1782 2376 2970 3564

4 Pole 740 888 1184 1480 1776

6 Pole 495 594 792 990 1188

Contents3 4

83

sECtIon 25

staRtIng altERnatIng CURREnt MotoRssquirrel Cage Motors

The above figures apply to Squirrel Cage motors of normal design and other types are available namely:

High torque Squirrel Cage machines will give approximately twice the above starting torques with unrestricted currents.

Low current Squirrel Cage machines restrict the current but give a lower starting torque than the high torque machines. These two types can now be used in many cases where slipring machines would have been necessary in the past.

Slipring machines (2- and 3-phase). All slipring machines must be started by means of a rotor resistance starter. A starting torque of full load torque is obtainable with a starting current of approximately 1 ¼ full load current, this usually being sanctioned by supply authorities for any size of motor.

Method of starting starting torque (approx) %

Full load torque

starting current (approx) %

Full load current

Direct 100% - 200% 350% - 700%

star delta (3 phase) 33% - 66% 120% - 230%

series parallel (2 phase) 25% - 50% 90% - 175%

auto transformer 25% - 85% 90% - 300%

seCtiON 24/25

ElECtRICal DEsIgn Data

Contents3 4

84 Contents3 4

85

WholE lIFE Cost

WholE lIFE Cost

Contents3 4

86

sECtIon 26

WholE lIFE Cost PRInCIPlEs anD PUMP DEsIgnWhole life cost can be broken down into a number of key components:

• Initial Capital Cost

• Operating/Energy Costs

• Replacement/Wear Part Costs

• Maintenance & Repair Costs

• Disposal Costs.

Initial Capital CostCapital cost is the most visible cost and has historically been the primary selection criterion for most items of capital equipment. Pump users are now becoming increasingly aware of post installation costs and their impact on the total cost of ownership. Lowest capital cost purchases rarely prove economic in the longer term and given that the initial capital cost of a centrifugal pump, inclusive of installation, typically equates to between 5%-20% of whole life cost, placing more emphasis on post installation cost will clearly prove much more economic.

operating/Energy CostsEnergy costs can easily equate to as much as 90% of the whole life cost of a pumping installation, dependant on installed power and equipment utilisation.

Analysis of operating costs, in terms of energy consumption, is relatively straightforward, given that pump utilisation and demand profiles are understood and predictable. The wire to water efficiency of existing or proposed installations can be compared and the results projected over the estimated lifetime of the installation. This should be a fundamental component of any tender assessment process or existing asset review procedure.

Less visible however, is an installations’ capacity to operate at or near optimum efficiency throughout its operational life. A degree of degradation in hydraulic performance is inevitable with time. This degradation in performance is primarily a result of wear and erosion of internal clearances. Wear rings limit fluid re-circulation between the high and low-pressure

Contents3 4

87

areas within a centrifugal pump. A combination of erosion from high velocity fluid passing between the wear ring surfaces and mechanical wear, resultant from shaft deflection, widens the clearances allowing an increase in internal re-circulation. Significantly, highlighting the importance of optimum pump selection, this process will be accelerated if the pump operates at a duty point less than 70% or more than 115% of best efficiency flow. The resultant loss of performance usually leads to the pump running for longer periods to deliver a given quantity of fluid.

Erosion of hydraulic profiles and increases in the relative roughness of surfaces in contact with the pumped fluid, will also significantly impact on pump performance.

Replacement/Wear Part Costs The replacement of major components within a pump, whether as a result of wear, erosion or following a component failure is often a very significant contributor to whole life costs. A replacement rotating assembly will typically equate to 70% of the costs of a replacement pump. It is not uncommon for all components forming the rotating assembly to require replacement within the lifetime of an installation. The selection of a conservatively engineered pump, manufactured from high-grade materials should negate this, substantially reducing maintenance costs and increasing the mean time between failure and major service outages. Parts supplied by the original pump manufacturers are likely to provide the highest levels of compatibility and will include any reliability modifications that have been developed since the original date of manufacture. SPP’s parts division provides a comprehensive section of spares for SPP and Crane pumps. We can also provide a wide range of re-engineered parts for other manufacturers’ pumps.

Maintenance & Repair CostsThe cost of regular monitoring and preventative maintenance is a necessary component of an installations’ whole life cost and historical evidence shows that regular maintenance is a lower cost option than unplanned emergency repairs. When calculating the cost of maintenance, installation downtime and resultant loss of productivity should be considered. Savings associated with increased mean time between failure and service outages will offset any higher initial capital costs incurred when installing a well-engineered pump, designed for ease of maintenance. SPP’s service division can provide a range

seCtiON 26

WholE lIFE Costs

Contents3 4

88

of field and service centre based preventative maintenance programmes to support our customers’ production and shut-down schedules. These can vary between simple annual or biannual site based maintenance through to planned pump and valve swap-out programmes to support maximum plant uptime.

A well-engineered installation should be so designed as to offer good bearing and seal life and facilitate all but a major overhaul in-situ, without recourse to disturb either pipework or prime movers.

Disposal CostsDisposal costs are relatively minor. Use of higher grade materials may enhance recycling value but this is minimal in the pumps whole life cost and is normally ignored.

FEatUREs oF a loW lIFE-CyClE Cost CEntRIFUgal PUMPThe majority of pumps employed on utility type applications fall into one of the following categories: Horizontal Split Casing, Vertical Suspended Bowl or End Suction Pumps. Only the latter are regularly manufactured to recognised international standards e.g. ISO 5199. The requirement for low life-cycle cost pumps is generally applicable to pumps with branch sizes 150mm and above, where power requirements are higher, so it is not usually relevant to the majority of End Suction Pump applications.

The following key areas have been identified by pump end users and designers in relation to low life-cycle cost applications.

Mechanical DesignA significant change has taken place over the last decade in that the switch from soft packed glands to mechanical seals for shaft sealing on utility applications is near universal. The benefits of this change however have not been fully realised, as mechanical seal life is generally proportional to certain key aspects of pump performance, not least shaft deflection, vibration levels and seal chamber design. The vast majority of utility pumps available today have their design roots in the packed gland era. In many instances this is leading to premature bearing and seal failures, as many pump shafts are quite simply too flexible without the support of numerous packing rings and neck bushes.

Contents3 4

89

This is arguably the most significant factor, influencing the mean time between failures of utility pumps. Mechanical seals and bearings are intolerant of shaft deflection and residual unbalance. Therefore it is suggested that a pump designed for low life-cycle cost would have a shorter span between bearings and an increased shaft diameter when compared to a similar pump designed in the packed gland era. Specifically shafts should be so designed, as to limit shaft deflection at the limits of the operating range of say, 50% - 115% of best efficiency flow, to a maximum of 0.05mm at the seal faces. Bearings likewise should be designed to provide a minimum L10 life of 50,000 hours at these limits.

hydraulic DesignWith the aid of 3-Dimensional Computational Fluid Dynamics, pump manufacturers are now able to produce hydraulic designs that achieve the theoretical maximum efficiency for a given specific speed or impeller geometry. The challenge is then to consistently replicate these designs in material form. High quality manufacturing techniques and procedures are therefore essential, particularly as pump casings and impellers (the most dimensionally critical components of any centrifugal pump) tend to be produced as castings. Only foundry techniques that ensure a high standard of dimensional accuracy and surface finish should be employed in low life-cycle cost pump production.

Efficiency DegradationThe maximum benefit of installing an energy efficient machine will only be realised if performance levels can be maintained for long periods of time between overhauls. Performance degradation is inevitable, however a combination of good hydraulic and mechanical design can have a positive impact in this area and prolong optimum efficiency for much longer periods of time.

Hydraulic design considerations are:

• Maintenance of optimum clearances between the impeller outside diameter and the volute cut-water, which will avoid vane pass cavitation.

• Optimisation of impeller geometry with satisfactory suction specific speed values, this will limit internal re-circulation and facilitate a wide band of operation (30%-115% of best efficiency flow).

seCtiON 26

WholE lIFE Costs

Contents3 4

90

• Application of internal hydrophobic coating (low electronic affinity) in order to reduce the relative surface roughness value of the pump casing; thus maintaining the relative surface roughness values at a more constant level, unlike that of a bare metal casing, which will oxidise once put into service immediately impacting on hydraulic performance.

Mechanical design considerations• Minimisation of shaft deflection will ensure no contact between impeller

eye ring and sealing/wear rings surfaces, thus maintaining ‘as new’ clearances for longer periods.

• Often overlooked but highly important is wear ring design. A labyrinth profile will help to provide a staged pressure drop across the wear ring, rather than simply allowing high velocity fluid to flow across wear ring faces rapidly eroding internal clearances.

• High-grade materials of construction for the pump impeller with good erosion/corrosion properties will ensure that the relative roughness of hydraulic surfaces remain reasonably smooth throughout.

PaCKagIng thE PUMPsEtWhen packaging a low life-cycle cost pump with a suitable prime mover, it is important to ensure that the same fundamental design principles be applied to the prime mover, baseplate/mounting assembly.

The benefits of a superior hydraulic design and first class component quality can easily be forfeited by coupling the highly efficient pump to a lower efficiency driver. Likewise bearing and seal design lives will not be realised if the pump and driver are connected via a flexible and inadequate baseplate or mounting frame.

The mounting arrangement as well as being rigid should facilitate a high degree of in-situ maintenance. Mechanical seals and bearings should be accessible without recourse to disturb either driver alignment of connecting pipework. This dictates the use of spacer type couplings, if drive end bearings and seals are to be maintainable in-situ.

Only through the application of all these design and packaging principles will the true benefits of Low Life-cycle Cost pumping be realised by the end user.

Contents3 4

91

EnERgy

EnERgy

Contents3 4

92

sECtIon 27

sPP EnERgy – EnERgy saVIng sERVICEsPumps are the single largest user of motive power in both industrial and commercial applications in the UK, accounting for over 30% of total power consumption within these sectors.

Pumps account for approximately 13% of the UK’s total annual electrical consumption (BPMA Data) and energy consumption during operation has been identified as the most significant impact of pumps on the environment. In recent years, energy costs have become volatile with Oil, Gas and Coal prices at record levels. With this in mind, SPP has identified the need to operate pump systems more efficiently, and can realistically offer reductions in energy consumption and running costs by 30 to 50%.

saving Costs, saving Energy, saving the EnvironmentIt is estimated that over 11 million motors with a total capacity of 90 GW are installed in UK industry – which represents about 40% of the UK’s total electricity consumption. With pumps contributing nearly a third of this consumption, there is considerable scope to reduce carbon emissions by improving pump system efficiency.

SPP Energy Division promotes the benefits of auditing complete pump systems and producing recommendations to minimise the energy consumption of pumps and their associated systems. SPP Energy Division can also if required supply many of the solutions capable of realising these savings coupled with ongoing monitoring to validate such savings and sustain them through the lifetime of the installation.

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93

savings through innovationThrough the use of proven systems and techniques, SPP Energy offers a complete energy saving solution for pumping systems that can be applied equally to new projects and existing installations.

It is clear that pump systems are heavy users of energy, especially large pumps that run continuously. Such pumps are generally oversized and operating far from their best efficiency points. They can suffer from poor pump intake conditions and inefficient running regimes - all wasting considerable amounts of energy. In order to save costs SPP Energy Division will undertake site audits focused on complete pump systems, ultimately producing a detailed report making recommendations for corrective action and clearly showing cost savings, kW/Hr savings, payback time and CO2 reduction.

0 50 100 150 200 250 300 350 400 450 500 550

0

System Power - kW

2000

4000

6000

8000

10000

12000

14000

16000

18000

20000

Annual C02 Savings Per 1% Efficiency Improvement

C0 2

Em

issi

ons

Sav

ing

s -

kg

C02 emissions 8277.5 kg C02

Savings per year

Energy Cost 0.43 kg C02/kWhAbsorbed Power 220 kWHours run per year 8750 hrs

20000 miles family car

Round the world flight

00

50 100 150 200 250 300 350 400 450 500 550

Power absorbed - kW

3500

3000

2500

2000

1500

1000

500

Annual Savings Per 1% Efficiency Improvement

Ann

ual s

avin

g £

Energy Cost 7 p/kWhAbsorbed Power 220 kWHours run per year 8750 hrs

Saving per year £1,347.50

seCtiON 27

EnERgy

Contents3 4

94

services offered by sPP Energy include:a. Site Survey/Audit (including equipment and operating regime)

b. Analysis by accredited engineers with Report (which will include recomendations for efficiency improvements)

c. Solutions – eg: • Upgrade/ refurbish/replace pumps • Training • Operational recommendations • Computational Fluid Dynamics (CFD) • System Modelling

d. Sustained improvements through Lowest Life Cycle cost

e. Monitoring and Review • Intrusive measurement (Thermodynamic) • Individual parameter measurement (Non intrusive - Ultrasonic) • Permanent or temporary installations • Pump and system performance log

f. Pump Systems Management Contracts.

sPP Energy – accreditationThe SPP Energy Team is certified and accredited in the use of Pump System Analysis Testing (PSAT) and Competent Pump System Assessor (CPSA) – working to globally recognised standards set within the Europe and the US.

The team also operates within guidelines set by: • Government Legislation • BPMA • Carbon Trust • ISO BS EN etc • Insurance assessors – such as Lloyds, Beauro Veritas, LPC, CEMARS, Achillies etc.

www.sppenergy.com

Contents3 4

95

EnERgy

ConVERsIonFaCtoRs

Contents3 4

96

Impe

rial t

o M

etric

Met

ric to

Impe

rial

Num

ber o

fNu

mbe

r of

Num

ber o

f

inch

esx

25.4

=m

mx

0.03

937

=in

ches

inch

esx

0.02

54=

mx

39.3

7=

inch

es

feet

x30

4.8

=m

mx

0.00

328

=fe

et

feet

x0.

3048

=m

x3.

281

=fe

et

yard

sx

0.91

44=

mx

1.09

36=

yard

s

mile

sx

1.60

9=

kmx

0.62

14=

mile

s

in2

x64

5.16

=m

m2

x0.

0015

5=

in2

ft2x

0.09

29=

m2

x10

.764

=ft2

yds2

x0.

836

=m

2x

1.19

6=

yds2

acre

sx

0.40

47=

hax

2.47

1=

acre

s

mile

s2x

2.59

=km

2x

0.38

61=

mile

s2

in3

x16

387

=m

m3

x0.

0000

61=

in3

ft3x

28.3

2=

litx

0.03

53=

ft3

ft3x

0.02

832

=m

3x

35.3

1=

ft3

gals

(Im

p)x

4.54

6=

litx

0.22

00=

gals

(Im

p)

gals

(Im

p)x

0.00

4546

=m

3x

220

=ga

ls (I

mp)

gals

(US)

x3.

785

=lit

x0.

2642

=ga

ls (U

S)

gals

(US)

x0.

0037

85=

m3

x26

4.2

=ga

ls (U

S)

acre

-inch

esx

1.02

8=

ha-c

mx

0.97

3=

acre

-inch

es

ha-c

mx

100

=m

3x

0.01

=ha

-cm

x 1

0000

0 =

lit

bbls

(oil)

x15

9=

litx

0.00

63=

bbls

bbls

(oil)

x0.

159

=m

3x

6.29

7=

bbls

lbs

x0.

4536

=kg

x2.

2046

=lb

s

long

tonn

e (Im

p)x

1016

=kg

x0.

0009

84=

tonn

e (m

etric

)

gal /

min

x0.

2727

=m

3 / h

x3.

667

=ga

l / m

in

sECtIon 28

ConVERsIon FaCtoRs

Contents3 4

97

1000

gal

s / h

x1.

263

=l /

sx

0.79

2=

1000

gal

s / h

mgd

x52

.61

=l /

sx

0.01

90=

mgd

cuse

csx

28.3

2=

l / s

x0.

0353

=cu

secs

cum

ins

x0.

472

=l /

sx

2.11

9=

cum

ins

barr

els

/ h (b

ph)

x0.

0441

6=

l / s

x22

.65

=bp

h

1000

bpd

x1.

04=

l / s

x0.

5345

=10

00 b

pd

1000

lb /

hx

0.12

653

/ s.g

.=

l / s

x7.

903

x s.

g.=

1000

lb /

h

tonn

es /

hx

0.28

34 /

s.g.

=l /

sx

3.52

8 x

s.g.

=to

nnes

/ h

tons

/ m

inx

17.0

0 / s

.g.

=l /

sx

0.05

88 x

s.g

.=

tons

/ m

in

m3 /

hr

x0.

2778

=l /

sx

3.6

=m

3 / h

r

p.s.

i.x

0.06

895

=ba

rx

14.5

04=

p.s.

i.

p.s.

i.x

0.07

03=

kg /

cm2

x14

.22

=p.

s.i.

p.s.

i.x

0.70

3 / s

.g.

=m

.liqu

idx

1.42

2 x

s.g.

=p.

s.i.

ft liq

uid

x0.

0298

9 x

s.g.

=ba

rx

33.4

56 /

s.g.

=ft

liqui

d

ins

Hgx

0.34

537

/ s.g

.=

m.li

quid

x2.

896

x s.

g.=

ins

Hg

ins

Hgx

0.03

386

=ba

rx

29.5

3=

ins

Hg

torr

s (m

m H

g)x

0.01

36 /

s.g.

=m

.liqu

idx

73.5

6 x

s.g.

=to

rrs

torr

s (m

m H

g)x

0.00

1333

=ba

rx

750

=to

rrs

kg /

cm2

x10

/ s.

g.=

m.li

quid

x0.

1x

s.g.

kg /

cm2

kg /

cm2

x0.

9806

5=

bar

x1.

197

=kg

/ cm

2

m li

quid

x0.

0980

65 x

s.g

.=

bar

x10

.197

/ s.

g.=

m li

quid

kPa

x0.

1019

7 / s

.g.

=m

x9.

807

x s.

g.=

kPa

Std

atm

x1.

0132

5=

bar

x0.

9879

=St

d at

m

hpx

0.74

57=

kWx

1.34

1=

hp

met

ric h

p (C

V, P

S, P

K, C

F)x

0.73

55=

kWx

1.35

96=

met

ric h

p

hpx

0.98

63=

met

ric h

p x

1.01

39=

hp

seCtiON 28

ConVERsIon FaCtoRs

Contents3 4

98

sUPPlEMEntaRy Data anD ConVERsIon FaCtoRs

1 Imp gal = 10 lb cold fresh water = 1.2 US gal

1 US gal = 8.33 lb cold fresh water = 0.833 Imp gal

1 Cubic foot = 6.23 Imp gal = 62.3 lb cold fresh water = 64 lb cold sea water

1 (long) ton = 2240 lbs = 224 Imp gal cold fresh water

1 (short) ton = 2000 lbs = 240 US gal cold fresh water

1 barrel (bbl) oil = 42 US gal = 35 Imp gal

1 acre-inch = 22610 Imp gal

1 dm3 = 0.220 gals (Imp)

l / s = (m3 / h) /3.6

Gallons per minute (gpm)

= gallons per hour / 60

= million gallons per day (mgd) / 694.4

Imperial gpm

= US gpm / 1.2

= cubic feet per second (cusecs) x 374

= cubic feet per minute (cumins) x 6.23

= lbs per hour / 600 / specific gravity

= tons per min x 224 / specific gravity

= tons per hour x 3.74 / specific gravity

= barrels (oil) per hour (bph) x 0.583

= 1000’s barrels per day (bpd) x 24.3 x10-6

1 atmosphere (British)

= 14.70 lbs / sq inch (psi) = 30 inches mercury (Hg) = 34 feet of water

Feet head

= psi x 2.31 / specific gravity

= ins Hg x 1.133 / specific gravity

= atmosphere (British) x 34 / specific gravity

1 Horsepower (hp) = 33000 ft lbs per minute = 550 ft lbs per second

Flow velocity ‘v’ in pipe v (ft / sec)

= 0.49 x gpm (Imp) d2

d = pipe actual bore in inches

Contents3 4

99

Flow velocity ‘v’ in pipe v (m / s)

= 1273.2 x l / s

d2

d = pipe actual bore in mm

‘Water’ horsepower (whp)

= Imp gpm x ft hd x s.g.

3300

= US gpm x ft hd x s.g.

3960

= lmp gpm x psi

1430

= Imp gal / hour x psi

85800

Mechanical hp = whp x 100

efficiency %

fluid hp

= l / s x m x s.g. = l / s x kg / cm2 (metric) = l / s x m x s.g. = l / s x kg / cm2 (British)

75 7.5 76 7.6

fluid kW

= l / s x m x s.g. = l / s x kg / cm2 = l / s x bar

101.97 10.197 10

Driver output kW

required

= fluid kW x 100 / E% (pump efficiency)

E (fraction) = fluid kW E% = fluid kW x 100

kW input to pump kW input to pump

seCtiON 28

ConVERsIon FaCtoRs

Contents3 4

100

sECtIon 29

VaCUUM tEChnICal DataPressure and vacuum units conversions. Air and saturated water steam specific volumes. Water saturation temperature.

Abso

lute

pre

ssur

e

Vacu

um

10001030

900800700

600

500

400

300

200

150

100908070

60

50

40

30

20

15

10987

6

5

4

3

2

1.5

760700

600

500

400

300

300

150

100908070

60

50

40

30

20

15

10987

6

5

4

3

2

1.5

1

mbar Torr “Hg psia

30 14

10987

6

5

4

3

2

10.90.8

0.70.6

0.5

0.4

0.3

0.2

0.10.090.080.07

0.06

0.05

0.04

0.03

0.02

25

20

15

10987

6

5

4

3

2

1.5

10.90.80.7

0.6

0.5

0.4

0.3

0.2

0.15

0.10

0.08

0.06

0.04

Ata

11033

0.90.80.7

0.6

0.5

0.4

0.3

0.2

0.15

0.100.090.080.07

0.06

0.05

0.04

0.03

0.02

0.010.0090.0080.007

0.006

0.005

0.004

0.003

0.002

“Hg %

0

5

10

15

2021222324

25

26

27

28

2929.129.229.329.4

29.5

29.6

29.7

29.8

29.929.9129.9229.93

29.9429.95

29.96

010

2030

40

50

60

70

80

90919293

94

95

96

97

98

9999.199.299.399.4

99.5

99.6

99.7

99.8

0

10

20

30

40

50

60

656666676869

70

71

72

73

73.5

74

74.5

75

75.5

75.6

75.7

75.8

75.9

0123

4

5

6

7

8

9

9.5

9.8

10

10.1

10.2

10.3

10.31

cmHg mH O m /kg m /kg ˚C ˚F

2

3

4

5

6

789

0.8160.90.1

0.5

10

15

20

30

40

50

60

708090

100

150

1.673

2

3

4

5

6

7 8 9 10

12 14 16 18 20

30

40

50

60 70 80 90 100

150

200

250

23 3

100 212

200

190

180

170

160

150

140

130

120

110

100

90

80

70

60

50

4040

32

95

90

85

80

75

70

65

60

55

50

45

40

35

30

25

20

15

10

5

0

Dry

air v

olum

e of

1k

g at

15˚

C

Satu

rate

d w

ater

ste

amvo

lum

e of

1kg

Wat

er s

atur

atio

nte

mpe

ratu

re

Contents3 4

101

sECtIon 30

PRoDUCt / aPPlICatIon ChaRts

Pum

p ty

pesP

P M

odel

Disc

harg

e an

d Pe

rfor

man

ceCo

nfigu

ratio

ns

Horiz

onta

lly

Split

Hydr

ostr

eam

150

mm

to 7

00 m

m.

Outp

uts

to

2500

l/s.

Hea

ds u

p to

275

m.

Horiz

onta

l, Ve

rtic

al O

pen

Shaf

t, Ve

rtic

al D

irect

Mou

nted

Ele

ctric

Mot

or o

r Ho

rizon

tal E

lect

ric M

otor

or E

ngin

e Dr

iven

. Hi r

es, v

Din

etc.

Thru

stre

am20

0 m

m to

100

0 m

m.

Outp

uts

up

to 4

500

l/s.

Head

s up

to 2

75m

.

Horiz

onta

l, Ve

rtic

al O

pen

Shaf

t, Ve

rtic

al D

irect

Mou

nted

Ele

ctric

Mot

or o

r Ho

rizon

tal E

lect

ric M

otor

or E

ngin

e Dr

iven

LLC

150

to 7

00m

m. O

utpu

ts to

250

0l/s

. He

ads

up to

275

mHo

rizon

tal,

Vert

ical

Ope

n Sh

aft,

Vert

ical

Dire

ct M

ount

ed

Elec

tric

Mot

or o

r Hor

izon

tal E

lect

ric M

otor

or E

ngin

e Dr

iven

.

Vert

ical

M

ulti-

Stag

e Su

spen

ded

Bow

l

Turb

ostr

eam

GH

, GL,

GR

, GT

100

mm

to 6

00 m

m.

Outp

uts

up

to 2

500

l/s. H

eads

up

to 3

00 m

. Pu

mpi

ng fr

om d

epth

s up

to 1

00 m

.Ve

rtic

al E

lect

ric M

otor

or E

ngin

e Dr

iven

. Wet

wel

l or D

ry w

ell.

LLC

200

to 1

000m

m. O

utpu

ts to

45

00l/s

. Hea

ds u

p to

160

mVe

rtic

al E

lect

ric M

otor

or E

ngin

e Dr

iven

. W

et w

ell o

r Dry

wel

l.

End

Suct

ion

Unis

trea

m32

mm

to 1

50 m

m.

Outp

uts

up to

14

0 l/s

. Hea

ds u

p to

105

m.

Horiz

onta

l DIN

242

55 E

lect

ric M

otor

or

Eng

ine

Driv

en.

Euro

stre

am32

mm

to 1

00 m

m.

Outp

uts

up to

10

0 l/s

. Hea

ds u

p to

105

m.

Horiz

onta

l Clo

se C

oupl

ed E

lect

ric

Mot

or D

riven

.

Inst

ream

40 m

m to

100

mm

. Ou

tput

s up

to

60 l/

s. H

eads

up

to 6

5m.

Vert

ical

Clo

se C

oupl

ed E

lect

ric

Mot

or D

riven

.

seCtiON 29/30

ConVERsIon FaCtoRs

Contents3 4

102

Pum

p ty

pesP

P M

odel

Disc

harg

e an

d Pe

rfor

man

ceCo

nfigu

ratio

ns

Aqua

stre

am20

0 m

m to

650

mm

. Ou

tput

s up

to

180

0 l/s

. He

ads

up to

28

m.

Horiz

onta

l or V

ertic

al E

lect

ric M

otor

or E

ngin

e Dr

iven

.

Dry

Wel

l Sol

ids

Hand

ling

Free

way

75 m

m to

200

mm

. Ou

tput

s to

10

0 l/s

. He

ads

up to

60

m.

Vert

ical

Dire

ct M

ount

ed o

r Ope

n Sh

aft E

lect

ric M

otor

Driv

en.

Free

way

LLC

200

mm

to 1

100

mm

. Ou

tput

s up

to

400

0 l/s

. He

ads

up to

100

m.

Vert

ical

Dire

ct M

ount

ed o

r Ver

tical

Ope

n Sh

aft,

Elec

tric

or

Engi

ne D

riven

.

Tran

sfor

mer

Oil

Pum

ps50

mm

to 2

50 m

m.

Outp

uts

up

to 2

20 l/

s.

Head

s up

to 3

0 m

.

In-L

ine

and

Elbo

w H

oriz

onta

l Int

egra

l Ele

ctric

Mot

or D

rive.

(C

usto

m d

esig

ns a

vaila

ble)

.

Cont

ract

ors

Pum

psAu

topr

ime

50 –

400

mm

. Out

puts

up

to 7

00

l/s. H

eads

up

to 1

60m

Acou

stic

can

opy

on ro

ad to

w o

r site

trai

ler o

r ski

d ty

pe c

hass

is

Dry

Wel

l Sol

ids

Hand

ling

Pack

aged

Ster

eo /

Disi

nteg

rato

r So

lids

Cutti

ng

EQ/E

V So

lids

Dive

rter

75 m

m to

250

mm

. Ou

tput

s up

to

250

l/s.

He

ads

up to

48

m. U

p to

100

mm

. Ou

tput

s up

to 2

0 l/s

.

Horiz

onta

l and

Ver

tical

Ope

n Sh

aft.

Elec

tric

Mot

or D

rive.

Ta

nk p

acka

ges.

Ele

ctric

Mot

or D

rive.

Contents3 4

103

sPP

Pum

p ty

pe:

Dive

rter

•

ster

eo

Dist

inte

grat

or•

Free

way

••

••

••

•

Euro

stre

am•

••

••

•

Unis

trea

m•

••

••

llC

Vert

ical

turb

ine

••

••

••

••

••

thru

stre

am•

••

••

••

•

hydr

ostr

eam

••

••

••

•

llC

split

Cas

e•

••

••

••

••

•

EnVI

RonM

Enta

l sE

RVIC

Es:

Wat

er s

uppl

yW

ater

tre

atm

ent

sew

age

trea

tmen

tDr

aina

geag

ricul

ture

Fore

stry

Cont

ract

ing

Unscreened sewage

Raw sludge

Digested sludge

activated sludge

screened sewage

storm water

Effluent

service water

Raw water lift

ground water extraction

Reservoir pumping

town water supply

boosting

Water intake

sump pumping

Drainage

Flood irrigation

sprinkler irrigation

swimming pools

sand filter washing

Fish farming

Fountains

aPPlICatIons

seCtiON 30

ConVERsIon FaCtoRs

Contents3 4

104

sPP

Pum

p ty

pe:

llC

split

Cas

e•

••

••

••

••

••

••

••

•

hydr

ostr

eam

••

••

••

••

••

••

••

••

thru

stre

am•

••

••

•

llC

Vert

ical

turb

ine

••

••

•

Free

way

••

•

Unis

trea

m•

••

••

•

Euro

stre

am•

••

••

••

••

aqua

stre

am•

••

tran

sfor

mer

oil

••

turb

ostr

eam

••

••

••

••

•

InDU

stRI

al

sERV

ICEs

:Po

wer

Food

Pape

rsu

gar

brw

eing

Mot

orPr

oces

sCh

emic

alst

eel

Plat

ics

onsh

ore/

offs

hore

oild

Indu

stry

sea water lift

Cooling water

Drilling water

Injection water booster

Crude oil shipping

Utility/service water

Washdown

ballast/deballast

oil slops

spray point

tank farm/fuel transfer

Pipeline boosting

Cargo handling

bottle washing

transformer oil cooling

thyristor cooling

Fish farming

Raw juices

Paper stock

Industrial stock

Process waste

Robot cooling

bearing cooling

Moulding machine cooling

Process liquids

aPPlICatIons

Contents3 4

105

FIRE

anD

MEC

hanI

Cal

sERV

ICEs

offs

hore

/ons

hore

Fire

pro

tect

ion

haza

rd p

rote

ctio

n

bulid

ing

serv

ices

hosp

ital s

ervi

ces

sprinkler systems

Foam pumping

hydrant systems

Fire monitor

hose-reel systems

Fire jockey

Fire fighting stationary

Fire fighting marine

hot water circulation

Condensate return

boosted systems

Cold water boosting

Chilled water circulation

Cooling tower circulation

air washer circulation

Water supply

sump pumping

aPPlICatIons

sPP

Pum

p ty

pe:

thus

trea

m•

••

••

••

••

••

•

turb

ostr

eam

••

••

••

••

••

••

•

Unis

trea

m•

••

••

••

•

Euro

stre

am•

••

••

••

••

••

••

Inst

ream

••

••

••

••

••

••

••

over

head

bel

t

Driv

e•

Mul

tistr

eam

••

••

seCtiON 30

ConVERsIon FaCtoRs

sPP

Pum

p ty

pe:

llC

split

Cas

e•

••

••

••

••

••

••

••

•

hydr

ostr

eam

••

••

••

••

••

••

••

••

thru

stre

am•

••

••

•

llC

Vert

ical

turb

ine

••

••

•

Free

way

••

•

Unis

trea

m•

••

••

•

Euro

stre

am•

••

••

••

••

aqua

stre

am•

••

tran

sfor

mer

oil

••

turb

ostr

eam

••

••

••

••

•

Contents3 4

106

notEs

Contents3 4

107

notEs

Contents3 4

108

notEs

Contents3 4

Contents3 4

data for pump users spp pumps

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