AMP EPG Engineering Catalog 2010 aadicps-fire.com/CPS catalog locked/without curve/CPS VT Catalog.pdf · ANSI/AWWA Specification E101, Section 5.1 “Standard Specifications ... 69

Vertical Turbine Deep Well

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Deep-Well Open Lineshaft Vertical Turbines

The CPS Vertical Turbine pumps are designed for long, dependable life in many applications. Modern processing methods require modern pumping equipment to satisfactorily handle the many and varied fluids used in the various industries. CPS Engineers, backed by over 125 years of manufacturing experience, have met this demand with the vertical turbines offered today. We have incorporated in our design, ideas and suggestions from competent engineers from all sections of the country.

Material Specifications

CONSTRUCTION

BRONZE FITTED ALL IRON ALL BRONZE

Bowl Assembly Cast Iron Cast Iron Bronze Bowl Bearings Bronze Bronze Bronze Impeller(s) Bronze Cast Iron BronzeBowl Shaft 416 SS 416 SS 416 SS Strainer Galvanized Steel Galvanized Steel Galvanized Steel Discharge Column A53 Steel A53 Steel A53 Steel Column Shaft C1045 Steel C1045 Steel C1045 Steel Column Bearings Rubber Rubber Rubber Discharge Head Cast Iron Cast Iron Cast Iron

PUMPING CONDITIONS:

Fluid to be Pumped: Design Capacity (USGPM): Differential Head (FEET): Maximum RPM: Minimum acceptable bowl efficiency, (%): Viscosity (SSU): Specific Gravity: Suction Pressure (PSIG) Temperature (°F):

PRODUCT BULLETIN MODEL DEEP-WELL OPEN

LINESHAFT VERTICAL TURBINE

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MODEL DEEP WELL OPEN LINESHAFT VT SPECIFICATIONS

Bowl Assembly: The pump bowls shall be of close grained, cast iron ASTM A48 Class 30. The water passages on bowl sizes 6” through 16” shall be lined with porcelain enamel or fusion epoxy lined to reduce friction loss, shall be free of blow holes, sand holes and other detrimental defects, and shall be accurately machined and fitted. The impellers shall be of bronze (enclosed or semi-open) and dynamically balanced. Impellers through 16” shall be securly fastened to the shaft with taper split bushings of steel. Larger sizes shall be double-keyed. Impellers shall be adjusted vertically by an external means.

The pump shaft shall be of A582 grade 416 stainless steel, turned, ground and polished. It shall be supported by bronze bearings above and below each impeller. The suction case bearing shall be grease lubricated and protected by a bronze sand collar. The size of the shaft shall be no less than that determined by ANSI/AWWA Specifications E101, Section A4.3 paragraph 4.3.3.

Suction Pipe & Strainer: The suction pipe shall be 10’ in length and of a size and weight at least equal to the outer column. A galvanized cone type strainer shall be provided having a net inlet area equal to at least four times the suction pipe area. The maximum opening size shall not be more than 75 percent on the minimum opening of the water passage through the bowl and impeller.

Column Assembly: The lineshafts shall be of carbon steel ASTM A108 grade C1045 with 300 series stainless steel sleeves spaced at 10’ intervals for 1800 RPM and 5’ for 2200 RPM and over, turned and ground. They shall be furnished in inter-changeable sections not over __________ feet in length.

The butting faces shall be machined square to the axis of the shaft, with maximum permissable axial misalignment on the thread axis with the shaft axis 0.002” in 6”. The size of the shaft shall be no less than that determined by ANSI/AWWA-E101 Specifications Section 5.5 for C1045 lineshaft and shall be such that elongation due to hydraulic thrust will not exceed the axial clearance of the impellers in the pump bowls. Maximum runout in 10’ shall not exceed 0.005”.

The lineshaft bearing shall be of bronze, internally spiral grooved to allow lubricant to flow through and threaded externally to act as enclosing tube connectors at 5’ intervals.

The shaft enclosing tube shall be of ASTM A120 schedule 80 with the ends machined square and parrallel, threaded internally to receive the line-shaft bearings. Maximum tube thread run-out in 5’ length shall not exceed 0.005”. Bearing spacing shall not exceed 5’.

The outer column shall be either flanged or threaded of ASTM A53 grade B steel pipe of ASTM A120 interchangable sections not over 10’ in length for 2200 RPM and over with the ends of each section faced parallel and machined. Threaded will have 8 straight threads per inch permitting the

end to butt and insuring alignment when connected by standard mill steel coupling. Flanged will be machined to accept bearing retainer in such a way as not to allow any movement of retainer after flanges are bolted securely together and to implement proper sealing of the column. The weight of the column pipe shall be no less than that stated in ANSI/AWWA Specification E101, Section 5.1 “Standard Specifications for Discharge Column Pipe.” The column size shall be such that friction loss will not exceed 5’ or 100’, based on the rated capacity of the pump. If possible, the column size shall be such also be such as to provide a velocity of not less than 5 feet per second at the rated capacity.

Top and bottom sections of column pipe on product lubricated pumps shall not exceed 5’ in length.

Discharge Head: The discharge head shall be of close grain, cast iron, ASTM A48 class 30, free of sand holes and other defects, accurately machined and with a surface discharge. Discharge flange shall be machined and drilled to ANSI standards for 125 lb. rating and shall be __________ inches nominal inside diameter. The top of the discharge head shall have a rabbet fit to accurately locate the vertical hollow shaft driver, and have a diameter equal to the drive base diameter (BD) and less than __________ inches.

Th discharge head shall be equipped with a tube tensioning device to apply and maintain proper tension to the shaft enclosing tube. The inner column tension nut assembly shall incorporate a tension nut, a bronze headshaft bearing and neoprene dust seals to prevent dirt from entering tube line at shaft. Provisions shall be made for locking the tension nut in place after tightening.

The top lineshaft shall be of ASTM A108 grade C1045 steel and shall not exceed 10’ in length. Impeller adjustment shall be provided at the top of the headshaft by means of adjusting nut which shall be positively locked in position.

Motor: The electric motor shall be vertical hollow shaft __________ RPM., three phase (50 or 60 Hz) __________ volts with a non-reverse ratchet, P-base, squirrel cage induction design. Enclosure shall meet NEMA weather protected type type 1 design with stainless steel screens to prevent entrance of rodents. Motor shall have Class B or Class F insulation with temperature rise as specified by NEMA standards for class insulation used and shall have a 1.15 service factor.

Thrust bearing shall be chosen to handle the continuous down thrust as specified by the pump manufacturer with an AFBMA B-10 one-year minimum or five year average life under design conditions. Provisions shall be made for momentary upthrust equal to 30 percent of rated down thrust. The motor rating shall be such that at design it will not be loaded beyond nameplate rating and at no place on the pump curve shall the loading exceed the service factor.

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DEEP WELL VERTICAL TURBINE SECTIONAL DRAWING

Item Number Item Description Item

Number Item Description

1 Discharge Head 70 Oil Lubricated O/C Section (10’ 0” long) TBE 2 Head Column Flange 71 I/C Section (5’ 0” long) 3 Head Column Flange Gasket 72 Oil Lubricated L/S Section (10’ 0” long) 4 Studs 73 Oil Lubricated O/C Section (5’ 0” long) TBE 5 Nuts 74 Oil Lubricated L/S Section (5’ 0” long) TBE 6 Head Discharge Flange 75 I/C Stabilizing Spider 7 Head Discharge Flange Gasket 76 Water Lubricated O/C Section 8 Discharge Flange Assembly Cap Screws 77 Water Lubricated O/C Section 9 Discharge Flange Assembly Nuts 78 Water Lubricated L/S Bearing Spider

10 Head Discharge Flange Assembly Studs 79 Water Lubricated L/S Bearing 11 Head Discharge Flange Assembly Nuts 80 Water Lubricated L/S Sleeve 14 Head Packing Housing with Bearing 81 Water Lubricated L/S Extension (3’ 9-7/8” long) 15 O-Ring 82 Water Lubricated L/S Section (5’ 0” long) 16 Head Packing Housing Cap Screws 83 Water Lubricated L/S Section (10’ 0” long) 17 Oil Lubricated Headshaft 84 Water Lubricated Bowl Shaft 18 Water Lubricated Headshaft 85 Oil Lubricated Bowl Shaft

18A Top Shaft 88 Oil Lubricated Discharge Case 19 Headshaft Flinger 89 Oil Lubricated Discharge Case Bearing 20 Headshaft Adjusting Nut 90 Water Lubricated Case Bearing 22 Packing (Set) 91 Water Lubricated Case Bearing 23 Packing Follower 93 Water Lubricated Case Bearing 25 Head Packing Housing Grease Fittings 94 Sand Cap Set Screws 26 Packing Follower Studs 96 Shaft Seal 27 Packing Follower Retainer Nuts 97 I/C Adapter Coupling 28 Adapter Flange 101 Top Bowl Assembly 29 Adapter Flange O-Ring 102 Top Bowl Bearing 30 Adapter Flange Assembly Cap Screws 103 Bowl Assembly (Enclosed Type) 31 Oil Lubricated Headshaft Bearing 104 Bowl Bearing 32 Water Lubricated Headshaft Bearing 105 Bowl Assembly (Semi-Open Type) 33 Water Lubricated Headshaft Bearing 106 Impeller (Enclosed Type) 34 Adjusting Nut Machine Screw 107 Impeller (Semi-Open Type) 40 I/C Tension Nut 108 Taper Lock 41 Tension Nut Set Screw 109 Suction Case Assembly (Enclosed Type) 42 I/C Seal Ring 110 Suction Case Bearing 43 I/C Seal Ring Nut 111 Suction Case Assembly 44 Headshaft Bearing Assembly Cap Screws 113 Suction Case End Plug 45 Headshaft Bearing Dust Seal 114 Suction Case Sand Cap 49 Solenoids Valve 115 Optional Set Screws for Brass Sand Cap 53 Vented Sight Drip Valve 116 Bowl Suction Flange 54 Tubing for Oil Lubrication 117 Bowl Assembly Cap Screws 55 Oil Line Connector for Headshaft Bearing 119 Suction Bell (Optional) 59 Oil Level Sight Glass 124 Oil Lubricated O/C Section (20’ 0” long) 63 2’ Long O/C Adapter Nipple TBE Top Section 125 Oil Lubricated L/S Section (20’ 0” long) 64 Inner Column Adapter 2’ 4” Long Stretch Nipple 126 Vented Toggle Valve 65 Oil Lubricated Lineshaft Bearing 149 Oil Lubricated O/C Assembly T&C (10’ 0” long) 66 Oil Lubricated Lineshaft Adapter Bearing 150 Oil Lubricated O/C Assembly T&C (5’ 0” long) 67 Shaft Coupling 151 Oil Lubricated O/C Assembly T&C (20’ 0” long) 68 Shaft Adapter Coupling 152 Water Lubricated O/C Asmbly T&C (10’ 0” long) 69 O/C Coupling 153 Water Lubricated O/C Asmbly T&C (5’ 0” long)

Recommended spare parts are in BOLD.

DEEP WELL OPEN LINESHAFT VERTICAL TURBINE

- Your Local Authorized Distributor -

MATERIALS OF CONSTRUCTION BOWL IMPELLERBOWL SHAFT SHAFT COUPLING BOWL BEARINGS SHAFT BEARINGS STRAINER BOWL W/RIMPELLER W/R COLUMN PIPE LINESHAFT PACKINGBASE PLATE DISCHARGE HEAD

PUMP TYPE DISCHARGE HEADSUCTION DISCHARGELINESHAFT COLUMNLUBRICATION MODELSTAGE GPMTDH TRIMRPM BHP

MOTOR

MAKE TYPEENCLOSURE NRRSRC HPRPM PHASEHERTZ VOLTAGEFRAME NO. TYPE COUPLING

OTHER SPECIFICATIONS DRAWING NO. SERIAL NO. FLUID SPECIFIC GRAVITYVISCOSITY TEMPERATUREPH NO. UNITS REQUIRED

CUSTOMER ADDRESS CITY ST ZIPTEL. ( ) FAX. ( ) REP. SUPPLIER SALESMAN

Sales & Marketing: Manufacturing:

Phone: Fax:

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Deep-Well Enclosed Lineshaft Vertical Turbines



CONSTRUCTION



PUMPING CONDITIONS:


PRODUCT BULLETIN MODEL DEEP-WELL ENCLOSED LINESHAFT VERTICAL TURBINE

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MODEL DEEP WELL ENCLOSED LINESHAFT VT SPECIFICATIONS



Suction Pipe & Strainer: The suction pipe shall be 10’ in length and of a size and weight at least equal to the outer column. A galvanized cone type strainer shall be provided having a net inlet area equal to at least four times the suction pipe area. The maximum opening size shall not be more than 75 percent on the minimum opening of the water passage through the bowl and impeller.

Column Assembly: The lineshafts shall be of carbon steel ASTM A108 grade C1045 with 300 series stainless steel sleeves spaced at 10’ intervals for 1800 RPM and 5’ for 2200 RPM and over, turned and ground. They shall be furnished in inter-changeable sections not over __________ feet in length.


The lineshafts shall be provided with ASTM A269 grade 304 stainless steel threaded sleeves at the location of each lineshaft bearing. The use of glues or any other means of securing the sleeve to the shaft, that is not field replaceable without the use of heat or special tools is not acceptable. The lineshaft bearing shall be of 70 minimum shore hardness, neoprene, snap-in type, internally sprial grooved to flush out sand and other abrasives, mounted inside bronze bearing retainers held in position in the column pipe. Bearing spacing shall not exceed 10’ for 1800 RPM of 5’ for 2200 RPM and above.

The outer column shall be either flanged or threaded of ASTM A53 grade B steel pipe of ASTM A120 interchangable sections not over 10’ in length for 2200 RPM and over with the ends of each section faced parallel and machined. Threaded will have 8 straight threads per inch permitting the end to butt and insuring alignment when connected by standard mill steel coupling. Flanged will be machined to accept bearing retainer in such a way as not to allow any movement of retainer after flanges are bolted securely together and to implement proper sealing of the column. The weight of the column pipe shall be no less than that stated in ANSI/AWWA Specification E101, Section 5.1 “Standard Specifications for Discharge Column Pipe.” The column size shall be such that friction loss will not exceed 5’ or 100’, based on the rated capacity of the pump. If possible, the column size shall be such also be such as to provide a velocity of not less than 5 feet per second at the rated capacity.



The standard cast iron stuffing box shall be rated for 125 PSI discharge pressure and shall be fitted with graphite acrylic packing. It shall have a lantern ring or grease chamber placed as required below the top packing ring. Throttle bearing shall be bronze with stainless steel bolting and with brass or stainless steel adjusting nuts. Sealing between the stuffing box and the discharge head shall be accomplished by means of an o-ring.

If the discharge pressure exceeds 125 PSI, a high pressure bypass style packing box shall be supplied with a minimum of six rings of packing and two lantern rings and a bypass to sump.

If the setting is greater than 50’ and a non-pressure discharge, the pump shall be fitted with lubricated assembly consisting of galvanized steel tank and fittings with manual valve to lubricate the lineshaft bearings prior to startup. If pumping into a pressurized system, a __________ inch solenoid prelube valve shall be supplied for __________ volts, 50 or 60 hertz, and the motor starter shall be fitted with a time delay relay to open prior to pump startup.

A unit which requires a mechanical seal shall have a housing bolted to the head with an o-ring seal. The housing shall have a lower bronze throttle bushing. The housing seal chamber shall accommodate a single sleeved (balanced/unbalanced) mechanical seal suitable for the maximum pressure developed by the pump of __________ PSI and temperature __________°F maximum. Seal materials shall be compatible with the liquid pumped. A balanced seal shall be mounted on a shaft sleeve. The shaft supplied shall be one-piece bowl, line and head-shaft where practical of 416 stainless steel material.

The top lineshaft shall be of ASTM A582 grade 416 stainless steel and shall not exceed 126” in length. Impeller adjustment shall be provided at the top of the headshaft by means of adjusting nut which shall be positively locked in position.



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DEEP WELL VERTICAL TURBINE SECTIONAL DRAWING







DEEP WELL ENCLOSED LINESHAFT VERTICAL TURBINE


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MOTOR





Phone: Fax:

Vertical Turbine Short Set

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Short-Set Cast Iron Head Vertical Turbines



CONSTRUCTION PART



PUMPING CONDITIONS:


PRODUCT BULLETIN MODEL SHORT-SET CAST IRON

HEAD VERTICAL TURBINE

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MODEL SHORT SET CAST IRON VT SPECIFICATIONS



Strainer: A __________ basket type clip-on strainer shall be provided having a net inlet area equal to at least four times the suction pipe area. The maximum opening size shall not be more than 75 percent on the minimum opening of the water passage through the bowl and impeller.

Column Assembly: The lineshafts shall be of __________. They shall be furnished in inter-changeable sections not over __________ feet in length.



The outer column pipe shall be 5” and larger of ASTM A53 grade B steel pipe of ASTM A120 in interchangable sections not over 10’ in length for 1800 RPM and 5’ in length for 2200 RPM and above.

THREADED: The ends of each section faced parallel and machined with 8 straight threads per inch permitting the end to butt and insuring alignment when connected by standard mill steel coupling.

FLANGED: The column assembly shall be flanged and machined to accept bearing retainer in such a way as not to allow any movement of retainer after flanges are bolted securely together and to implement proper sealing of the column. The weight of the column pipe shall be no less than that stated in ANSI/AWWA Specification E101, Section 5.1 “Standard Specifications for Discharge Column Pipe.” The column size shall be such that friction loss will not exceed 5’ or 100’, based on the rated capacity of

the pump. If possible, the column size shall be such also be such as to provide a velocity of not less than 5 feet per second at the rated capacity.






The top lineshaft can be of _________ and shall not exceed 10’ in length and can be equipped with a 304 stainless steel threaded replacement sleeve locked in place by a lineshaft coupling for packing wear area. Impeller adjustment shall be provided at the top of the headshaft by means of adjusting nut which shall be positively locked in position. The headshaft shall also be __________ and shall be connected to the top lineshaft beneath the motor to facilitate ease of assembly and maintenance.



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SHORT SET VERTICAL TURBINE SECTIONAL DRAWING







SHORT SET CAST IRON HEAD VERTICAL TURBINE




MOTOR





Phone: Fax:

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Short-Set Fabricated Head Vertical Turbines



CONSTRUCTION


Bowl Assembly Cast Iron Cast Iron Bronze Bowl Bearings Bronze Bronze Bronze Impeller(s) Bronze Cast Iron BronzeBowl Shaft 416 SS 416 SS 416 SS Strainer Galvanized Steel Galvanized Steel Galvanized Steel Discharge Column A53 Steel A53 Steel A53 Steel Column Shaft C1045 Steel C1045 Steel C1045 Steel Column Bearings Rubber Rubber Rubber Discharge Column Cast Iron Cast Iron Cast Iron Discharge Head BRONZE FITTED ALL IRON ALL BRONZE

PUMPING CONDITIONS:


PRODUCT BULLETIN MODEL SHORT-SET FABRICATED

HEAD VERTICAL TURBINE

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MODEL SHORT SET FABRICATED HEAD VT SPECIFICATIONS



Strainer: A __________ basket type clip-on strainer shall be provided having a net inlet area equal to at least four times the suction pipe area. The maximum opening size shall not be more than 75 percent on the minimum opening of the water passage through the bowl and impeller.

Column Assembly: The lineshafts shall be of __________. They shall be furnished in inter-changeable sections not over __________ feet in length.





FLANGED: The column assembly shall be flanged and machined to accept bearing retainer in such a way as not to allow any movement of retainer after flanges are bolted securely together and to implement proper sealing of the column. The weight of the column pipe shall be no less than that stated in ANSI/AWWA Specification E101, Section 5.1 “Standard Specifications for Discharge Column Pipe.” The column size shall be such that friction loss will not exceed 5’ or 100’, based on the rated capacity of

the pump. If possible, the column size shall be such also be such as to provide a velocity of not less than 5 feet per second at the rated capacity.


Discharge Head: The discharge head shall be of Schedule 40 fabricated steel, free from defects, accurately machined and with a surface discharge. Discharge flange shall be machined and drilled to ANSI standards for __________ pounds rating faced shall be __________ inches nominal inside diameter. The top of the discharge head shall have a rabbet fit to accurately locate the vertical hollow shaft driver, and have a diameter equal to the driver base diameter (BD) and less than __________ inches.




The top lineshaft can be of _________ and shall not exceed 10’ in length and can be equipped with a 304 stainless steel threaded replacement sleeve locked in place by a lineshaft coupling for packing wear area. Impeller adjustment shall be provided at the top of the headshaft by means of adjusting nut which shall be positively locked in position. The headshaft shall also be __________ and shall be connected to the top lineshaft beneath the motor to facilitate ease of assembly and maintenance.



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SHORT SET VERTICAL TURBINE SECTIONAL DRAWING







6

SHORT SET FABRICATED HEAD VERTICAL TURBINE




MOTOR





Phone: Fax:

Vertical Turbine Can


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Short Set Can With Cast Iron Head Vertical Turbines



CONSTRUCTION



PUMPING CONDITIONS:


PRODUCT BULLETIN MODEL SHORT-SET CAN WITH CAST

IRON HEAD VERTICAL TURBINE

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MODEL SHORT SET CAN WITH CAST IRON HEAD VT SPECIFICATIONS



Column Assembly: The butting faces shall be machined square to the axis of the shaft, with maximum permissable axial misalignment on the thread axis with the shaft axis 0.002” in 6”. The size of the shaft shall be no less than that determined by ANSI/AWWA-E101 Specifications Section 5.5 for C1045 lineshaft and shall be such that elongation due to hydraulic thrust will not exceed the axial clearance of the impellers in the pump bowls. Maximum runout in 10’ shall not exceed 0.005”.




FLANGED: The column assembly shall be flanged and machined to accept bearing retainer in such a way as not to allow any movement of retainer after flanges are bolted securely together and to implement proper sealing of the column. The weight of the column pipe shall be no less than that stated in ANSI/AWWA Specification E101, Section 5.1 “Standard Specifications for Discharge Column Pipe.” The column size shall be such that friction loss will not exceed 5’ or 100’, based on the rated capacity of the pump. If possible, the column size shall be such also be such as to provide a velocity of not less than 5 feet per second at the rated capacity.


Discharge Head: The discharge head shall be of close grain, cast iron, ASTM A48 class 30, free of sand holes and other defects, accurately machined and with a surface discharge. The base of head should be also machined to an ANSI 125 lb. rating to match the flange on top of the

barrel. Discharge flange shall be machined and drilled to ANSI standards for 125 lb. rating flat faced and shall be __________ inches nominal inside diameter. The top of the discharge head shall have a rabbet fit to accurately locate the vertical hollow shaft driver, and have a diameter equal to the drive base diameter (BD) and less than __________ inches.

Stiffing Box: The seal arrangement provided shall be one of the following (packing or mechanical seal):






Suction Barrel: The unit shall be supplied with a fabricated steel suction barrel. The barrel shall be capable of containing the maximum suction pressure supplied to the suction flange. The bottom end of the suction barrel shall be supplied with a welded plate cap dor water service. A weld cap shall be supplied for all hydrocarbon service applications.

The barrel shall be equipped with a square base plate which shall be machined and tapped to match the discharge head base flange supplied. The base shall be drilled to allow the barrel to be secured in place with anchor bolts. Barrel shall be supplied with proper gasket or o-ringh and bolting for application to seal between the barrel flange and the head base flange.

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SHORT SET CAN WITH CAST IRON HEAD SECTIONAL DRAWING







6

SHORT SET CAN WITH CAST IRON HEAD VERTICAL TURBINE




MOTOR





Phone: Fax:

1

Short Set Can With Fabricated Steel Head Vertical Turbines



CONSTRUCTION



PUMPING CONDITIONS:


PRODUCT BULLETIN MODEL SHORT-SET CAN WITH

FABRICATED STEEL HEAD VERTICAL TURBINE

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MODEL SHORT SET CAN WITH FABRICATED STEEL HEAD VT SPECIFICATIONS









Discharge Head: The discharge head shall be of Schedule 40 fabricated steel, free from defects, accurately machined and with a surface discharge. Discharge flange shall be machined and drilled to ANSI

standards for __________ pounds rating faced shall be __________ inches nominal inside diameter. The top of the discharge head shall have a rabbet fit to accurately locate the vertical hollow shaft driver, and have a diameter equal to the driver base diameter (BD) and less than __________ inches.

Stuffing Box: The seal arrangement provided shall be one of the following (packing or mechanical seal):








5

SHORT SET CAN WITH FABRICATED STEEL HEAD SECTIONAL DRAWING







SHORT SET CAN WITH FABRICATED STEEL HEAD VERTICAL TURBINE




MOTOR





Phone: Fax:

1

Short Set “T” Can With Fabricated Steel Head Vertical Turbines



CONSTRUCTION



PUMPING CONDITIONS:


PRODUCT BULLETIN MODEL SHORT-SET “T” CAN WITH

FABRICATED STEEL HEAD VERTICAL TURBINE

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MODEL SHORT SET “T” CAN WITH FABRICATED STEEL HEAD VT SPECIFICATIONS









Discharge Head: The discharge head shall be fabricated of carbon steel materials using ASTM A181 flanges, ASTM A53 grade B body pipe and ASTM A36 steel plate with the suction and discharge flanges inline with each other and located 180° apart, or as specified. Discharge head shall be capable of containing maximum pressure developed by pump plus suction pressure. The suction and discharge flanges shall be 150 lb. ANSI raised face flanges with bolt holes straddling discharge centerline. Flange

pressure ratings must be specified for higher operating pressures. A ¼” NPT pressure gauge connection shall be supplied on suction and discharge pipes. A ¾” NPT barrel vent shall be located on the outer casing of the discharge head.

The discharge head shall be supplied with adequate integral motor stand height to accept seal arrangement required and adjustable flanged or spacer coupling.

Stuffing Box: The seal arrangement provided shall be one of the following (packing or mechanical seal):








5

SHORT SET “T” CAN WITH FABRICATED STEEL HEAD SECTIONAL DRAWING







SHORT SET “T” CAN WITH FABRICATED STEEL HEAD VERTICAL TURBINE




MOTOR





Phone: Fax:

Vertical Turbine Submersible


1

Submersible Vertical Turbines



CONSTRUCTION



PUMPING CONDITIONS:


PRODUCT BULLETIN MODEL SUBMERSIBLE VERTICAL

TURBINE

PRO

DU

CT

BU

LL

ET

IN

M

UN

ICIP

AL

C

OM

ME

RC

IAL

IN

DU

STR

IAL

M

OD

EL

VE

RT

ICA

L T

UR

BIN

E

Que

nch

Wat

er, F

iltra

tion,

Tra

nsfe

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oost

er, S

uppl

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ater

Pr

oces

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emic

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Filte

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Car

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2

MODEL SUBMERSIBLE VT SPECIFICATIONS



Riser Pipe: The riser pipe shall be sized such that the friction loss wiill not exceed 5’ per 100’ based on the rated capacity of the pump. If possible, the riser pipe should be sized such that the minimum velocity will not be less than 5’ per second at the rated capacity. Riser pipe sections shall not exceed __________ in length. The pipe shall be ¾” tapered (NPT) threaded from material conforming to ASTM A120 or ASTM A53 grade 53.

Maximum water temperature: 85°°°° Fahrenheight.

Minimum flow past the motor: ½ foot per second

Motor Adapter: A motor adapter of close grained ductile iron with rabbeted fits shall be supplied to connect the submersible motor to the bowl assembly. It shall include the motor adapter bearing assembly and a corrosion resistant metal strainer whose free area shall be at least three times the impeller suction eye area. The maximum strainer opening shall

not be more than 75% of the minimum opening through the bowl or impeller.

Submersible Motor: The electric motor shall be vertical hollow shaft __________ RPM., three phase (50 or 60 Hz) __________ volts with a non-reverse ratchet, P-base, squirrel cage induction design. Enclosure shall meet NEMA weather protected type type 1 design with stainless steel screens to prevent entrance of rodents. Motor shall have Class B or Class F insulation with temperature rise as specified by NEMA standards for class insulation used and shall have a 1.15 service factor.


Surface Plate: The surface plate shall be fabricated from carbon steel with a flat face base flange to match the well casing flange, short radius 90° steel elbow terminating in a 150 pound raised faced steel discharge flange. The surface plate shall be fitted with properly sized electrical junction box to allow for splicing surface cables and well cables. It shall also be tapped from a well vent and air-line and shall be provided with lifting lugs of sufficient strength to lift the entire pump and motor assembly including riser pipe. A short 12”, threaded or flanged, nipple shall extend below the surface plate for connection to riser pipe.

Power Cable: The power cable shall be sized such that the voltage drop will not exceed five percent at the motor rated full load current and voltage. Cable shall be designed specifically for submersible pump service and shall consist of either three single conductors individually insulated or three individual conductors individually insulated and the whole covered with an outer jacket.

3

OPEN LINESHAFT TURBINE PUMP SECTIONALS



67 Shaft Coupling 107 Impeller (Semi-Open Type) 84 Water Lubricated Bowl Shaft 108 Taper Lock 90 Water Lubricated Case Bearing 109 Suction Case Assembly (Enclosed Type) 91 Water Lubricated Case Bearing 110 Suction Case Bearing 93 Water Lubricated Case Bearing 111 Suction Case Assembly 94 Sand Cap Set Screws 113 Suction Case End Plug

103 Bowl Assembly (Enclosed Type) 114 Suction Case Sand Cap 104 Bowl Bearing 115 Optional Set Screws for Brass Sand Cap 105 Bowl Assembly (Semi-Open Type) 117 Bowl Assembly Cap Screws 106 Impeller (Enclosed Type)


4

SUBMERSIBLE VERTICAL TURBINE




MOTOR





Phone: Fax:

Vertical Turbine Engineering Information

11/22/04, Page 1 of 1480E.1

CIE Bowl CIECI Impeller CI

No Yes Yes No Yes No Yes No Imp. Polish Yes No Yes Yes No Yes No Yes3 2 4 6 6 7 9 12 2 2 3 5 5 7 73 2 4 6 6 7 9 12 2 2 3 5 5 7 63 2 4 6 6 7 8 10 2 2 3 5 5 7 63 2 4 6 6 7 8 10 2 2 3 5 5 7 63 2 4 6 6 7 8 10 2 2 3 5 5 7 63 2 4 6 6 7 8 10 2 2 3 5 5 6 63 2 4 6 6 7 8 10 2 2 3 5 5 6 62 2 3 6 5 7 7 9 2 2 3 5 5 6 62 2 3 6 5 7 7 9 2 2 3 5 5 6 62 2 3 6 6 7 7 10 2 2 3 5 5 6 62 2 3 6 6 7 7 10 2 2 3 5 5 6 62 2 3 6 5 7 7 9 2 2 3 5 5 6 62 2 3 5 5 7 7 9 2 2 3 5 5 6 62 2 3 5 5 7 7 9 2 2 3 5 5 6 62 2 3 5 5 7 7 9 2 2 3 5 5 6 62 2 3 5 5 7 7 9 2 2 3 5 5 6 62 2 3 5 6 7 7 9 2 2 3 5 5 6 52 2 3 5 5 7 7 9 2 2 4 6 4 6 52 2 3 5 5 7 7 9 2 2 4 6 4 6 52 2 3 5 5 7 7 9 2 2 4 6 4 6 52 2 3 5 5 7 7 9 2 2 4 6 4 6 52 2 3 5 5 7 7 9 2 2 4 6 4 6 52 2 3 5 5 7 6 9 2 2 4 6 4 6 52 2 3 5 5 6 6 9 2 2 4 6 4 6 52 2 3 5 5 6 6 9 2 2 4 6 4 6 52 2 3 6 5 7 7 9 2 2 4 6 4 6 52 2 3 5 5 7 7 9 2 2 4 6 4 6 52 2 3 5 5 7 7 9 2 2 4 6 4 6 5

Notes:Cast Iron enameled through 24".Standard bronze bowls have uncoated flow passages. Coatings can be furnished to provide increased efficiencies.Refer To Factory for price addition and efficiency."No" indicates that impellers are unpolished. "Yes" indicates that impellers will be polished.For efficiencies with material, material combination, models or sizes not shown, Refer To Factory.Any applicable staging correction shown on the performance cures must be calculated in addition to the above efficiency deductions.Stainless steel wear rings further reduce both efficiency and head per stage. Refer To Factory for efficiency deductions.For bowls machined for extra lateral (not deep setting construction) deduct two (2) points from efficiency.

Bowl Unit Efficiency Adjustment Notes:1. Performance curves show the performance of (a) polished bronze impellers (b) with cast iron bowls with coated flow passages.Because the highest efficiencies attainable are produced by this combination, their efficiencies are the basic values used in the performance section.2. Non-polished impellers have their vane exit tips filled, for streamlining, and casting irregularities (if any) "clean-up". Polished impellers have their flow passage surfaces smoothed to a high degree for maximum performance.3. THESE EFFICIENCY DEDUCTIONS MUST BE MADE IN ADDITION TO ANY STAGING CORRECTIONS SHOWN ON THEPERFORMANCE CURVES.

No

7

7777

7777

9977

9999

9999

9999

12DC

12XC

14WC14YC14ZC15KC18LC

22LC

10JC10KC

480 Vertical Turbine

CI

12JC 24LC

20HC10YC

10MC10LC

14XC

10ZC

10HC10WC

18MC18HC20LC

14HC

12YC

20MC

13MC

Bas

ic v

alue

s sh

own

on p

erfo

rman

ce c

urve

s

Stainless Steel

999

BronzeBronze

StainlessSteel Bronze

For bowl units with other than (a) polished bronze impellers and (b) enameled or plastic coated iron bowl, reduce the heads and efficiencies shown on the performance curves by the following values:

VERTICAL TURBINE PUMPSBowl Unit Efficiency Adjustments

CIE

6JCL6JCM6JCH6JCX6JCW6JCY

12WC

8YC

7MC

6JCJ 12NC12LC12GC12MC

12MCE12HC

BronzeYes

8WC

8EHC

Bas

ic v

alue

s sh

own

on p

erfo

rman

ce c

urve

s

8LC

7HC8JC

8MC8KC

CPS PUMPS

CICIE

BronzeBronze

14LC14MC

24MC24HC

12IC12KC

VERTICAL TURBINE PUMPS

TUR B INE TE R MINOL OGYTUR B INE TE R MINOL OGY

1. DATUM OR GR ADE - The elevation of the surface1. DATUM OR GR ADE - The elevation of the surfacefrom which the pump is supported.from which the pump is supported.

2. S TAT IC WATE R LE VE L - The vertical distance from2. S TAT IC WATE R LE VE L - The vertical distance fromgrade to the water level when no water is beinggrade to the water level when no water is beingdrawn from the well.drawn from the well.

3. DR AWDOWN - The distance between the static3. DR AWDOWN - The distance between the staticwater level and the water level when pumping atwater level and the water level when pumping atrequired capacity.required capacity.

4. PUMP ING WATE R LE VE L - The vertical distance4. PUMP ING WATE R LE VE L - The vertical distancefrom grade to water level when pumping at re-from grade to water level when pumping at re-quired capacity. Pumping water level equals staticquired capacity. Pumping water level equals staticWater Level plus Drawdown.Water Level plus Drawdown.

5. S E TT ING - The distance from grade to the top of5. S E TT ING - The distance from grade to the top ofthe pump bowl assembly.the pump bowl assembly.

6. F IE LD PUMP ING HE AD - Lift below discharge plus6. F IE LD PUMP ING HE AD - Lift below discharge plushead above discharge plus friction losses inhead above discharge plus friction losses indischarge line. This is the head for which thedischarge line. This is the head for which thecustomer is responsible and does not includecustomer is responsible and does not includeany losses within the pump.any losses within the pump.

7. C OLUMN FR IC T ION LOS S - Head loss in the pump7. C OLUMN FR IC T ION LOS S - Head loss in the pumpdue to friction in the column assembly. F rictiondue to friction in the column assembly. F rictionloss is measured in feet and is dependentloss is measured in feet and is dependentupon column and shaft s ize and setting. S eeupon column and shaft s ize and setting. S eeTurbine C olumn Friction Loss Table in catalog.Turbine C olumn Friction Loss Table in catalog.

8. TDH (LAB . HE AD) - Total head which the pump8. TDH (LAB . HE AD) - Total head which the pumpbowl assembly must deliver at the given capacity.bowl assembly must deliver at the given capacity.TDH equals F ield Pumping Head plus C olumnTDH equals F ield Pumping Head plus C olumnFriction Loss .

9. LABOR ATOR Y E FF IC IE NC Y - The efficiency of the9. LABOR ATOR Y E FF IC IE NC Y - The efficiency of thebowl unit only. This value is read directly frombowl unit only. This value is read directly fromthe performance curve.the performance curve.

10. LABOR ATOR Y HOR S E POWE R - The horsepower10. LABOR ATOR Y HOR S E POWE R - The horsepowerrequired by the bowls only to deliver a givenrequired by the bowls only to deliver a givencapacity against Laboratory Head.capacity against Laboratory Head.

11. S HAFT FR IC T ION LOS S - The horsepower11. S HAFT FR IC T ION LOS S - The horsepowerrequired to turn the lineshaft in the bearings .required to turn the lineshaft in the bearings .S ee Mechanical F riction in Turbine Pump LineS ee Mechanical F riction in Turbine Pump LineS hafts in catalog.S hafts in catalog.

12. F IE LD HOR S E POWE R OR BR AKE HOR S E POWE R -12. F IE LD HOR S E POWE R OR BR AKE HOR S E POWE R -S um of laboratory horsepower plus shaft lossS um of laboratory horsepower plus shaft loss(and the driver thrust bearing loss under certain(and the driver thrust bearing loss under certainconditions .)

E NG INE E R ING DATA

13. PUMP F IE LD E FF IC IE NC Y (WATE R TO WATE R ) - The13. PUMP F IE LD E FF IC IE NC Y (WATE R TO WATE R ) - Theefficiency of the complete pump less the driver,efficiency of the complete pump less the driver,with all losses between laboratory and field per-with all losses between laboratory and field per-formance being taken into account.formance being taken into account.

14. TOTAL PUMP THR US T - The sum of the weight of14. TOTAL PUMP THR US T - The sum of the weight ofthe shaft plus hydraulic thrust of the liquid beingthe shaft plus hydraulic thrust of the liquid beingpumped. S ee S haft S tretch S ection in C atalog forpumped. S ee S haft S tretch S ection in C atalog forshaft weight per foot. Performance curves giveshaft weight per foot. Performance curves givehydraulic "K" factor. Total thrust equals :hydraulic "K" factor. Total thrust equals :

S haft Wt. Per Foot x S etting in Feet + "K" x TDHS haft Wt. Per Foot x S etting in Feet + "K" x TDH

15. OVE R ALL E FF IC IE NC Y (WIR E TO WATE R ) - The15. OVE R ALL E FF IC IE NC Y (WIR E TO WATE R ) - Theefficiency of the pump and motor complete. Overallefficiency of the pump and motor complete. Overallefficiency = Pump F ield E fficiency x Motor E fficiency.efficiency = Pump F ield E fficiency x Motor E fficiency.

LAB . HP =LAB . HP = C apacity x TDHC apacity x TDH3960 x Laboratory E fficiency3960 x Laboratory E fficiency

3960 x Brake Horsepower3960 x Brake HorsepowerC apacity x F ield Pumping HeadC apacity x F ield Pumping HeadF ield E fficiency =F ield E fficiency =

Grade

Stat

icLe

vel

Pum

ping

Leve

lPu

mpi

ngLe

vel

P um

pSe

tting

Pum

pSe

tting

Lift

Belo

w

Col

umn

Fric

tion

Loss

NOT TO S C ALENOT TO S C ALE

Dra

wdo

wn

P age 1Page 1

VER TICAL PUMP SELECTION GUIDEVER TICAL PUMP SELECTION GUIDE

WELL OR SUMP CONDITIONSWELL OR SUMP CONDITIONS

WELL OR SUMP PUMPWELL OR SUMP PUMP

Pump application:Pump application:Inside diameter of surface casing or sump (in):Inside diameter of surface casing or sump (in):Total depth of well or sump (ft.):Total depth of well or sump (ft.):Is casing stepped down?: Where? (ft.):Is casing stepped down?: Where? (ft.):Smaller (in.): casing from (ft.): to (ft.):Smaller (in.): casing from (ft.): to (ft.):Screen set (ft.): to (ft.):Screen set (ft.): to (ft.):and from (ft.): to (ft.):and from (ft.): to (ft.):Sump water level: Min.: Max.:Sump water level: Min.: Max.:Well static water level (ft.):Well static water level (ft.):Well pumping water level (ft.):Well pumping water level (ft.):

FLUID CONDITIONSFLUID CONDITIONS

Fluid to be pumped:Fluid to be pumped:Ph value:Specific Gravity: Temperature (°F):Specific Gravity: Temperature (°F):Viscosity:Foreign matter in fluid. (Describe):Foreign matter in fluid. (Describe):

Capacity (USGPM):Capacity (USGPM):Bowl head in feet (TDH):Bowl head in feet (TDH):Bowl setting (column length) (ft.):Bowl setting (column length) (ft.):Column lubrication required: (oil) or (water) .Column lubrication required: (oil) or (water) .Type impellers required: (semi-open) or (enclosed).Type impellers required: (semi-open) or (enclosed).Bowl size: No. of stages:Bowl size: No. of stages:NOTE: Bowl head = elevation difference in feet betweenNOTE: Bowl head = elevation difference in feet betweenpumping liquid level in well or sump and pump dischargepumping liquid level in well or sump and pump dischargeconnection plus friction losses in column and dischargeconnection plus friction losses in column and dischargehead plus system head requirements.head plus system head requirements.

PUMPING HYDRAULIC CONDITIONSPUMPING HYDRAULIC CONDITIONS

DRIVER

Size: HP: Type: (VHS) (VSS)Size: HP: Type: (VHS) (VSS)Speed of driver (RPM): Ratio (if gear):Speed of driver (RPM): Ratio (if gear):Non-reverse ratchet desired:Non-reverse ratchet desired:Current characteristics (ph): (hz): (volts):Current characteristics (ph): (hz): (volts):Other driver characteristics:Other driver characteristics:

Suction pipe size (in.): Length (ft.):Suction pipe size (in.): Length (ft.):Strainer (type): (material):Strainer (type): (material):Discharge flange size: Column pipe size:Discharge flange size: Column pipe size:Discharge head connection: (standard) or (special)Discharge head connection: (standard) or (special)

(If special, describe fully):(If special, describe fully):Seal arrangement: Stretch Nipple Kit (oil lube):Seal arrangement: Stretch Nipple Kit (oil lube):

Packing Housing Kit (water lube):Packing Housing Kit (water lube):Mechanical seal:Mechanical seal:

SUCTION AND DISCHARGE COMPONENTSSUCTION AND DISCHARGE COMPONENTS

DRIVER

FABRICA TED HEA VY DUTYDUTY

ST ANDARD

OILLUB.

IMPELLERSSEMI-OPEN

CONESTRAINER

DISCHARGEHEADASSEMBL YASSEMBL Y

COLUMNAND SHAFTASSEMBL Y

BOWLASSEMBL Y

ELECTRICMOT ORDRIVE

GEAR DRIVEGEAR DRIVEWITH RIGHT ANGLEWITH RIGHT ANGLEDIESEL ENGINE

LUB.WATER

CLOSEDIMPELLERS

STRAINERBASKET SUCTION

CASE BELLCASE BELL SUCTION PIPESUCTION PIPECONECTIONWITH CONESTRAINER

FLANGED SUCTIONFLANGED SUCTIONFOR DR Y PITAPPLICA TION

(TYPE "L") (TYPE "T")FABRICA TED

Page 2

B AR R E L S IZINGB AR R E L S IZING

S uction pipe s ize (in):S uction pipe s ize (in):Outs ide diameter of barrel (in):Outs ide diameter of barrel (in):S uction type: (F langed) (P lain end) (Victaulic)S uction type: (F langed) (P lain end) (Victaulic)Total length of barrel (ft.):Total length of barrel (ft.):

F LUID C ONDIT IONSFLUID C ONDIT IONS

F luid to be pumped:F luid to be pumped:Ph value:S pecific G ravity: Temperature (°F ):S pecific G ravity: Temperature (°F ):Viscos ity:Foreign matter in fluid. (Describe):Foreign matter in fluid. (Describe):

Discharge P ressure (ft.):Discharge P ressure (ft.):S uction P ressure (ft.):S uction P ressure (ft.):Differential P ressure or Head (ft.):Differential P ressure or Head (ft.):C apacity (US GPM):C apacity (US GPM):Pump differential head (ft.):Pump differential head (ft.):C olumn losses (ft.):C olumn losses (ft.):S uction barrel and discharge head losses (ft.):S uction barrel and discharge head losses (ft.):Bowl head (differential head plus losses) (ft.):Bowl head (differential head plus losses) (ft.):C olumn lubrication: (product).C olumn lubrication: (product).Type impellers required: (semi-open) or (enclosed) .Type impellers required: (semi-open) or (enclosed) .Bowl s ize: No. of S tages :Bowl s ize: No. of S tages :

PUMP ING HYDR AULIC C ONDIT IONSPUMP ING HYDR AULIC C ONDIT IONS

DR IVE R

S ize: HP : Type: (VHS ) (VS S )S ize: HP : Type: (VHS ) (VS S )S peed of driver (R PM): R atio (if gear):S peed of driver (R PM): R atio (if gear):Non-reverse ratchet des ired:Non-reverse ratchet des ired:C urrent characteris tics (ph): (hz): (volts ):C urrent characteris tics (ph): (hz): (volts ):Other driver characteris tics :Other driver characteris tics :

S uction pipe s ize (in.):S uction pipe s ize (in.):S uction pipe type: (flanged) (plain end) (victaulic groove)S uction pipe type: (flanged) (plain end) (victaulic groove)Discharge flange s ize (in.): R ating: (150#) (300#)Discharge flange s ize (in.): R ating: (150#) (300#)S eal arrangement: (mechanical seal kit) (P acking Housing K it)S eal arrangement: (mechanical seal kit) (P acking Housing K it)

S UC TION AND DIS C HAR GE C OMPONE NTSS UC TION AND DIS C HAR GE C OMPONE NTS

DR IVE R

FABR IC ATE D("TR " S E R IE S )

S TANDAR D

WATE R LUBEWITH P IPEWITH P IPE

DIS C HAR GEHE ADAS S E MBLY

BAR R E LAS S E MBLY

BOWLAS S E MBLY

VHS E LE C TR ICMOTORDR IVE DR IVE

MOTORVS S E LE C TR IC

FABR IC ATE D(TYPE "B ")

C OLUMNAND S HAFTAS S E MBLY

C ONNE C TION C ONNE C TIONWITH FLANGE DWITH FLANGE DWATE R LUBE

S E MI-OPE N ORS E MI-OPE N ORE NC LOS E D IMPE LLE R SE NC LOS E D IMPE LLE R SWITH DIS C HAR GE C AS EWITH DIS C HAR GE C AS EFOR THR E ADE D C OLUMNFOR THR E ADE D C OLUMN

S E MI-OPE N OR E NC LOS E DS E MI-OPE N OR E NC LOS E DIMPE LLE R S WITHOUTIMPE LLE R S WITHOUTDIS C HAR GE C AS E FORDIS C HAR GE C AS E FORFLANGE D C OLUMNFLANGE D C OLUMN

S E MI-OPE N OR E NC LOS E DS E MI-OPE N OR E NC LOS E DIMPE LLE R S WITHOUTIMPE LLE R S WITHOUTDIS C HAR GE C AS E FORDIS C HAR GE C AS E FORDIR E C T ADAPTION TODIR E C T ADAPTION TODIS C HAR GE HE ADDIS C HAR GE HE AD

(TYPE "L") (TYPE "T")FABR IC ATE D

(S TYLE "A")(S TYLE "A")FABR IC ATE D

Page 3Page 3

VERTICAL PUMP SELECTIONGUIDE CAN PUMP

WE LL OR S UMP C ONDIT IONSWE LL OR S UMP C ONDIT IONS

Ins ide diameter of surface cas ing or sump (in.):Ins ide diameter of surface cas ing or sump (in.):Total depth of well or sump (ft.):Total depth of well or sump (ft.):Is cas ing stepped down? : Where? (ft.):Is cas ing stepped down? : Where? (ft.):S maller (in.): cas ing from (ft.): to (ft.):S maller (in.): cas ing from (ft.): to (ft.):S creen set (ft.): to (ft.):S creen set (ft.): to (ft.):and from (ft.): to (ft.):and from (ft.): to (ft.):

S ump water level (ft.): Min.: Max.:S ump water level (ft.): Min.: Max.:Well s tatic water level (ft.):Well s tatic water level (ft.):Well pumping water level (ft.):Well pumping water level (ft.):


F luid to be pumped:F luid to be pumped:Ph value:S pecific G ravity: Temperature (°F ):S pecific G ravity: Temperature (°F ):Viscos ity:Foreign matter in fluid. (Describe):Foreign matter in fluid. (Describe):

C apacity (US GPM):C apacity (US GPM):Bowl head in feet (TDH):Bowl head in feet (TDH):Bowl setting (column length) (ft.):Bowl setting (column length) (ft.):Type impellers required: (E nclosed only offered on S ubmers ibles .Type impellers required: (E nclosed only offered on S ubmers ibles .C ontact factory for semi-open impeller application.)C ontact factory for semi-open impeller application.)Bowl s ize: No. of stages :Bowl s ize: No. of stages :NOTE : Bowl head = elevation difference in feet between pumpingNOTE : Bowl head = elevation difference in feet between pumpinglevel in well or sump and pump discharge connection pluslevel in well or sump and pump discharge connection plusfriction losses in column and discharge head plus system headfriction losses in column and discharge head plus system headrequirements .)


DR IVE R

Motor Diameter: HP :Motor Diameter: HP :S peed of driver (R PM): Full load amps:S peed of driver (R PM): Full load amps:C urrent characteris tics (ph/): (hz): (volts ):C urrent characteris tics (ph/): (hz): (volts ):Min. velocity past motor for cooling (ft/sec):Min. velocity past motor for cooling (ft/sec):Other driver characteris tics :Other driver characteris tics :

Discharge flange type:Discharge flange type:R iser pipe s ize:R iser pipe s ize:C olumn check valve: (yes) (no) S ize:C olumn check valve: (yes) (no) S ize:E lectrical cable s ize: Length:E lectrical cable s ize: Length:


BOWLAS S E MBLY

DR IVE R

UNDE R GR OUNDDIS C HAR GE HE AD

DIS C HAR GES UBME R S IBLE

DIS C HAR GEAS S E MBLY

R IS E RP IPEAS S E MBLY

R IS E RP IPE

VALVEC HE C K

E NC LOS E DIMPE LLE R S

S UBME R S IBLEMOTOR

Page 4Page 4

VERTICAL PUMP SELECTIONGUIDE SUBMERSIBLE PUMP

VER TICAL PUMP SELECTION GUIDEVER TICAL PUMP SELECTION GUIDE

WE LL OR S UMP C ONDIT IONSWE LL OR S UMP C ONDIT IONS

LOW LIFT (Mixed Flow/AxialFlow) PUMPLOW LIFT (Mixed Flow/AxialFlow) PUMP

Ins ide diameter of surface cas ing or sump (in):Ins ide diameter of surface cas ing or sump (in):Total depth of well or sump (ft.):Total depth of well or sump (ft.):S ump water level: Min.: Max.:S ump water level: Min.: Max.:


F luid to be pumped:F luid to be pumped:If water, is it clear, raw, river, brackish? :If water, is it clear, raw, river, brackish? :S pecific G ravity: Temperature (°F ):S pecific G ravity: Temperature (°F ):Foreign matter in fluid. (Describe):Foreign matter in fluid. (Describe):"Discharge P ressure" or head (ft.):"Discharge P ressure" or head (ft.):

C apacity (US GPM):C apacity (US GPM):C ontinuous flow: Min.: Max.:C ontinuous flow: Min.: Max.:Bowl head in feet (TDH):Bowl head in feet (TDH):Bowl setting (column length) (ft.):Bowl setting (column length) (ft.):C olumn lubrication preferred: (oil) or (water) .C olumn lubrication preferred: (oil) or (water) .Bowl s ize: Type: (mixed flow) (axial flow)Bowl s ize: Type: (mixed flow) (axial flow)

NOTE : Bowl head = elevation difference in feet betweenNOTE : Bowl head = elevation difference in feet betweenpumping liquid level in well or sump and pump dischargepumping liquid level in well or sump and pump dischargeconnection plus friction losses in column and dischargeconnection plus friction losses in column and dischargehead plus system head requirements . Velocity head musthead plus system head requirements . Velocity head mustbe added by user to determine system total head.be added by user to determine system total head.


DR IVE R

Type:S peed of driver (R PM): R atio (if gear):S peed of driver (R PM): R atio (if gear):Non-reverse ratchet des ired:Non-reverse ratchet des ired:C urrent characteris tics (ph): (hz): (volts ):C urrent characteris tics (ph): (hz): (volts ):Other driver characteris tics :Other driver characteris tics :

S trainer (type): (material):S trainer (type): (material):Discharge s ize:Discharge s ize:Discharge type: (150# flange) (plain end) (victaulic groove)Discharge type: (150# flange) (plain end) (victaulic groove)


DR IVE R

OILLUB .

DIS C HAR GEHE ADAS S E MBLY

C OLUMNAND S HAFTAS S E MBLY

BOWLAS S E MBLY

E LE C TR ICMOTORDR IVE

GE AR DR IVEWITH R IGHT ANGLEDIE S E L E NG INE

LUB .WATE R

DIS C HAR GE HE ADABOVE GR OUNDABOVE GR OUND

BE LOW GR OUNDDIS C HAR GE HE ADDIS C HAR GE HE AD

(S TR AINE R OPTIONAL)MIXE D FLOWMIXE D FLOW

(S TR AINE R OPTIONAL)AXIAL FLOW

Page 5

INTAKE DESIGNINTAKE DESIGN

3,0005 6 8 10 15 20 25 30 40 50 60 80 100 150

200250

300400

500700 1000

4,000

6,000

8,000

10,000

15,000

20,000

30,000

40,000

60,000

80,000

100,000

150,000

200,000

300,000

GAL

LON

SPE

RM

INU

TEPE

RPU

MP

GAL

LON

SPE

RM

INU

TEPE

RPU

MP

R E C OMME NDE D S UMP DIME NS IONS IN INC HE SR E C OMME NDE D S UMP DIME NS IONS IN INC HE S

S UMP DIME NS IONS VE R S US FLOWS UMP DIME NS IONS VE R S US FLOW

C B S H YA

(Vc =

2FE

E TPE

RS E

COND

)

A(V

c =2

FEE T

PER

S ECO

ND)

The following sump design recommendations areThe following sump design recommendations arebased on the Hydraulic Institute S tandards 14th E ditionbased on the Hydraulic Institute S tandards 14th E dition1983. These recommendations are not to be considered1983. These recommendations are not to be consideredexact as there are many des ign considerations to evaluateexact as there are many des ign considerations to evaluatein arriving at a properly des igned sump which do notin arriving at a properly des igned sump which do notappear in this section.appear in this section.

The function of the intake is to supply an evenly distributedThe function of the intake is to supply an evenly distributedflow of water to the pump suction bell or suction case. Anflow of water to the pump suction bell or suction case. Anuneven flow is characterized by strong local currents , favorsuneven flow is characterized by strong local currents , favorsthe formation of vortices , and under certain submergencethe formation of vortices , and under certain submergenceconditions will result in the introduction of air into the pumpconditions will result in the introduction of air into the pumpwith a resulting loss of pump performance, accompanied bywith a resulting loss of pump performance, accompanied bynoise, also uneven distribution can increase or decrease thenoise, also uneven distribution can increase or decrease thepower consumption with a change in total dynamic head.power consumption with a change in total dynamic head.There can be vortices which do not appear on the surface,There can be vortices which do not appear on the surface,and these also may have adverse effects .and these also may have adverse effects .

Uneven velocity distribution leads to rotation of portions ofUneven velocity distribution leads to rotation of portions ofthe mass of water about a centerline called vortex motion.the mass of water about a centerline called vortex motion.This centerline may also be moving. Uneven distributionThis centerline may also be moving. Uneven distributionof flow is caused by the geometry of the intake and theof flow is caused by the geometry of the intake and themanner in which water is introduced into the intake frommanner in which water is introduced into the intake fromthe primary source.the primary source.

C alculated low average velocity is not always a proper bas isC alculated low average velocity is not always a proper bas isfor judging the excellence of an intake. High local velocitiesfor judging the excellence of an intake. High local velocitiesin currents and in swirls may be present in intakes whichin currents and in swirls may be present in intakes whichhave very low average velocity. Indeed, the unevenhave very low average velocity. Indeed, the unevendistribution which they represent occurs less in a higherdistribution which they represent occurs less in a highervelocity flow with sufficient turbulence to discourage thevelocity flow with sufficient turbulence to discourage thegradual built-up of a larger and larger vortex in any region.gradual built-up of a larger and larger vortex in any region.Numerous small surface eddies may be present withoutNumerous small surface eddies may be present withoutcaus ing any trouble.caus ing any trouble.

The ideal intake des ign is a direct channel going directlyThe ideal intake des ign is a direct channel going directlyto the pump. Any turn or obstructions are detrimentalto the pump. Any turn or obstructions are detrimentals ince they may cause eddy currents and tend to initiates ince they may cause eddy currents and tend to initiatedeep-cored vortices .deep-cored vortices .

Water should not flow past one pump to reach another.Water should not flow past one pump to reach another.If pumps must be placed in line of flow, it may beIf pumps must be placed in line of flow, it may benecessary to construct an open front cell around eachnecessary to construct an open front cell around eachpump or to put turning vanes under the pump to deflectpump or to put turning vanes under the pump to deflectthe water upward. S treamlining should be used to reducethe water upward. S treamlining should be used to reducethe trail of alternating vortices in the wake of the pumpthe trail of alternating vortices in the wake of the pumpor of other obstructions in the stream flow.or of other obstructions in the stream flow.

F IGUR E 1F IGUR E 1

NOTE :

GE NE R AL

Page 6Page 6

The amount of submergence for a successful operation willThe amount of submergence for a successful operation willdepend greatly on the approaches to the intake and the s izedepend greatly on the approaches to the intake and the s izeof the pump. While specific des ign is generally beyondof the pump. While specific des ign is generally beyondthe scope of the pump manufacture's responsibility, he maythe scope of the pump manufacture's responsibility, he maycomment while the intake layout is still preliminary if he iscomment while the intake layout is still preliminary if he isprovided with the necessary intake drawings reflecting theprovided with the necessary intake drawings reflecting thephys ical limitations of the s ite.phys ical limitations of the s ite.

F igures 1, 2 & 3 provide general sump dimension informationF igures 1, 2 & 3 provide general sump dimension informationfor s ingle and simple multiple pump arrangements . Thesefor s ingle and simple multiple pump arrangements . Theseguidelines cover pumps in the 3,000 to 300,000 GPM range.guidelines cover pumps in the 3,000 to 300,000 GPM range.Additional information for smaller capacity pumps can beAdditional information for smaller capacity pumps can befound at the end of this discuss ion. All of the dimensionsfound at the end of this discuss ion. All of the dimensionsin F igures 1, 2 & 3 are based on the rated capacity of thein F igures 1, 2 & 3 are based on the rated capacity of thepump at des ign head. If the pump is to operate forpump at des ign head. If the pump is to operate fors ignificant periods at a higher capacity, the higher capacitys ignificant periods at a higher capacity, the higher capacityshould be used as the bas is for determining dimensions .should be used as the bas is for determining dimensions .

Dimension C (distance from lip of suction bell to sump floor)Dimension C (distance from lip of suction bell to sump floor)is an average value based on the analys is of many pumps.is an average value based on the analys is of many pumps.The manufacturer should be consulted prior to determiningThe manufacturer should be consulted prior to determininga final valuea final value

Dimension B (distance between pump centerline and backDimension B (distance between pump centerline and backwall) is a suggested maximum dimension. If the positionwall) is a suggested maximum dimension. If the positionof the back wall is dictated by other factors , it may beof the back wall is dictated by other factors , it may benecessary to install a "false" wall for proper intake des ign.necessary to install a "false" wall for proper intake des ign.

Dimension S (minimum sump width for a s ingle pump) canDimension S (minimum sump width for a s ingle pump) canbe increased, but if it is to be made smaller thebe increased, but if it is to be made smaller themanufacturer should be consulted or a model constructedmanufacturer should be consulted or a model constructedto determine the adequacy of the des ign.to determine the adequacy of the des ign.

Dimension H (normal low water level) takes into accountDimension H (normal low water level) takes into accountfriction losses through the inlet screen and approachfriction losses through the inlet screen and approachchannel. The pump should be operated only momentarilychannel. The pump should be operated only momentarilyor infrequently when the sump water level falls below thisor infrequently when the sump water level falls below thislevel.

Minimum submergence (provided with bowlMinimum submergence (provided with bowlperformance data) is normally specified as "Dimensionperformance data) is normally specified as "DimensionH minus Dimension C ".H minus Dimension C ".

Dimensions Y and A are recommended minimum values .Dimensions Y and A are recommended minimum values .These dimensions can be as large as des ired but shouldThese dimensions can be as large as des ired but shouldbe restricted to the limitations indicated on the curve. Ifbe restricted to the limitations indicated on the curve. Ifthe des ign does not include a screen, dimension A shouldthe des ign does not include a screen, dimension A shouldbe considerably longer. The screen or gate widths shouldbe considerably longer. The screen or gate widths shouldnot be substantially less than S , and heights should not benot be substantially less than S , and heights should not beless than H. If the main stream velocity is more than twoless than H. If the main stream velocity is more than twofeet per second, it may be necessary to constructfeet per second, it may be necessary to constructstraightening vanes in the approach channel, increasestraightening vanes in the approach channel, increasedimension A, conduct a sump model test of the installation,dimension A, conduct a sump model test of the installation,or work out some combination of these factors .or work out some combination of these factors .

On multiple pump installations the information presented inOn multiple pump installations the information presented inF igures 1, 2 & 3 applies , with the addition of the followingF igures 1, 2 & 3 applies , with the addition of the followingfactors :

F igure 4 (low velocity and straight line flow to all units )F igure 4 (low velocity and straight line flow to all units )represents the recommended style of pit for multiple pumprepresents the recommended style of pit for multiple pumpinstallations . Velocities in the pump area should approximateinstallations . Velocities in the pump area should approximateone foot per second, although with careful des ign velocitiesone foot per second, although with careful des ign velocitiesof two feet per second or higher may produce satis factoryof two feet per second or higher may produce satis factoryresults . Not recommended would be any des ign feature thatresults . Not recommended would be any des ign feature thatwould introduce eddying (such as an abrupt change in s izewould introduce eddying (such as an abrupt change in s izeof inlet pipe to sump or inlet on one s ide.)of inlet pipe to sump or inlet on one s ide.)

S UMP DIME NS IONS VE R S US FLOWS UMP DIME NS IONS VE R S US FLOWFIGUR E 2F IGUR E 2

SS

MULTIPLE S UMPMULTIPLE S UMP

B

Y

S C R E E N

A

MULTIPLE PUMPMULTIPLE PUMPILLUS TR ATION

S INGLE PUMPS INGLE PUMPILLUS TR ATION

TR AS H R AC KTR AS H R AC K

VcS TR E AM FLOWS TR E AM FLOW

S S S INGLE S UMP ;S S S INGLE S UMP ;

F IGUR E 3 S UMP DIME NS IONS

C

H

PUMP ING WATE R LE VE LPUMP ING WATE R LE VE L

S UMP DIME NS IONSS UMP DIME NS IONS

S2

S2

NOTE :

Page 7Page 7

INTAKE DESIGN


SVe = 1fpsVe = 1fpsS = 1 1/2 TO 2DS = 1 1/2 TO 2D

B

A

Ve

ALT.

Ve = 2fpsVe = 2fps& UP& UP

IF A = LessIF A = LessThan 8DThan 8D

R E C OMME NDE D NOT R E C OMME NDE DNOT R E C OMME NDE D

F igure 5 (multiple pumps in same sump) indicates bestF igure 5 (multiple pumps in same sump) indicates bestoperation without separating walls . If all pumps are inoperation without separating walls . If all pumps are inoperation at the same time, the use of separating wallsoperation at the same time, the use of separating wallswill improve operation. If walls are to be used forwill improve operation. If walls are to be used forstructural purposes , and pumps will operate intermittently,s tructural purposes , and pumps will operate intermittently,flow space should be left behind each wall from the pitflow space should be left behind each wall from the pitfloor up to at least the minimum water level. The wallfloor up to at least the minimum water level. The wallshould not extend upstream beyond the rim of theshould not extend upstream beyond the rim of thesuction bell. Pumps should NOT be placed aroundsuction bell. Pumps should NOT be placed aroundthe edge of a sump either with or without dividing walls .the edge of a sump either with or without dividing walls .

F IGUR E 5

Add wall thicknessto C dist. R ound orogive wall ends .ogive wall ends .Gap at rear of wallGap at rear of wallapprox. D/3.

NOT R E C OMME NDE DR E C OMME NDE D

B

F igure 6 correctly shows a small pipe emptying into aF igure 6 correctly shows a small pipe emptying into alarge pump pit with a gradually increas ing taper section.large pump pit with a gradually increas ing taper section.Abrupt changes in s ize are not des irable. The angleAbrupt changes in s ize are not des irable. The angleshould be as large as poss ible, preferably not less thanshould be as large as poss ible, preferably not less than45 degrees . P it velocities should be kept at less than45 degrees . P it velocities should be kept at less thanone foot per second.

F IGUR E 6

R E C OMME NDE D NOT R E C OMME NDE DNOT R E C OMME NDE D

a MAX. a = 15°MAX. a = 15°PR E FE R R E D a = 10°PR E FE R R E D a = 10°

F igure 7 demonstrates how an abrupt change from inletF igure 7 demonstrates how an abrupt change from inletpipe to pit con be accommodated. P it velocities must bepipe to pit con be accommodated. P it velocities must bekept below one foot per second and the length must equalkept below one foot per second and the length must equalor exceed the values shown. As ratio W/P increases , theor exceed the values shown. As ratio W/P increases , theinlet velocity at P may be increased up to an allowedinlet velocity at P may be increased up to an allowedmaximum of eight feet per second at W/P = 10. In linemaximum of eight feet per second at W/P = 10. In linepumps are not recommended unless the ratio of pit topumps are not recommended unless the ratio of pit topump size is quite large, and pumps are separated by apump size is quite large, and pumps are separated by agenerous margin longitudinally.generous margin longitudinally.

Vp

P

W

Y

WD

YS

V1

Baffles , grating or strainer shouldbe introduced across inlet channelbe introduced across inlet channelat beginning of maximum widthat beginning of maximum widthsection.

NOT R ecommended Unless :NOT R ecommended Unless :

W/P 1.0 1.5 2.5 4.0 10.015D10D8D5D3DY

V 1 2 4 6 8P

W = 5D or more, orW = 5D or more, orV = 0.2fps or less ANDY = S ame as chart toY = S ame as chart to

left1

NOT R E C OMME NDE DNOT R E C OMME NDE DR E C OMME NDE D

S = is greater than 4DS = is greater than 4D

F igure 8 illustrates installation in a tunnel or pipe line.F igure 8 illustrates installation in a tunnel or pipe line.The intake des ign must incorporate an inlet "ell" (suitableThe intake des ign must incorporate an inlet "ell" (suitablefor flows up to 8 feet per second) or suction bell withfor flows up to 8 feet per second) or suction bell withthe pump located at least two pipe diameters above thethe pump located at least two pipe diameters above thetop of the tunnel. The tunnel must be free of air or ittop of the tunnel. The tunnel must be free of air or itmay be necessary to lower the scoop.may be necessary to lower the scoop.

1. The dimension D is generally the diameter of the suction1. The dimension D is generally the diameter of the suctionbell measured at the inlet. This dimension may varybell measured at the inlet. This dimension may varydepending upon pump design. C ontact factory for specificdepending upon pump design. C ontact factory for specificdimensions .2. F igures apply to sumps for clear liquid. C ontact factory2. F igures apply to sumps for clear liquid. C ontact factoryfor fluid/solids mixtures .

FMIN. 2'MIN. 2'

V UP TO 8fpsV UP TO 8fps


D

D

A2

A

R E C OMME NDE D

D D

D

Y

D

NOTE S :

Page 8


Vortexing in pump suction pits is harmful to pit structuresVortexing in pump suction pits is harmful to pit structuresand the pumps themselves . While it is poss ible to eliminateand the pumps themselves . While it is poss ible to eliminatesump problems in the des ign phases , it is much moresump problems in the des ign phases , it is much moredifficult and often expensive to solve problems in existingdifficult and often expensive to solve problems in existingsumps or modified sumps S ump model tests aresumps or modified sumps S ump model tests arerecommended to test the effectiveness of proposed changesrecommended to test the effectiveness of proposed changesbefore construction begins . F igures 9 through 19 illustratebefore construction begins . F igures 9 through 19 illustratetypical sump problems with poss ible solutions .typical sump problems with poss ible solutions .

In F igure 9 the inlet velocity should be reduced by spreadingIn F igure 9 the inlet velocity should be reduced by spreadingthe inflow over a larger area or by adding baffling to changethe inflow over a larger area or by adding baffling to changeits direction and speed. The baffles may be floor mountedits direction and speed. The baffles may be floor mountedextending above the minimum water level or ceiling mountedextending above the minimum water level or ceiling mountedextending close to the floor.extending close to the floor.

In F igure 10 the location of the pumps should be changedIn F igure 10 the location of the pumps should be changedin relation to the direction of inflow.in relation to the direction of inflow.

Add perforated baffleAdd perforated baffleapproximately as indicated.approximately as indicated.

F IGUR E 9F IGUR E 9Original

R elocated

In F igure 11 a cone is added to reduce the poss ibility ofIn F igure 11 a cone is added to reduce the poss ibility ofsubmerged vortex formation.submerged vortex formation.


PUMP ING WATE R LE VE LPUMP ING WATE R LE VE L

C one added to reduce poss ibilityC one added to reduce poss ibilityof submerged vortex formation.of submerged vortex formation.

In F igures 12 and 13 the "no-flow" bays are modified byIn F igures 12 and 13 the "no-flow" bays are modified byeither breaking them open at the back and rounding theeither breaking them open at the back and rounding theedges (F igure 12) or by removing them altogether (figureedges (F igure 12) or by removing them altogether (figure13).

F IGUR E 12F IGUR E 12 F IGUR E 13F IGUR E 13Original

C orrected

R emoved

In F igure 14 sharp corners at gates , screens , etc., areIn F igure 14 sharp corners at gates , screens , etc., areeliminated to allow a smooth flow.eliminated to allow a smooth flow.

In F igure 15 velocity and vortexing is reduced by adding aIn F igure 15 velocity and vortexing is reduced by adding abell extens ion suction plate and splitter to the suction bell.bell extens ion suction plate and splitter to the suction bell.The splitter is attached in line with the flow.The splitter is attached in line with the flow.

F igure 16 shows the use of floating rafts around the pumpF igure 16 shows the use of floating rafts around the pumpcolumn to prevent surface vortices .column to prevent surface vortices .

F igure 17 shows the use of floating large spheres to preventF igure 17 shows the use of floating large spheres to preventsurface vortices .surface vortices .


F loating rafts are usedF loating rafts are usedaround the pump columnaround the pump columnto prevent vortexing.to prevent vortexing.

Large spheres are used toLarge spheres are used toprevent surface vortexes .prevent surface vortexes .

In F igure 18 the clearance between the back wall and theIn F igure 18 the clearance between the back wall and thepump was reduced to improve the velocity pattern to thepump was reduced to improve the velocity pattern to thepump and to reduce the poss ibility of vortex formation.pump and to reduce the poss ibility of vortex formation.

In F igure 19 the direction of inlet flow was changed graduallyIn F igure 19 the direction of inlet flow was changed graduallyby means of parallel turning vanes .by means of parallel turning vanes .

Gate

Added


F IGUR E 15F IGUR E 15WATE R LE VE LWATE R LE VE L

S plitter must be in-line withS plitter must be in-line withflow to prevent submergedflow to prevent submergedvortexing.

PUMP ING

Dashed linesDashed linesshow enlargedbell andsplitter.


V = 3fps and overV = 3fps and over


3/4D Max.

C orrected back wallC orrected back wallOriginal back wallOriginal back wall

The velocity pattern to the pumpThe velocity pattern to the pumpcan often be improved to reducecan often be improved to reducethe poss ibility of vortex formation.the poss ibility of vortex formation.

C OR R E C TION OF E XIS T ING S UMPSC OR R E C TION OF E XIS T ING S UMPS

Page 9Page 9


OPEN LINESHAFT PUMPSOPEN LINESHAFT PUMPS

S PE E D(rpm) 3/4 1 1 3/16 1 1/21 1/2 1 11/16 1 15/16 2 3/16

S HAFT DIAME TE R (INC HE S )S HAFT DIAME TE R (INC HE S )

120120120120120S BR880

60 84 90 96 100

88847872601200 R

S B120 120 120 120 120120120

6060

42 48120 120 120120120120120

SBR1460

54 66 66 72 76

70666060481760 R

S B120 120 120 120 120120120

4842

30 3660 60 6060606060

S BR2900

36 42 48 48 52

48484236363600 R

S B60 60 60 60 606060

3030

Note: R - S tandard R ubber BearingNote: R - S tandard R ubber BearingS B - S olid Bearing (brass , carbon, graphite, teflon, etc.)S B - S olid Bearing (brass , carbon, graphite, teflon, etc.)

The above chart is to aid in the selection of lineshaft bearing spacing for pump column onThe above chart is to aid in the selection of lineshaft bearing spacing for pump column onvertical turbine pumps.vertical turbine pumps.

These recommendations are based on manufacture standards and firs t critical frequencyThese recommendations are based on manufacture standards and firs t critical frequencyshaft calculation.shaft calculation.

S olid type bearings tend to have a s light running noise.S olid type bearings tend to have a s light running noise.

Page 10Page 10

MAXIMUM BEARING SPACING ONMAXIMUM BEARING SPACING ON

SUCTION BARREL SELECTIONSUCTION BARREL SELECTION

R ecommended capacity for a suction barrel can beR ecommended capacity for a suction barrel can bedetermined by calculation of the fluid velocity. R ecommendeddetermined by calculation of the fluid velocity. R ecommendedflow past the largest portion of the pump should not exceedflow past the largest portion of the pump should not exceed5 ft/sec. (V.)5 ft/sec. (V.)

TO C ALC ULATE :TO C ALC ULATE :

GPM x QGPM x Q(D )(D )1

2 - 2(d )(d ) 2V =

where: GPM - amount of flow requiredwhere: GPM - amount of flow requiredQ - constant 0.4085 (cubic feet per sec)Q - constant 0.4085 (cubic feet per sec)D - I.D. of barrel in inchesD - I.D. of barrel in inchesd - O.D. of bowl in inchesd - O.D. of bowl in inches

E XAMPLE :12 3/4" steel suction barrel with a wall12 3/4" steel suction barrel with a wallthickness of 0.375 would have an I.D. of 12"thickness of 0.375 would have an I.D. of 12"

10MC bowl with an O.D. of 9 1/2"10MC bowl with an O.D. of 9 1/2"

F low design of 500 GPMF low design of 500 GPM


V = 2(9 1/2)(9 1/2)-2(12)500 x 0.4085500 x 0.4085

500 x 0.4085500 x 0.4085144 - 90.25

=

=

=53.75204.25 3.8 ft/sec.3.8 ft/sec.

This indicates that this bowl will work in this s ize barrel.This indicates that this bowl will work in this s ize barrel.

1. NPS H should always be considered when placing any1. NPS H should always be considered when placing anypump into a suction can.pump into a suction can.

4. If the suction of the barrel is below the suction inlet4. If the suction of the barrel is below the suction inletof the pump, the fluid velocity can be disregarded inof the pump, the fluid velocity can be disregarded inbarrel selections .barrel selections .

5. If there is sufficient NPS H and efficiency is not5. If there is sufficient NPS H and efficiency is notimportant, it is permiss ible to exceed 5 ft/sec. -important, it is permiss ible to exceed 5 ft/sec. -the maximum recommended ever would be 9 ft/sec.the maximum recommended ever would be 9 ft/sec.

12

V = 2(d )(d )2-21(D )(D )

GPM x QGPM x Q

2. The pump suction should be located (2) barrel2. The pump suction should be located (2) barreldiameters below barrel inlet or (2) suction diametersdiameters below barrel inlet or (2) suction diametersabove the barrel inlet, never allow the suction inlet ofabove the barrel inlet, never allow the suction inlet ofthe pump to be set in the area of the suction barrelthe pump to be set in the area of the suction barrel

3. S uction inlet s ize should have an inlet velocity of equal3. S uction inlet s ize should have an inlet velocity of equalto or less than 5 ft/sec.to or less than 5 ft/sec.

inlet.

P age 11Page 11

F IGUR E NO. 1F IGUR E NO. 1 F IGUR E NO. 2F IGUR E NO. 2

F IGUR E NO. 3F IGUR E NO. 3 F IGUR E NO. 4F IGUR E NO. 4

(1) - It is advantageous to(1) - It is advantageous toknow whether or not a pump will fit in a well and operateknow whether or not a pump will fit in a well and operatenormally. S ince the pump column can be curved, within limits ,normally. S ince the pump column can be curved, within limits ,without being detrimental to pump operation, a well is surveyedwithout being detrimental to pump operation, a well is surveyedto find out in what directions and how sharply it curves throug-to find out in what directions and how sharply it curves throug-hout its length.hout its length.

(2) - The equipment to be used is lis ted(2) - The equipment to be used is lis tedbelow.

(a) A reel of small s teel cable long enough to reach to the(a) A reel of small s teel cable long enough to reach to thedes ired depth.des ired depth.

(b) A cage about two feet long with a diameter about 1/4"(b) A cage about two feet long with a diameter about 1/4"smaller than the I.D. of the well cas ing.smaller than the I.D. of the well cas ing.

(c) A small pulley for the steel cable, having a frame which(c) A small pulley for the steel cable, having a frame whichcan be bolted to a board.can be bolted to a board.

(3) - Attach the pulley to a board thick(3) - Attach the pulley to a board thickenough to carry the weight of the cage and line without bending.enough to carry the weight of the cage and line without bending.S upport the board horizontally at least ten feet above the top ofS upport the board horizontally at least ten feet above the top ofthe well cas ing. The board and supports should be arranged sothe well cas ing. The board and supports should be arranged sothat the location of the pulley can be shifted at least two feet inthat the location of the pulley can be shifted at least two feet inany horizontal direction by s liding the board. A derrick is theany horizontal direction by s liding the board. A derrick is themost convenient support, but if there is no derrick a tripod ormost convenient support, but if there is no derrick a tripod orother structure must be constructed.other structure must be constructed.

R un the cable through the pulley and attach the end to the centerR un the cable through the pulley and attach the end to the centerof the cage. Hang the cage s lightly above the well cas ing andof the cage. Hang the cage s lightly above the well cas ing andmove the pulley until the axis of the cage is in line with themove the pulley until the axis of the cage is in line with thecenter of the well.center of the well.

Next, establish with a straightedge four marks on the well cas ingNext, establish with a straightedge four marks on the well cas ingor floor which can be used to determine two horizontal lines ator floor which can be used to determine two horizontal lines atright angles to each other, pass ing as near to the center of theright angles to each other, pass ing as near to the center of thewell as the cable will permit without the cable being deflected fromwell as the cable will permit without the cable being deflected fromits center pos ition. To s implify the procedure, one of these linesits center pos ition. To s implify the procedure, one of these linesshould be parallel to the board carrying the pulley. Usually theshould be parallel to the board carrying the pulley. Usually thelines are laid off as North-S outh and E ast-West lines .lines are laid off as North-S outh and E ast-West lines .

(4) - Lower the cage ten feet at a(4) - Lower the cage ten feet at atime and measure deflections in the North, S outh, E ast or Westtime and measure deflections in the North, S outh, E ast or Westdirections from the center, as shown in F igure No. 3, at eachdirections from the center, as shown in F igure No. 3, at eachten-foot interval. The vertical distance of the center of the pulleyten-foot interval. The vertical distance of the center of the pulleyabove the level of the place where deflection measurements areabove the level of the place where deflection measurements aremade must also be measured. The center of the pulley is calledmade must also be measured. The center of the pulley is calledthe datum point.the datum point.

F igure No. 1 shows an elevation of a well with a cage in the well,F igure No. 1 shows an elevation of a well with a cage in the well,and F igure No. 3 shows a plan view of the top of the well withand F igure No. 3 shows a plan view of the top of the well witha straightedge in its two positions . In making the measurementsa straightedge in its two positions . In making the measurementsindicated, it must be remembered that the straightedge wasindicated, it must be remembered that the straightedge waslocated by the s ide of the cable instead of the center. S ince thelocated by the s ide of the cable instead of the center. S ince thecable was in the center of the well, the straightedge does not liecable was in the center of the well, the straightedge does not lieexactly on a diameter and deflections must always be measuredexactly on a diameter and deflections must always be measuredon the same sides of the cable that determined the North-S outhon the same sides of the cable that determined the North-S outhand E ast-West lines .and E ast-West lines .

(5) - The cable must not be(5) - The cable must not betouching the s ide of the well cas ing when readings are taken. Bytouching the s ide of the well cas ing when readings are taken. Byrefering to F igure No. 1 it is evident that if the well is crookedrefering to F igure No. 1 it is evident that if the well is crookedthe cable can touch the well cas ing when the cage is loweredthe cable can touch the well cas ing when the cage is loweredpast a bend or spiral. When the cable touches the cas ing, anypast a bend or spiral. When the cable touches the cas ing, anyreadings beyond this point are valueless . It is necessary to shiftreadings beyond this point are valueless . It is necessary to shift

PUR POS E OF S UR VE Y ING A WE LLPUR POS E OF S UR VE Y ING A WE LL

E QUIPME NT NE C E S S AR YE QUIPME NT NE C E S S AR Y

E QUIPME NT S E T-UPE QUIPME NT S E T-UP

C AGE POS IT ION R E ADINGSC AGE POS IT ION R E ADINGS

the datum point so that the cable will not touch the cas ing. Ifthe datum point so that the cable will not touch the cas ing. Ifthe crook is above the water level, this condition can be observed.the crook is above the water level, this condition can be observed.If it is below the water level, it may be suspected if the locationIf it is below the water level, it may be suspected if the locationof the cable remains constant as the cage is lowered. Itof the cable remains constant as the cage is lowered. Itoccas ionally happens , however, that the well is actually s lantingoccas ionally happens , however, that the well is actually s lantingor curving so that it will give a constant reading for a while and,or curving so that it will give a constant reading for a while and,s ince shifting the pulley is apt to introduce errors unless greats ince shifting the pulley is apt to introduce errors unless greatcare is used, it is best to be sure that the cable is touchingcare is used, it is best to be sure that the cable is touchingbefore any shifts are made. If the well is so crooked that thebefore any shifts are made. If the well is so crooked that thecable touches at a second point after being shifted, it iscable touches at a second point after being shifted, it isimposs ible to survey it beyond this point by us ing this method.imposs ible to survey it beyond this point by us ing this method.

If the data is worked up and plotted, it is poss ible to see whetherIf the data is worked up and plotted, it is poss ible to see whetheror not any of the above difficulties are present. Usually, a shiftor not any of the above difficulties are present. Usually, a shiftin one direction will be sufficient, but sometimes it is necessaryin one direction will be sufficient, but sometimes it is necessaryto shift in the other direction also. The pulley should be shiftedto shift in the other direction also. The pulley should be shiftedas far as the surveyor deems necessary and for every shift it isas far as the surveyor deems necessary and for every shift it isimportant that the position (vertically and in both directionsimportant that the position (vertically and in both directionshorizontally) of the datum point be accurately determined. F igurehorizontally) of the datum point be accurately determined. F igureNo. 2 shows a well being surveyed with the datum point shifted.No. 2 shows a well being surveyed with the datum point shifted.

(6) - After the data has been(6) - After the data has beencalculated it should be plotted on graph paper. The deflectionscalculated it should be plotted on graph paper. The deflectionsfor the true view are determined graphically by drawing thefor the true view are determined graphically by drawing thediagonals of parallelograms produced by plotting the displacementdiagonals of parallelograms produced by plotting the displacementreadings as shown in F igure No. 4. C ross-section paper withreadings as shown in F igure No. 4. C ross-section paper withone-inch squares , divided into ten smaller squares to the inch, isone-inch squares , divided into ten smaller squares to the inch, isconvenient for laying out the well. If the depth is laid out withconvenient for laying out the well. If the depth is laid out withten feet to the inch and the cage displacement with ten inches toten feet to the inch and the cage displacement with ten inches tothe inch, it usually results in a satis factory representation of thethe inch, it usually results in a satis factory representation of thewell. The horizontal scale should be large enough to show thewell. The horizontal scale should be large enough to show thedefects in the well clearly, but at the same time it must bedefects in the well clearly, but at the same time it must be

S HIFT ING THE DATUM POINTS HIFT ING THE DATUM POINT

N

S

W E E

N

W

S

WE S TDIS PLAC E ME NT

NOR THDIS PLAC E ME NT DIAGONALC ABLE

NOR THR E ADING

WE S TR E ADING

R E ADINGS TR AIGHTE DGE S TR AIGHTE DGE

R E ADINGELEV

ATIO

NO

FEL

EVAT

ION

OF

DAT

UM

POIN

TD

ATU

MPO

INT

DEP

THO

FC

AGE

DEP

THO

FC

AGE

A

DIS PLAC E ME NT OF C AGEDIS PLAC E ME NT OF C AGEFR OM C E NTE R LINEFR OM C E NTE R LINE

PLOTT ING THE C AGE POS IT IONSPLOTTING THE C AGE POS IT IONS

S HIFT

Page 12Page 12

A SIMPLE METHOD OFSURVEYING A DEEP WELL

A SIMPLE METHOD OFSURVEYING A DEEP WELL

THE WE LL AT ITS S UR FAC ETHE WE LL AT ITS S UR FAC E

recognized that unless the well diameter is plotted to exactly therecognized that unless the well diameter is plotted to exactly thesame scale as the s ide deflection, the well plot will be mis leadingsame scale as the s ide deflection, the well plot will be mis leadingand of practically no value.and of practically no value.

On the plot a straightedge can be used to represent the cable andOn the plot a straightedge can be used to represent the cable andto indicate whether or not the cable was touching the cas ing atto indicate whether or not the cable was touching the cas ing atany point.any point.

If it is determined from the plot that the cable probably did notIf it is determined from the plot that the cable probably did nottouch the well cas ing at any of the readings , during the survey,touch the well cas ing at any of the readings , during the survey,it is an indication that the readings were accurate. In order toit is an indication that the readings were accurate. In order todetermine what s ize of column pipe and bowl diameter can bedetermine what s ize of column pipe and bowl diameter can besafely operated in the well, construct from cardboard a cross-safely operated in the well, construct from cardboard a cross-section of the column and bowl unit to the same scale as usedsection of the column and bowl unit to the same scale as usedin plotting the survey. If the model of column and bowl unit canin plotting the survey. If the model of column and bowl unit canbe placed in the well without binding on the well cas ing, whenbe placed in the well without binding on the well cas ing, wheninserted on the plot of the true view of the survey, it is a goodinserted on the plot of the true view of the survey, it is a goodindication that the actual pump will do likewise.indication that the actual pump will do likewise.

C E NTE R LINE S INDIC ATE C E NTE R OFC E NTE R LINE S INDIC ATE C E NTE R OF

100

90

80

70

60

0

10

20

30

40

50

N S E W TR UEVIE W

DEPT

HOF

WEL

LDE

PTH

OFW

E LL

WATE RLE VE LDATUM POINTS HIFTE D 12°S HIFTE D 12°AT 80 Ft.AT 80 Ft.

E levation of datum point 20 ft. Water level 60 ft.E levation of datum point 20 ft. Water level 60 ft.Datum point shifted 12" North at 80 ft.Datum point shifted 12" North at 80 ft.

DepthC ageFeet

R eadings ofR eadings ofDeflectionsof C ableInches

Displacementof C ageInches

N S WE E WSN

50

40

30

20

10

60

70

80

90

100

0.10 0.15

0.15 0.10 0.30 0.20

0.20 0.20 0.50 0.50

0.10 0.30 0.30 0.90

0.35 1.25

0.50 0.37 0.20 1.48

1.10 0.40 6.75 1.80

8.00 0.40 8.00 2.00

7.80 0.42 11.10 2.30

7.50 0.44 15.00 2.64

FOR MULA

Displacement of cage from center line =Displacement of cage from center line =R eading x (depth of cage + E l. of Datum)R eading x (depth of cage + E l. of Datum)

E l. of DatumE l. of Datum

S ample C alculation at 10 ft. depth:S ample C alculation at 10 ft. depth:

20C age displacement =C age displacement =

0.10 x (10 + 20)0.10 x (10 + 20)= .15"= .15"

Displacement of cage from center line whenDisplacement of cage from center line whendatum point is shifted =datum point is shifted =

*(shift = reading) x*(shift = reading) x(C age Depth + E l. of Datum)(C age Depth + E l. of Datum)

E l. of DatumE l. of Datum- shift

*Add the reading to the shift when shift and reading are on*Add the reading to the shift when shift and reading are onopposite s ides of center line: S ubtract when shift and readingopposite s ides of center line: S ubtract when shift and readingare on same side of center line.are on same side of center line.

S ample C alculation at 80 ft. depth:S ample C alculation at 80 ft. depth:

C age diplacement =C age diplacement =

(12 - 8) x(12 - 8) x(80 + 20)(80 + 20)

20- 12 = 8"- 12 = 8"

S ince distance A (see F igure No. 2 ) is greater than the shift,S ince distance A (see F igure No. 2 ) is greater than the shift,it is evident that the cage displacement is south from theit is evident that the cage displacement is south from thecenter line.center line.

Formula No. 1 is used in all E AS T calculations in this case,Formula No. 1 is used in all E AS T calculations in this case,but if there is a shift in the E ast-West direction, Formulabut if there is a shift in the E ast-West direction, FormulaNo. 2 would have to be used in the same manner as for theNo. 2 would have to be used in the same manner as for theNorth-S outh direction.North-S outh direction.

DIS PLAC E ME NTOF C AGEOF C AGE

No. 1No. 1

No. 2No. 2

Page 13Page 13

SAMPLE DATA, CALCULATIONSAND PLOT 18" WELL

SAMPLE DATA, CALCULATIONSAND PLOT 18" WELL

Open line shaft pumps utilize neoprene line shaft bearingsOpen line shaft pumps utilize neoprene line shaft bearingswhich must be kept wet when the unit is operating. Afterwhich must be kept wet when the unit is operating. Afterthe pump liquid fills the column pipe, the bearings arethe pump liquid fills the column pipe, the bearings arekept lubricated by this liquid. At start-up and shut-down,kept lubricated by this liquid. At start-up and shut-down,however, certain precautions must be taken to providehowever, certain precautions must be taken to providelubrication to these bearings .lubrication to these bearings .

S TAR T-UP : Under normal conditions if the static waterS TAR T-UP : Under normal conditions if the static waterlevel is 30 feet of less , prelubrication is not required s incelevel is 30 feet of less , prelubrication is not required s incethe bearings will hold enough moisture to provide initialthe bearings will hold enough moisture to provide initial

lubrication. On deeper settings , however, it is necessary thatlubrication. On deeper settings , however, it is necessary thatthe bearings receive prelubrication as outlined below.the bearings receive prelubrication as outlined below.

S HUT-DOWN: Non-R everse R atchet mechanisms mounted inS HUT-DOWN: Non-R everse R atchet mechanisms mounted inthe driver are recommended on units with settings of 50 feetthe driver are recommended on units with settings of 50 feetor more. The Non-R everse R atchet prevents reverse rotationor more. The Non-R everse R atchet prevents reverse rotationdue to backflow, thus eliminating post lubrication requirements .due to backflow, thus eliminating post lubrication requirements .If Non-reverse ratchets are not employed, post lubricationIf Non-reverse ratchets are not employed, post lubricationmust be provided using methods s imilar to those outlinedmust be provided using methods s imilar to those outlinedbelow.

PR E S S UR E ONS OLE NOID

VALVE

OUTE R C OLUMN S IZEOUTE R C OLUMN S IZE(INC HE S )

S OLE NOID VALVE AND F ITT ING S IZES OLE NOID VALVE AND F ITT ING S IZEINC HE S

5"S MALLE R 6" AND 8"6" AND 8" 10" AND

LAR GE R

1-10 PS I

11-75 PS I11-75 PS I

76-150 PS I76-150 PS I

1-1/4"

1"

3/4" 1"

1-1/4"

1-1/2"

1-1/2"

2"

2-1/2"

S OLE NOID VALVE AND F ITT INGSS OLE NOID VALVE AND F ITT INGS

S TATIC WATE R LE VE LS TATIC WATE R LE VE L(FE E T)0'-30'

T IME DE LAYTIME DE LAY(MINUTE S )

31'-70'

71'-150'

151'-250'

251'-350'

351'-450'

3-1/2 min.3-1/2 min.

2-1/2 min.2-1/2 min.

1-1/2 min.1-1/2 min.

1 min.1 min.

1/2 min.1/2 min.

8" TO 10"8" TO 10"

TANK & F ITT ING S IZE STANK & F ITT ING S IZE S

1"

2-1/2" TO 4"2-1/2" TO 4"

4-1/2" TO 6"4-1/2" TO 6"

F ITT INGS

TIME DE LAY R E LAYTIME DE LAY R E LAY

OUTE RC OLUMN

S IZE

30'-300'

TANK50 GAL.50 GAL. 100 GAL.

TANKF ITT INGS1-1/2"

TANK200 GAL.

F ITT INGS2"

14"

12"

30'-200'

30'-125'

30'-70'

30'-50'

S IZE

S TATIC WATE R LE VE L (FE E T)S TAT IC WATE R LE VE L (FE E T)

50'-150'

70'-200'

125'-300'

200'-400'

300'-400'

150'-300'

200'-400'

300'-400'

NOTE S :T IME DE LAY S E TT ING BAS E DTIME DE LAY S E TT ING BAS E DON PR OPE R S OLE NOIDON PR OPE R S OLE NOID

0-30 FT. S E TT ING NO0-30 FT. S E TT ING NO

S E LE C T ION

PR E -LUBR IC ATION R E QUIR E D.PR E -LUBR IC ATION R E QUIR E D.

PUMP INGPLANT PANE LPLANT PANE L

PR E -LUBETANK

GATEVALVE

BUTTE R FLYVALVE

T IME DE LAYR E LAY

FLOATVALVE

S OLE NOID VALVE C HE C KVALVE C HE C K

BUTTE R FLYVALVE

T IME DE LAYTIME DE LAYR E LAY

C ABLE (1)C ABLE (1)S OLE NOID

GATE VALVEGATE VALVE

C HE C K VALVEC HE C K VALVE

F IGUR E 1F IGUR E 1 F IGUR E 2

F IGUR E 3F IGUR E 3 F IGUR E 4

PLANT PANE LPLANT PANE LPUMP ING

PLANT PANE LPLANT PANE LPUMP ING

PRELUBRICATION RECOMMENDATION FOR WATERLUBRICATED OPEN SHAFT TURBINE PUMPSPRELUBRICA RECOMMENDA FOR WATERLUBRICATED OPEN SHAFT TURBINE PUMPS

There are two commonly used methods to determine theThere are two commonly used methods to determine thewater level in wells - airline and gauge, or an electricwater level in wells - airline and gauge, or an electricsounder.

The airline method can use a standard pressure gauge,The airline method can use a standard pressure gauge,indirect reading depth gauge, or direct reading depthindirect reading depth gauge, or direct reading depthgauge.INS TALLATION: The airline is installed so that the lower end is approx.INS TALLATION: The airline is installed so that the lower end is approx.2' from the inlet of the pump - for reliable readings the airline should2' from the inlet of the pump - for reliable readings the airline shouldextend 20' below low water level if poss ible. All airline joints mustextend 20' below low water level if poss ible. All airline joints mustbe air tight for proper operation. The upper end of the airline isbe air tight for proper operation. The upper end of the airline isconnected to a gauge and snifter valve. E xact vertical length of theconnected to a gauge and snifter valve. E xact vertical length of theairline must be recorded at installation, by noting on the face of theairline must be recorded at installation, by noting on the face of thegauge. Use as many nylon ties as necessary to firmly attach the airlinegauge. Use as many nylon ties as necessary to firmly attach the airlineto the column and bowl assembly without collaps ing the airline.to the column and bowl assembly without collaps ing the airline.ME THOD OF OPE R ATION: A tire pump is used to expel all waterME THOD OF OPE R ATION: A tire pump is used to expel all waterfrom the airline, when this point is reached the gauge reading willfrom the airline, when this point is reached the gauge reading willremain constant. The maximum maintained pressure is equal toremain constant. The maximum maintained pressure is equal tothe height of water above the end of the airline (DIM Z).the height of water above the end of the airline (DIM Z).INDIR E C T R E ADING DE PTH GAUGE (F IXE D DIAL): Pump up airlineINDIR E C T R E ADING DE PTH GAUGE (F IXE D DIAL): Pump up airlineuntil maximum pressure (all water is expelled from airline) isuntil maximum pressure (all water is expelled from airline) isreached, reading on gauge will be distance "Z". Water level (belowreached, reading on gauge will be distance "Z". Water level (belowsurface) is obtained by subtracting "Z" from "Y" (W.L. = Y - Z).surface) is obtained by subtracting "Z" from "Y" (W.L. = Y - Z).DIR E C T R E ADING DE PTH GAUGE (MOVABLE DIAL): S et the movableDIR E C T R E ADING DE PTH GAUGE (MOVABLE DIAL): S et the movablegauge dial so that the length of airline (Y ) is at the pin stopgauge dial so that the length of airline (Y ) is at the pin stop(gauge pointer pos ition at 0 pressure). Pump airline to maximum(gauge pointer pos ition at 0 pressure). Pump airline to maximumpressure, gauge will read water level (Y - Z) direct.pressure, gauge will read water level (Y - Z) direct.PR E S S UR E GAUGE : A pressure gauge can be used by convertingPR E S S UR E GAUGE : A pressure gauge can be used by convertingPS I to feet of water as follows:PS I to feet of water as follows:Feet of Water = PS I x 2.31Feet of Water = PS I x 2.31Operation would be identical to indirect reading gauge.Operation would be identical to indirect reading gauge.

AIR LINE ME THOD:AIR LINE ME THOD:

X = Y - ZX = Y - ZE XAMPLE :

Y = 100 ft.Y = 100 ft.Z = 15 lb./sq. in.Z = 15 lb./sq. in.

= 15 x 2.31 = 34.65 ft.= 15 x 2.31 = 34.65 ft.X = ?X = 100 - 34.65X = 100 - 34.65

= 65.35 ft.= 65.35 ft.*If the effective length of the airline is not known, it may be*If the effective length of the airline is not known, it may bedetermined by measuring the actual water level. When thedetermined by measuring the actual water level. When thepump is idle by some other method, and comparing it to thepump is idle by some other method, and comparing it to themaximum reading obtained on the direct reading gauge ormaximum reading obtained on the direct reading gauge oradding to the maximum reading of the indirect gauge.adding to the maximum reading of the indirect gauge.

The electric sounder consists essentially of a battery, a spoolThe electric sounder consists essentially of a battery, a spoolof well insulated waterproof wire and a millivolt meter. Oneof well insulated waterproof wire and a millivolt meter. Oneterminal of the battery is connected to the pump head and theterminal of the battery is connected to the pump head and theother through the potentiometer to one end of the spool ofother through the potentiometer to one end of the spool ofwire. The other end of the wire from the spool must bewire. The other end of the wire from the spool must beprotected so that it will not close the circuit, if it should bumpprotected so that it will not close the circuit, if it should bumpagainst the pump in being lowered into the well, but at theagainst the pump in being lowered into the well, but at thesame time so arranged that the circuit will be closed whensame time so arranged that the circuit will be closed whenthe end of the wire contacts the water in the well. The wirethe end of the wire contacts the water in the well. The wirefrom spool, then, is lowered into the well until; the needle offrom spool, then, is lowered into the well until; the needle ofthe potentiometer deflects , indicating that the water levelthe potentiometer deflects , indicating that the water levelhas been reached and the contact closed. The wire is thenhas been reached and the contact closed. The wire is thenproperly marked, pulled from the well and measured with aproperly marked, pulled from the well and measured with asteel tape to determine the water level. (It is poss ible tosteel tape to determine the water level. (It is poss ible tocalibrate the spool of wire so that it is direct reading.)calibrate the spool of wire so that it is direct reading.)

E LE C TR IC S OUNDE R ME THODE LE C TR IC S OUNDE R ME THOD

X = Depth to water in feet (this is unknown).X = Depth to water in feet (this is unknown).Y = Length of air line in feet (this was measured at installation).Y = Length of air line in feet (this was measured at installation).Z = Water pressure on airline, in feet head of water. S tandardZ = Water pressure on airline, in feet head of water. S tandard

gauge reads in lb./sq. in. Multiply reading by 2.31 to convertgauge reads in lb./sq. in. Multiply reading by 2.31 to convertto feet of water. Altitude type gauge reads directly in feetto feet of water. Altitude type gauge reads directly in feetof water.of water.

INLE T TO PUMPINLE T TO PUMPAPPR OX. 2' ABOVEAPPR OX. 2' ABOVE

Y

X

LE VE LWATE R

Z

AIR LINE

AIR LINEAIR LINEF ITT ING

NIPPLE

TE E

BUS HING

S NIFTE RVALVE

R E ADING GAUGER E ADING GAUGE

TIR EPUMP

NYLON TIE SNYLON TIE S

Page 15Page 15

WATER LEVEL TESTINGWATER LEVEL TESTING

Pump curves are generally based on standard motorPump curves are generally based on standard motorspeeds . For performance of pumps at speeds other thanspeeds . For performance of pumps at speeds other thanthose published, it is necessary to calculate new C apacity,those published, it is necessary to calculate new C apacity,Head, and BHP.Head, and BHP.

The following "Affinity Laws" are used in speed variationThe following "Affinity Laws" are used in speed variationcalculations :

1. The capacity of a turbine pump varies in direct1. The capacity of a turbine pump varies in directproportion to the speed.proportion to the speed.

2. The head of a turbine pump varies in proportion to the2. The head of a turbine pump varies in proportion to thesquare of the speed.square of the speed.

3. The horsepower varies in proportion to the cube of the3. The horsepower varies in proportion to the cube of thespeed.

In general, it is good engineering practice not to increaseIn general, it is good engineering practice not to increasethe speed of a turbine pump designed for 1760 R PM tothe speed of a turbine pump designed for 1760 R PM tomore than 2200 R PM. At higher R PM harmonic or shaftmore than 2200 R PM. At higher R PM harmonic or shaftvibration may occur caus ing excess ive wear in the pump.vibration may occur caus ing excess ive wear in the pump.

FOR MULAS :

Q 2 = 1QN 2

1N

N 1

2NH 1=2H ( )

2

3

( )BHP 2 = 1BHPN 2

1N

Q = Quantity in GPMQ = Quantity in GPMH = Head in FeetH = Head in FeetBHP = Brake HorsepowerBHP = Brake HorsepowerN = S peed in R PM (published)N = S peed in R PM (published)N = S peed in R PM (required)N = S peed in R PM (required)

NOTE : DO NOT E XC E E D MINIMUM TR IM DIAME TE RNOTE : DO NOT E XC E E D MINIMUM TR IM DIAME TE RINDIC ATE D ON S TANDAR D C ATALOG C UR VE .INDIC ATE D ON S TANDAR D C ATALOG C UR VE .

1

2

E XAMPLEAn impeller operating at 1760 R PM is rated to deliver 900 GPM at 76 Feet of Head, and requiresAn impeller operating at 1760 R PM is rated to deliver 900 GPM at 76 Feet of Head, and requires20.3 BHP to drive it. What will the effect of changing the speed to 1460 R PM?20.3 BHP to drive it. What will the effect of changing the speed to 1460 R PM?

The direct ratio of speeds will be:The direct ratio of speeds will be:

1460 R PM C APAC ITY will be:1460 R PM C APAC ITY will be:

1460 R PM HE AD will be;1460 R PM HE AD will be;

The cube of the ratio will be:The cube of the ratio will be: 0.82955 x 0.82955 x 0.82955 = 0.570850.82955 x 0.82955 x 0.82955 = 0.57085

0.68815 x 76 = 52.30 Feet of Head0.68815 x 76 = 52.30 Feet of Head

0.82955 x 0.82955 = 0.688150.82955 x 0.82955 = 0.68815

0.82955 x 900 = 746.59 GPM0.82955 x 900 = 746.59 GPM

0.8295514601760

=

0.57085 x 20.3 = 11.59 BHP0.57085 x 20.3 = 11.59 BHP1460 R PM BR AKE HOR S E POWE R will be:1460 R PM BR AKE HOR S E POWE R will be:

The square of the ratio will be:The square of the ratio will be:

The efficiency is still another factor to be considered, but is not serious ly altered forThe efficiency is still another factor to be considered, but is not serious ly altered forsmall changes in speed. If the above pump had an efficiency of 85% at 900 GPM when operatingsmall changes in speed. If the above pump had an efficiency of 85% at 900 GPM when operatingat 1760 R PM, the efficiency would still be approximately 85% at 746.59 GPM when operating at 1460 R PM.at 1760 R PM, the efficiency would still be approximately 85% at 746.59 GPM when operating at 1460 R PM.

R PM GPM HE AD HP0.50330.63270.79551400

HPHE ADGPMR PM

1450 0.8239 0.6788150015501600165017001760 R E FE R TO PE R FOR MANC E C UR VER E FE R TO PE R FOR MANC E C UR VE18001850190019502000205021002150220022502300235024002450 8.0004.0002.0003520

MULTIPLIE R S FOR PUMP PE R FOR MANC E AT VAR IOUS S PE E DS US INGMULTIPLIE R S FOR PUMP PE R FOR MANC E AT VAR IOUS S PE E DS US ING1760 R PM AS R E FE R E NC E S PE E D1760 R PM AS R E FE R E NC E S PE E D

0.55920.61910.72640.85230.68310.77560.88070.75130.82640.90910.82400.87890.93750.90120.93300.9659

1.06971.04601.02271.16141.10491.05111.25811.16541.07951.36011.22761.10801.46741.29131.13641.58021.35671.16481.69871.42371.19321.82301.49231.22161.95311.56251.25002.08931.63431.27842.23171.70781.30682.38051.78281.33522.53571.85951.36362.69751.93781.3920

250025502600265027002750280028502900295030003050310031503200325033003350340034503500

1.4205 2.0177 2.86603.04152.09921.44893.22392.18231.47733.41352.26711.50573.61042.35341.53413.81472.44141.56254.02662.53101.59094.24622.62221.61934.47362.71501.64774.70902.80941.67614.95252.90551.70455.20433.00311.73305.46453.10241.76145.73323.20331.78986.01053.30581.81826.29673.40991.84666.59183.51561.87506.89603.62301.90347.20943.73191.93187.53223.84251.96027.86443.95471.9886

Page 16Page 16

FORMULA FOR CHANGING PUMP SPEEDCHANGES IN PERFORMANCE

FORMULA FOR CHANGING PUMP SPEEDCHANGES IN PERFORMANCE

IMPELLER DIAMETER TRIM PROCEDUREIMPELLER DIAMETER TRIM PROCEDURECHANGES IN PERFORMANCECHANGES IN PERFORMANCE

The effect of changing the outer diameter is to decreaseThe effect of changing the outer diameter is to decreasethe peripheral speed of the impeller which has exactly thethe peripheral speed of the impeller which has exactly thesame effect as reducing the rotative speed without alteringsame effect as reducing the rotative speed without alteringthe diameter. The effect is to change the Head generatedthe diameter. The effect is to change the Head generatedin proportion to the square of the speed, or the square ofin proportion to the square of the speed, or the square ofthe diameter, according to the fundamental formula:the diameter, according to the fundamental formula:

V2= 2GHGravity (32.17 feet per second)G ravity (32.17 feet per second)=G

H = Head (in feet)Head (in feet)

When the peripheral speed is changed, however, theWhen the peripheral speed is changed, however, thevelocity of the water flowing through the impeller is changedvelocity of the water flowing through the impeller is changedin direct proportion. S ince this changes the quantity of waterin direct proportion. S ince this changes the quantity of waterdelivered, both changes must be considered when trimmingdelivered, both changes must be considered when trimmingan impeller.an impeller.

There is still a third factor to be considered. Assuming thereThere is still a third factor to be considered. Assuming thereis no major change in the speed (with the quantity in directis no major change in the speed (with the quantity in directproportion to the diameter, and the head in proportion toproportion to the diameter, and the head in proportion tothe square) the work done (or power required) will be asthe square) the work done (or power required) will be asthe product of the two which is proportional to the cube ofthe product of the two which is proportional to the cube ofthe diameter.the diameter.

E XAMPLE :An impeller of 9.313 inch outs ide diameter (of vanes) is ratedAn impeller of 9.313 inch outs ide diameter (of vanes) is ratedto deliver 900 GPM at 76 Feet of Head, and requires a driverto deliver 900 GPM at 76 Feet of Head, and requires a driverof 20.3 BHP. (Data taken form a published curve.) What willof 20.3 BHP. (Data taken form a published curve.) What willbe the effect of changing the diameter to 8.750 inches?be the effect of changing the diameter to 8.750 inches?S OLUTION:The direct ratio of diameters will be: 8.750 - 9.313 = 0.93955The direct ratio of diameters will be: 8.750 - 9.313 = 0.93955S o the new Quantity will be: 0.93955 x 900 = 845.59 GPMS o the new Quantity will be: 0.93955 x 900 = 845.59 GPMThe square of the ratio will be: 0.93955 x 0.93955 = 0.88275The square of the ratio will be: 0.93955 x 0.93955 = 0.88275S o the new Head will be: 0.88275 x 76 = 67.09 Feet of HeadS o the new Head will be: 0.88275 x 76 = 67.09 Feet of HeadThe cube of the ration will be: 0.93955 x 0.93955 x 0.93955 = 0.82938The cube of the ration will be: 0.93955 x 0.93955 x 0.93955 = 0.82938

The efficiency is still another factor to be considered. It isThe efficiency is still another factor to be considered. It isnot serious ly altered for small changes in diameter. R efernot serious ly altered for small changes in diameter. R eferto bowl performance curves for actual change in efficiency.to bowl performance curves for actual change in efficiency.

S ince a pump is made of several bowls with impellers , it isS ince a pump is made of several bowls with impellers , it isonly necessary to figure one impeller. The new head isonly necessary to figure one impeller. The new head ismultiplied by the number of stages for the whole pump. Themultiplied by the number of stages for the whole pump. Thequantity and efficiency, however, will be as calculated forquantity and efficiency, however, will be as calculated forthe s ingle impeller, as all will perform the same in series .the s ingle impeller, as all will perform the same in series .

This procedure applies in the same way to open andThis procedure applies in the same way to open andenclosed impellers .enclosed impellers .

*All impellers require lower shroud removal for all trim*All impellers require lower shroud removal for all trimdiameters . S emi-open impeller trim diameters arediameters . S emi-open impeller trim diameters aremeasured the same way.measured the same way.

FULL DIAFULL DIA

TR IM DIATR IM DIA

A

A

S o the new power will be: 0.82938 x 20.3 = 16.84 BHPS o the new power will be: 0.82938 x 20.3 = 16.84 BHP

Page 17

40

60

80

100

120

0 20 40 60

160

140

C APAC ITY IN %C APAC ITY IN %

90

80

70

100

HEA

DIN

%

80 100 120 140BR

AKE

HO

RSE

POW

E RIN

%BR

AKE

HO

RSE

POW

ERIN

%

ABCDEF

AB

C

EF

A = IDE ALA = IDE AL

B = .040"

C = .080"

D = .160"

E = .240"

F = .320"

D

The above chart indicates the approximate effect of rais ing semi-open impellers from theirThe above chart indicates the approximate effect of rais ing semi-open impellers from theirideal (A) operating position. R ais ing the impellers increases the clearance between impellerideal (A) operating position. R ais ing the impellers increases the clearance between impellerand bowl seat and reduces the performance accordingly. The chart is general and will notand bowl seat and reduces the performance accordingly. The chart is general and will notbe exactly correct for any particular pump model s ince each model will react differently. 100%be exactly correct for any particular pump model s ince each model will react differently. 100%head and capacity are to be taken as the head and capacity of the pump at peak efficiency. -head and capacity are to be taken as the head and capacity of the pump at peak efficiency. -E XAMPLE : If a particular pump delivers 250 GPM at 50' head at peak efficiency when theE XAMPLE : If a particular pump delivers 250 GPM at 50' head at peak efficiency when theimpellers are properly adjusted, rais ing the impellers 0.080" would reduce the capacity toimpellers are properly adjusted, rais ing the impellers 0.080" would reduce the capacity toapproximately 181 GPM (72 1/2% of 250 GPM) while maintaining the 50' head - or conversely,approximately 181 GPM (72 1/2% of 250 GPM) while maintaining the 50' head - or conversely,the pump would deliver 250 GPM at 37 1/2' head (75% of 50'.) The horsepower would bethe pump would deliver 250 GPM at 37 1/2' head (75% of 50'.) The horsepower would beabout 91 1/2% of the previous horsepower.about 91 1/2% of the previous horsepower.

Page18

EFFECTS OF RAISINGSEMI-OPEN IMPELLERSEFFECTS OF RAISING

SEMI-OPEN IMPELLERS

The formula for Velocity Head is :The formula for Velocity Head is :

hv = vhv = v 22g

where "g" is the acceleration due towhere "g" is the acceleration due togravity (32.174 feet per second)gravity (32.174 feet per second)

By knowing the head we can transpose the formula to read:By knowing the head we can transpose the formula to read:2ghv = this obtains the velocity.this obtains the velocity.

Velocity can also be obtained by applying the values to these formulas .Velocity can also be obtained by applying the values to these formulas .

where hv = velocity headwhere hv = velocity head

v = velocity in feet/secondv = velocity in feet/second

GPM = Gallons per minuteGPM = Gallons per minute

D = I.D. of column pipeD = I.D. of column pipe

d = O.D. of shaft or oil tubed = O.D. of shaft or oil tube

A (area) = 0.7854 x (D+d)(D-d)A (area) = 0.7854 x (D+d)(D-d)

The Velocity Head (Head due to Velocity) of moving water at a given velocity is the equivalent Head throughThe Velocity Head (Head due to Velocity) of moving water at a given velocity is the equivalent Head throughwhich it would have to fall to acquire the same velocity, or the Head necessary to accelerate water. Thewhich it would have to fall to acquire the same velocity, or the Head necessary to accelerate water. TheVelocity head must always be considered when accurate testing is required, but normally is such a negligibleVelocity head must always be considered when accurate testing is required, but normally is such a negligibleamount that its factor is a small value when figuring total Head conditions . It is important to consider Velocityamount that its factor is a small value when figuring total Head conditions . It is important to consider VelocityHead when your Total Head values are low, which occurs in Axial F low pumps or when S uction Lift valves areHead when your Total Head values are low, which occurs in Axial F low pumps or when S uction Lift valves arehigh, such as in centrifical pump applications .high, such as in centrifical pump applications .

hv = 0.0155vhv = 0.0155v 2 where v = 0.4085 x GPMv = 0.4085 x GPMD2 or v = 0.321 x GPMv = 0.321 x GPM

Areahv = 0.00259 (GPM)hv = 0.00259 (GPM) 2

4D

E xample

C alculations Based on: GPM = 1219.35C alculations Based on: GPM = 1219.35D = 10" (P ipe O.D. = 10.750, Wall thickness 0.330)D = 10" (P ipe O.D. = 10.750, Wall thickness 0.330)d = 1.6875d = 1.6875

0.321 x GPM0.321 x GPM( AR E A (

2or

77.723530.321 x 1219.350.321 x 1219.35

( (2

77.72353391.41135

( (2

hv = 0.0155hv = 0.0155 (5.035944) 2 = 0.39309

0.00259 x GPM0.00259 x GPMD 4

2hv =hv =

0.00259 x 1219.350.00259 x 1219.35hv =hv = 410

2

0.00259 x 1486814.4220.00259 x 1486814.422hv =hv =10,000

3850.849354hv =hv =10,000

= 0.38508= 0.38508

hv = 0.0155v where v =hv = 0.0155v where v =2

hv = 0.0155v where v =hv = 0.0155v where v =2

2hv = 0.0155v where v =hv = 0.0155v where v =

Notes :to calculate velocity in column pipe withto calculate velocity in column pipe withlineshaft or oil tubing the following formulalineshaft or oil tubing the following formulais used to determine the area.is used to determine the area.

Page 19Page 19

VELOCITY HEAD

S pecific speed is the speed in R PM at which a given impeller would operate if reduced proportionallyS pecific speed is the speed in R PM at which a given impeller would operate if reduced proportionallyin s ize so as to deliver a capacity of one GPM at one foot of head.in s ize so as to deliver a capacity of one GPM at one foot of head.


Ns =Ns =R /MIN x (GAL/MIN)R /MIN x (GAL/MIN) .5

WHE R E : R /MIN = Pump rotational speed in revolutions per minute.R /MIN = Pump rotational speed in revolutions per minute.GAL/MIN = Pump discharge in U.S . gallons per minuteGAL/MIN = Pump discharge in U.S . gallons per minute

FT = Total bowl head per stage in feet of liquid pumpedFT = Total bowl head per stage in feet of liquid pumped

FOR ME TR IC :FOR ME TR IC :

M

.5R /MIN x (M /H)R /MIN x (M /H)Ns =Ns =

3.75

.75FT

WHE R E : M /H = Pump discharge in cubic meters per hourM /H = Pump discharge in cubic meters per hour

M = Total bowl head per stage in meters of liquid pumpedM = Total bowl head per stage in meters of liquid pumped

1. The capacity and head should be selected at the best efficiency point of the largest diameter1. The capacity and head should be selected at the best efficiency point of the largest diameterimpeller used in the pump.impeller used in the pump.

2. S pecific S peed (Ns) is always calculated for a s ingle stage.2. S pecific S peed (Ns) is always calculated for a s ingle stage.3. S pecific S peed (Ns) of any given pump is the same at all rotative speeds .3. S pecific S peed (Ns) of any given pump is the same at all rotative speeds .4. Low specific speed (Ns) indicates the pump design is for low capacity and high head.4. Low specific speed (Ns) indicates the pump design is for low capacity and high head.5. High specific speed (Ns) indicates the pump design is for high capacity and low head.5. High specific speed (Ns) indicates the pump design is for high capacity and low head.

14.375 .75.51780 x (200)1780 x (200)

Ns =

E XAMPLER /MIM = 1780R /MIM = 1780

GAL/MIN = 200GAL/MIN = 200

FT = 14.375FT = 14.375

Ns =25173.00141

7.38254 = 3409.80= 3409.80

orFT.75

R /MIN x GAL/MINNs =Ns =

Ns =Ns =R /MIN x GAL/MINR /MIN x GAL/MIN

.75FT

or

FT.75.5R /MIN x (GAL/MIN)R /MIN x (GAL/MIN)

Ns =

WHE R E :

1780 x1780 xNs =Ns =

200.7514.375

= 3409.80= 3409.807.3825425173.00141

Ns =Ns =

3

Page 20Page 20

SPECIFIC SPEED

The chart and illustration represented is the recommendedThe chart and illustration represented is the recommendedacceptable vibration limits for vertical pumps. Vibrations inacceptable vibration limits for vertical pumps. Vibrations inexcess of the chart values may be acceptable if they showexcess of the chart values may be acceptable if they showno continued increase over long periods of time and thereno continued increase over long periods of time and thereis no other indication of damage, such as an increase inis no other indication of damage, such as an increase inbearing clearance or noise level. C onvers ion formulas forbearing clearance or noise level. C onvers ion formulas forvibration readings are as follows:vibration readings are as follows:

60

1

100

5'

D = 1.910 x 10D = 1.910 x 10 4 vf

v = 3.696 x 10v = 3.696 x 10 a3f

a = 2.704 x 10 vfa = 2.704 x 10 vf -4

where,D = Displacement, peak toD = Displacement, peak to

peak, in mils (0.001 inches)peak, in mils (0.001 inches)

v = Velocity, peak, in inchesv = Velocity, peak, in inchesper second

a = Acceleration, peak, in G 'sa = Acceleration, peak, in G 's

f = F requency in cycles perf = F requency in cycles perminute

200

300

400

500

600

800

1000

1200

1500 1800

2000

3000

3600

4000

5000

6000

2

3

4

5

610'

8

10

15

20'

0.1"/S E C .

0.2"/S E C .

0.2"/S E C .0.3"/S E C .

0.3"/S E C .0.4"/S E C .

0.6"/S E C .0.8"/S E C .1.0"/S E C .

0.001G

ACCE LE R ATION

ACCE LE R ATION

G 's (PE AK )G 's (PE AK )

0.01G

VE LOC ITY

(PE AK )

0.1G

1.5G

1.0G

0.5G

5' 10'

20'

5' OR LE S S5' OR LE S S

DIST

ANCE

FROM

BASE

TODI

S TAN

CEFR

OMBA

S ETO

POIN

TOF

MEA

SUR E

MEN

T-FE

E T*

POIN

TOF

MEA

SUR E

MEN

T-FE

E T*

V ibration F requency C ycles Per Minute (R eadings F iltered)Vibration F requency C ycles Per Minute (R eadings F iltered)

*Measure Vibration at top motor bearing*Measure Vibration at top motor bearing AC C E PTABLE F IE LD VIBR ATION LIMITS FOR VE R T IC AL PUMPSAC C E PTABLE F IE LD VIBR ATION LIMITS FOR VE R T IC AL PUMPS(NON-R IG ID S TR UC TUR E S ) - Based on Hydraulic Institute(NON-R IG ID S TR UC TUR E S ) - Based on Hydraulic InstituteS tandards , 14th E dition, 1983S tandards , 14th E dition, 1983

DISP

LACE

MEN

TPE

AKTO

PEAK

-MIL

S(0

.001

")PE

AKTO

PEAK

-MIL

S(0

.001

")

MOTOR

DIS C HAR GEHE AD

P IC KUP POINTP IC KUP POINT

( )S 90° FR OM DIS C HAR GE OF PUMP ;( )S 90° FR OM DIS C HAR GE OF PUMP ;

Page 21

MOTOR VIBRATION LIMITSMOTOR VIBRATION LIMITS

Torque (lb. ft.) =Torque (lb. ft.) = WR N2307 x t307 x t

W = weight in lbs . (weight of impeller + weight of taper lock)W = weight in lbs . (weight of impeller + weight of taper lock)R = radius of gyration in feetR = radius of gyration in feetN = change in R PMN = change in R PMt = time of acceleration in secondst = time of acceleration in secondsInertia of a cylinder about its axisInertia of a cylinder about its axis

WR =WR = 22Weight (lbs .) x [radius (ft.)]Weight (lbs .) x [radius (ft.)]

Inertia of an impeller about its axisInertia of an impeller about its axis

Weight (lbs .) x [(outer radius in ft.) - (shaft diameter) ]Weight (lbs .) x [(outer radius in ft.) - (shaft diameter) ]2

2

2

WR =WR =2

C ONVE R T ING LINE AR TO R OTATIONAL INE R T IAC ONVE R T ING LINE AR TO R OTATIONAL INE R T IA

2E quivalent WR =E quivalent WR =2 W

39.48 NV

(

(

W = Weight in pounds (lbs .)W = Weight in pounds (lbs .)

V = Linear Velocity in feet per min. (fpm) = 0.262 x Dia. (in.) x R PMV = Linear Velocity in feet per min. (fpm) = 0.262 x Dia. (in.) x R PM

N = Motor speed in R PM when load is moving at velocity VN = Motor speed in R PM when load is moving at velocity V

(

(N loadN loadN motor2E quivalent

2

E QUIVALE NT WR FOR BE LTE D OR GE AR E D LOADSE QUIVALE NT WR FOR BE LTE D OR GE AR E D LOADS2

WR =(at Motor S haft)(at Motor S haft) WR2(load)

Actual C alculatedActual C alculated2WR = 2WR of loadWR of loadN load = Full S peed of Load (R PM)N load = Full S peed of Load (R PM)

N motor = Full S peed of Motor (R PM)N motor = Full S peed of Motor (R PM)

S HAFTDIA

2

OUTE R R ADIUSOUTE R R ADIUS

Page 22Page 22

TORQUE REGUIRED TOACCELERATE A REVOLVING BODY

TORQUE REGUIRED TOACCELERATE A REVOLVING BODY

There are two types of thrust in a vertical turbine. It's very important to understand these types andThere are two types of thrust in a vertical turbine. It's very important to understand these types andtheir effects on performance and failures of pumps and drivers .their effects on performance and failures of pumps and drivers .

In a vertical turbine the water or liquid is picked up by a vaned impeller and discharged thru aIn a vertical turbine the water or liquid is picked up by a vaned impeller and discharged thru anumber of equally spaced diffus ion vanes . S ometimes , if this vane spacing is not equal or the inletnumber of equally spaced diffus ion vanes . S ometimes , if this vane spacing is not equal or the inletangles are not equal, you will have a small amount of unbalance radial thrust due to the hydraulicangles are not equal, you will have a small amount of unbalance radial thrust due to the hydraulicforces .

Axial thrust is created from the pressure difference of the impeller and is normally in the downwardAxial thrust is created from the pressure difference of the impeller and is normally in the downwardposition. However, the most important is the upward force coming form the velocity of liquid enteringposition. However, the most important is the upward force coming form the velocity of liquid enteringthe impeller eye. The liquid flow enters axially and is turned by the vanes , leaving the impeller in athe impeller eye. The liquid flow enters axially and is turned by the vanes , leaving the impeller in asemi-radial direction. The angle of exit depends on the specific speed. The upward dynamic force insemi-radial direction. The angle of exit depends on the specific speed. The upward dynamic force inthe low-specific speed impeller is s ignificant enough to overcome the effect of pressure difference,the low-specific speed impeller is s ignificant enough to overcome the effect of pressure difference,therefore caus ing a net upthrust, which will s tart at 120% of BE P. This is not unusual for enclosedtherefore caus ing a net upthrust, which will s tart at 120% of BE P. This is not unusual for enclosedimpellers .

In a normal operating pump, the upthrust is usually momentary and much smaller than the downthrust.In a normal operating pump, the upthrust is usually momentary and much smaller than the downthrust.Because the predominant force is downward, driver manufactures des ign their units (whether electricBecause the predominant force is downward, driver manufactures des ign their units (whether electricmotors or right angle gear drives) for continuos downthrust operation. Most drivers are des igned tomotors or right angle gear drives) for continuos downthrust operation. Most drivers are des igned tohandle 30% momentary upthrust loads . S ometimes , when a pump is run at a very high capacity, thehandle 30% momentary upthrust loads . S ometimes , when a pump is run at a very high capacity, theupthrust can be greater than the downthrust, especially on close coupled turbines .upthrust can be greater than the downthrust, especially on close coupled turbines .

In a typical deep well turbine, the static weight of the driveshaft serves as sufficient static head toIn a typical deep well turbine, the static weight of the driveshaft serves as sufficient static head tooffset most upthrust s ituations . C lose-coupled barrel pumps should be started against a closed valveoffset most upthrust s ituations . C lose-coupled barrel pumps should be started against a closed valveor system head which eliminates the momentary upthrust problem.or system head which eliminates the momentary upthrust problem.

When a pump must fill a long pipeline, the initial s tartup head is low and it may run in upthrust untilWhen a pump must fill a long pipeline, the initial s tartup head is low and it may run in upthrust untilthe system head develops . And in some applications the NPS HR may exceed the NPS HA allowing it tothe system head develops . And in some applications the NPS HR may exceed the NPS HA allowing it torun in upthrust. A throttling valve or temporary orifice plate is a good solution. This is especiallyrun in upthrust. A throttling valve or temporary orifice plate is a good solution. This is especiallyimportant in a submers ible pump.important in a submers ible pump.

S ome of the problems caused by continuous operation in upthrust are:S ome of the problems caused by continuous operation in upthrust are:

1. Mechanical seal failure caused when the shaft moves upward in an excess amount.1. Mechanical seal failure caused when the shaft moves upward in an excess amount.This changes the adjustment between the stationary face and the rotating face.This changes the adjustment between the stationary face and the rotating face.

2. Bent lineshaft caused by compress ion loads which cause rapid bearing wear and2. Bent lineshaft caused by compress ion loads which cause rapid bearing wear andvibration.

3. Impellers can rub or bump the top of the bowls hub caus ing wear on the bowl and3. Impellers can rub or bump the top of the bowls hub caus ing wear on the bowl andimpellers . S ometimes enough pressure is applied to loosen the taperlock and allow theimpellers . S ometimes enough pressure is applied to loosen the taperlock and allow theimpeller to spin freely on the shaft.impeller to spin freely on the shaft.

4. Damage to thrust bearings in the drivers .4. Damage to thrust bearings in the drivers .

Page 23Page 23

THRUST

(The total downthrust produced is the sum of the hydraulic thrust(The total downthrust produced is the sum of the hydraulic thrustplus the static thrust (dead weight) of the shaft and impellers .plus the static thrust (dead weight) of the shaft and impellers .

DIA. (IN's )

LBS ./FT.

AR E A

3/4

1.50

0.44 0.78

2.67

1 1 3/16

3.77

1.11 1.23

4.17

1 1/41 1/4 1 1/2

6.01

1.77 2.24

7.60

1 11/161 11/16 1 15/16

10.02

2.95

2 3/16

12.78

3.76 3.97

13.52

2 1/42 1/4 2 7/16

15.87

4.67

S HAFT WE IGHTS AND AR E ASS HAFT WE IGHTS AND AR E AS

TOTAL THR US T FOR MULATOTAL THR US T FOR MULA

TOTAL THR US T = (K x H x S G ) + (W x S ) + (Imp. Weight x No. of S tages)TOTAL THR US T = (K x H x S G ) + (W x S ) + (Imp. Weight x No. of S tages)

K = Thrust Factor for PumpK = Thrust Factor for Pump

H = Bowl Head (Total Head + C olumn Friction Loss) in FeetH = Bowl Head (Total Head + C olumn Friction Loss) in Feet

W = Weight of S haft in PoundsW = Weight of S haft in Pounds

S = S etting (Total C olumn Length) in FeetS = S etting (Total C olumn Length) in Feet

S G = S pecific G ravity of LiquidS G = S pecific G ravity of Liquid

E XAMPLE : The total thrust for a 12KC A-4 stage pump with a 1 1/2" line shaft with a totalThe total thrust for a 12KC A-4 stage pump with a 1 1/2" line shaft with a totalhead of 304 feet and a setting of 250 feet, would be calculated as follows:head of 304 feet and a setting of 250 feet, would be calculated as follows:

TOTAL THR US T = (K x H x S G ) + (W x S ) + (Imp. Weight x No. of S tages)TOTAL THR US T = (K x H x S G ) + (W x S ) + (Imp. Weight x No. of S tages)

K = 6.50K = 6.50 H = 306 W = 6.01W = 6.01 S = 250S = 250 S G = 1.00

TOTAL THR US T = (6.50 x 306 x 1) + (6.01 x 250) + (16 x 4)TOTAL THR US T = (6.50 x 306 x 1) + (6.01 x 250) + (16 x 4)

NOTE S :The driver selected must have thrust capacity greater than the total thrust value.The driver selected must have thrust capacity greater than the total thrust value.Thrust factors (K ) and impeller weights can be found on the performance curve page for the specific model.Thrust factors (K ) and impeller weights can be found on the performance curve page for the specific model.

S HAFT S IZE 3600 2900 1800 1500 1200 1000 900

0.200.260.320.520.603/4

1 1.10 0.88 0.55 0.44 0.35

0.480.610.751.301.451 3/161 3/16

1 1/4

1 1/2 0.96 0.751.20 0.60 0.55

0.700.780.941.201.401 11/161 11/16

1 15/161 15/16 1.90 1.60 1.20 1.00 0.90

1.151.301.502.002.302 3/16

2 1/4

2 7/16 2.90 2.40 1.90 1.60 1.40

R E VOLUTIONS PE R MINUTER E VOLUTIONS PE R MINUTE

FR IC T ION H.P. LOS S PE R 100 FE E TFR IC T ION H.P. LOS S PE R 100 FE E T

= 1989 + 1502.5 + 64 = 3555.5= 1989 + 1502.5 + 64 = 3555.5

0.17 0.15

0.29 0.26

0.40 0.36

0.390.441.33 0.79 0.67 0.52

1.90

2.36

2.50 2.07 1.60 1.41 1.26

Page 24Page 24

THRUST LOADS

NNPS H(NE T POS IT IVE S UC TION HE AD) Is the total suction head in feet of the liquid being pumped (absolute at the pump(NE T POS IT IVE S UC TION HE AD) Is the total suction head in feet of the liquid being pumped (absolute at the pumpcenterline or impeller eye) less the absolute vapor pressure (in feet) of the liquid being pumped. It must alwayscenterline or impeller eye) less the absolute vapor pressure (in feet) of the liquid being pumped. It must alwayshave a positive value and can be calculated by the following equations : To help explain the conditions twohave a positive value and can be calculated by the following equations : To help explain the conditions twoexpress ionswill be used: the firs t express ion is bas is for when the suction lift-liquid supply level is below the pumpwill be used: the firs t express ion is bas is for when the suction lift-liquid supply level is below the pumpcenterlineor impeller eye; the second express ion is bas is for pos itive suction, (flooded), where the liquid supply level isor impeller eye; the second express ion is bas is for pos itive suction, (flooded), where the liquid supply level isabovethe pump centerline or impeller eye.the pump centerline or impeller eye.

NOTE S :

(NE T POS IT IVE S UC TION HE AD R E QUIR E D) Is the amount of suction head, over vapor pressure, required to(NE T POS IT IVE S UC TION HE AD R E QUIR E D) Is the amount of suction head, over vapor pressure, required toprevent more than 3% loss in total head to the firs t stage of the pump at a specific capacity. NPS HRprevent more than 3% loss in total head to the firs t stage of the pump at a specific capacity. NPS HRis obtained by laboratory testing, (closed loop system). In a closed-loop test facility you can obtain deareatedis obtained by laboratory testing, (closed loop system). In a closed-loop test facility you can obtain deareatedwater, which can not be accomplished in a open pit installation. Deareation occurs in a closed-loop systemwater, which can not be accomplished in a open pit installation. Deareation occurs in a closed-loop systemwhen the static pressure is below atmospheric pressure and it increases at higher water temperature.when the static pressure is below atmospheric pressure and it increases at higher water temperature.Therefore, it is necessary to run comparable NPS HR test at the same water temperature. Also a closed-loopTherefore, it is necessary to run comparable NPS HR test at the same water temperature. Also a closed-loopsystem can be used in special requirement s ituations when pumping liquids other than water.system can be used in special requirement s ituations when pumping liquids other than water.

NPS HR

The typical pump curve depicts NPS HR or NPS H with the NPS HR ris ing as the capacity rises .The typical pump curve depicts NPS HR or NPS H with the NPS HR ris ing as the capacity rises .

NPS HA(NE T POS IT IVE S UC TION HE AD AVAILABLE ) Is the total suction head in feet (meters ) of liquid absolute, determined(NE T POS IT IVE S UC TION HE AD AVAILABLE ) Is the total suction head in feet (meters ) of liquid absolute, determinedat the firs t stage impeller datum, less the absolute vapor pressure of the liquid in feet (meters ).at the firs t stage impeller datum, less the absolute vapor pressure of the liquid in feet (meters ).

*C alculations with regard to NPS HR as follows:*C alculations with regard to NPS HR as follows:

NPS HR = hNPS HR = h a - hvpa + ( iZ - Ze )

S YMBOLS AND DE F INIT IONSS YMBOLS AND DE F INIT IONSiZ (R equired submergence ) =(R equired submergence ) = +vpah+aNPS HR - hNPS HR - h Zs

ha = absolute pressure (in feet of the liquid being pumped) on the surface of the liquid supply level (this will be= absolute pressure (in feet of the liquid being pumped) on the surface of the liquid supply level (this will bebarometric pressure if suction is from an open tank or sump; or the absolute pressure existing in a closedbarometric pressure if suction is from an open tank or sump; or the absolute pressure existing in a closedtank such as a condenser hotwell or deareator).tank such as a condenser hotwell or deareator).= Vapor pressure of pumped liquid, ft (m) absolute, at pumping temperature.= Vapor pressure of pumped liquid, ft (m) absolute, at pumping temperature.vpah

Zs = Water depth over impeller eye or the vertical distance from the suction pipe centerline to the eye= Water depth over impeller eye or the vertical distance from the suction pipe centerline to the eyeof the bottom impeller, ft (m).of the bottom impeller, ft (m).

= S uction pressure, lb/in (KPa), above atmospheric pressure. This may be positive or negative.= S uction pressure, lb/in (KPa), above atmospheric pressure. This may be positive or negative.sP 2h3 = Friction loss between pressure tap connection and suction flange.= F riction loss between pressure tap connection and suction flange.

= S ummation of friction and shock losses in suction elbow and barrel.= S ummation of friction and shock losses in suction elbow and barrel.4h

Zs+vpah-aNPS HA = hNPS HA = h

*C alculations with regard to NPS HA as follows:*C alculations with regard to NPS HA as follows:

Pa = Atmospheric pressure in lb/in (KPa) absolute.= Atmospheric pressure in lb/in (KPa) absolute.2

= Vapor pressure of water in lb/in (KPa) absolute at pumping temperature.= Vapor pressure of water in lb/in (KPa) absolute at pumping temperature.Pvpa 2S .G . = S pecific gravity of liquid at pumping temperature.= S pecific gravity of liquid at pumping temperature.

OR 2.31S .G . (Pa - Pvpa) + Z(Pa - Pvpa) + Z s

sZ = NPS HR -= NPS HR - Pa + Pvpa - ZPvpa - ZS .G .2.31 2.31

S .G . st - + h + h2V

gs 2

3 4

NPS HA =NPS HA =

For S uction Lift:For S uction Lift:NPS H = hNPS H = ha avp ts fs- h - h- h - h - h+ h- h- h sfstpv aaNPS H = hNPS H = h

For Pos itive (flooded) S uction:For Pos itive (flooded) S uction:

hst = S tatic height in feet that the liquid supply level is above or below the pump centerline or impeller eye.= S tatic height in feet that the liquid supply level is above or below the pump centerline or impeller eye.= All suction line losses (in feet) including entrance losses and friction losses through pipe, valves and fittings ,= All suction line losses (in feet) including entrance losses and friction losses through pipe, valves and fittings ,ect.

fsh

= 32.16 feet per second (acceleration of gravity).= 32.16 feet per second (acceleration of gravity).g

Ze = the vertical distance from the suction inlet to the impeller centerline.= the vertical distance from the suction inlet to the impeller centerline.= the vertical distance from the pumping water level to the discharge centerline.= the vertical distance from the pumping water level to the discharge centerline.stZ

= the velocity head in suction pipe at point of pressure tap or piezometer connection.= the velocity head in suction pipe at point of pressure tap or piezometer connection.Vs2/2 g

Page 25Page 25

NPSHR CALCULATIONSNPSHR CALCULATIONS

ALTITUDE vs . ATMOS PHE R IC PR E S S UR EALT ITUDE vs . ATMOS PHE R IC PR E S S UR E ALT ITUDE OF S OME MAJ OR C IT IE SALT ITUDE OF S OME MAJ OR C IT IE S

ALT ITUDE PS IA FT. OF WATE RFT. OF WATE R C ITY APPR OX. ALT ITUDEAPPR OX. ALT ITUDE

0500

1,0001,5002,0002,5003,0003,5004,0004,5005,0005,5006,0006,5007,0007,5008,0008,5009,0009,500

10,00010,50011,00011,50012,00012,50015,000 8.3

9.19.39.59.79.9

10.110.310.510.710.911.111.311.511.812.012.212.412.712.913.213.413.713.914.214.414.7 34.0

33.332.832.131.531.030.429.829.228.828.227.627.226.726.225.725.224.724.323.823.422.922.422.021.621.119.2 800

3501,9004,2503,5701,900800

1,100290

1,000500100900800

4,700700

2,200580

5,270700550600

6,1003,440370

1,1005,200ALBUQUE R QUE

ATLANTAAMAR ILLOC ALGAR Y

C HE YE NNEC HIC AGO

C INC INNATIC LE VE LAND

DE NVE RDE TR OIT

E DMONTONFOR T WOR THFOR T WOR THIDAHO FALLSIDAHO FALLSKANS AS C ITYKANS AS C ITYMINNE APOLIS

MONTR E ALNAS HVILLE

OMAHAOTTAWAPHOE NIX

P ITTS BUR GHR E G INA

R OS WE LLS ALT LAKE C ITYS ALT LAKE C ITY

S POKANETOR ONTO

TULS A760WINNIPE G

Page 26

ATMOSPHERIC PRESSURE

Where no instruments are available to accuratelyWhere no instruments are available to accuratelymeasure the flow of water from a pump, themeasure the flow of water from a pump, thefollowing method will serve as an approximation.following method will serve as an approximation.

Flow from Full Horizontal PipeFlow from Full Horizontal Pipe

Flow (GPM ) = A x D x 1.105Flow (GPM) = A x D x 1.105Where: A = Area of pipe in square inchesWhere: A = Area of pipe in square inches

D = Horizontal distance in inchesD = Horizontal distance in inches1.015 = Correction Factor1.015 = Correction Factor

Using an ordinary rule of carpenters square, measureUsing an ordinary rule of carpenters square, measurethe horizontal distance from the end of the dischargethe horizontal distance from the end of the dischargepipe to a point exactly 12 inches above the fallingpipe to a point exactly 12 inches above the fallingstream of water. The discharge pipe must be levelstream of water. The discharge pipe must be leveland running full of water when the reading is taken.and running full of water when the reading is taken.Multiply this distance (in inches) by the cross sectionalMultiply this distance (in inches) by the cross sectionalarea of the pipe in square inches and the answerarea of the pipe in square inches and the answerwill be the approximate capacity in gallons per minute.will be the approximate capacity in gallons per minute.

By checking this method of estimation using accurateBy checking this method of estimation using accurateflow meters it has been found a correction factor offlow meters it has been found a correction factor of1.015 should be applied.1.015 should be applied.

Flow from Inclined PipeFlow from Inclined Pipe

Flow From Horizontal Pipe (Partially Filled)Flow From Horizontal Pipe (Partially Filled)

F = E ffective area factor shown belowF = Ef fective area factor shown belowD = Horizontal distance in inchesD = Horizontal distance in inches

Where: A = Area of pipe in square inchesWhere: A = Area of pipe in square inchesFlow (GPM ) = A x D x 1.039 x FFlow (GPM) = A x D x 1.039 x F

Area of pipe equals inside Dia. x 0.7854Area of pipe equals inside Dia. x 0.7854 2

EXAMPLE: D = 20 Inches - Pipe inside diameter = 10 inches -D = 20 Inches - Pipe inside diameter = 10 inches -F = 2 1/2 inchesF = 2 1/2 inchesA = 10 x 10 x 0.7854 = 78.54 square inchesA = 10 x 10 x 0.7854 = 78.54 square inchesR = 2 1 /2 - 10 = 25%R = 2 1/2 - 10 = 25%F = 0.805

Flow = 78.54 x 20 x 1.039 x 0.805 = 1314 GPMFlow = 78.54 x 20 x 1.039 x 0.805 = 1314 GPM

PAR TIALL Y FILLED PIPESPAR TIALL Y FILLED PIPES

Horizontal Distance = DHorizontal Distance = D

12"

D

12"

12"

Horizontal Distance = DHorizontal Distance = DF

RA TIOF/D = RF/D = R

% FFACT OR

EFF . AREAEFF . AREA

5101520253035404550

0.981

0.5000.5640.6270.6880.7470.8050.8580.9050.948 0.373

0.3120.2530.1950.1420.0950.0520.0190.000

0.436

100959085807570656055

EFF . AREAFACT OR

F%F/D = RF/D = RRA TIO

Where: A = 78.54 (10" pipe)Where: A = 78.54 (10" pipe)D = 20"

EXAMPLE: A x D x 1.105A x D x 1.10578.54 x 20 x 1.10578.54 x 20 x 1.105GPM = 1736

Page 27

ESTIMATING FLOW FROMHORIZONTAL OR INCLINED PIPES

ESTIMATING FLOW FROMHORIZONTAL OR INCLINED PIPES

R =DIA. OF OR IF IC E IN INC HE SDIA. OF OR IF IC E IN INC HE SDIA. OF DIS C HAR GE P IPEDIA. OF DIS C HAR GE P IPE

G .P.M. = KA 2gh = KA x 8.025 hKA 2gh = KA x 8.025 h

IN S QUAR E INC HE SIN S QUAR E INC HE SAR E A OF OR IF IC EAR E A OF OR IF IC E

A =A =

h =HE IGHT OF WATE R IN GLAS SHE IGHT OF WATE R IN GLAS SABOVE C E NTE R OF P IPEABOVE C E NTE R OF P IPEIN INC HE S

h

NOT LE S S THANNOT LE S S THAN3 FT. FR OM ANY3 FT. FR OM ANY

OBS TR UC TION

NOT LE S SNOT LE S STHAN 20 IN.THAN 20 IN.

The orifice method is a s imple way to measure theThe orifice method is a s imple way to measure theflow of water from a pipe discharging horizontally in-flow of water from a pipe discharging horizontally in-to open air without bends or obstruction in the lastto open air without bends or obstruction in the lastthree feet. The sketch shows the arrangement.three feet. The sketch shows the arrangement.

A plate is clamped over the end of the pipe with theA plate is clamped over the end of the pipe with thecircular orifice located at the exact center of the pipe.circular orifice located at the exact center of the pipe.The s ize of the orifice should preferably be from one-The s ize of the orifice should preferably be from one-half to three-quarter the s ize of the pipe, but must behalf to three-quarter the s ize of the pipe, but must beselected of such s ize that it will be running full ofselected of such s ize that it will be running full ofwater.

At a point on the s ide of the discharge pipe not lessAt a point on the s ide of the discharge pipe not lessthan 20 inches back from the orifice a hole should bethan 20 inches back from the orifice a hole should bedrilled and tapped for an 1/8" or 1/4" pipe. A shortdrilled and tapped for an 1/8" or 1/4" pipe. A short

piece of pipe is screwed into this hole until the innerpiece of pipe is screwed into this hole until the innerend is just flush with the inner wall of the dischargeend is just flush with the inner wall of the dischargepipe. A piece of rubber hose is s lipped over this pipepipe. A piece of rubber hose is s lipped over this pipeand also over one end of a piece of glass tubing sup-and also over one end of a piece of glass tubing sup-ported in a vertical pos ition.ported in a vertical pos ition.

The diameter of the orifice divided by the ins ide pipeThe diameter of the orifice divided by the ins ide pipediameter gives the ratio "R " and from the curve thediameter gives the ratio "R " and from the curve theproper value of "K " is found. In the formula "A" isproper value of "K " is found. In the formula "A" isfigured as the area of the orifice in square inches ,figured as the area of the orifice in square inches ,"G " equals 32.2, and "H" is read as the height of the"G " equals 32.2, and "H" is read as the height of thewater column in the glass tube above the center ofwater column in the glass tube above the center ofthe pipe in inches . Gallons per minute "G .P.M." canthe pipe in inches . Gallons per minute "G .P.M." canthen be figured. This method is s impler than a weirthen be figured. This method is s impler than a weirand fully as accurate.and fully as accurate.

1.0

0.9

0.8

0.7

0.6

0.5

CONS

TANT

KUS

EDIN

FORM

ULA

CONS

TANT

KUS

EDIN

FORM

ULA

0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 1.0R atio of Dia. of Orifice to Dia. of Discharge P ipe = RR atio of Dia. of Orifice to Dia. of Discharge P ipe = R

Page 28

ORIFICE METHOD OFMEASURING WATERORIFICE METHOD OFMEASURING WATER

H.INC HE S H

3"P IPE1 3/4"1 3/4"

OR IF IC E OR IF IC E2 1/2"2 1/2"P IPE

4" 6"P IPE

3"ORIFIC E ORIFIC E

4 3/4"P IPE

6" 8"P IPE

6"OR IF IC E OR IF IC E

8"P IPE10"

GALLONS PE R MINUTEGALLONS PE R MINUTE

INC HE SH.

GALLONS PE R MINUTEGALLONS PE R MINUTE10"

P IPE8"

OR IF IC EOR IF IC E6"

P IPE8"6"

P IPE4 3/4"4 3/4"

OR IF IC EOR IF IC E3"

P IPE6"4"

P IPE2 1/2"2 1/2"

OR IF IC EOR IF IC E1 3/4"1 3/4"P IPE

3"

1 1.000234

65

789

101112131415

181716

222324

212019

252627

302928

313233343536373839404142434445464748495051525354555657585960

11.3 24.0 31.7 101.6 154.5 296.51.414 16.1 33.9 44.9 143.8 218.5 419.01.732 19.6 41.6 55.2 176.0 267.6 513.0

593.0309.0203.363.548.022.72.0002.236 25.3 53.6 71.1 227.4 345.5 692.02.449 27.8 58.8 77.8 249.0 378.5 727.02.646 30.0 63.5 84.0 268.7 409.0 785.02.828 32.0 67.9 89.9 287.2 437.0 838.03.000 34.0 72.0 95.4 305.0 463.0 889.03.162 35.9 76.0 100.6 321.2 488.0 938.03.317 37.6 79.6 105.4 337.0 512.0 982.03.464 39.3 83.2 110.2 352.0 530.0 1027.03.606 40.8 86.6 114.6 367.0 557.0 1069.03.742 42.3 89.8 119.0 381.0 577.5 1108.03.873 43.9 93.0 123.1 394.0 598.0 1148.04.000 45.3 96.0 127.2 407.0 618.0 1186.04.123 46.7 98.9 131.0 419.0 637.0 1222.04.243 48.1 101.8 135.0 432.0 655.0 1258.04.359 49.3 104.7 138.5 442.0 673.0 1291.04.472 50.7 107.4 142.3 454.0 692.0 1327.04.583 52.0 110.0 145.8 466.0 708.0 1359.04.690 53.2 112.6 149.3 477.0 725.0 1391.04.796 54.3 115.0 152.5 487.0 740.0 1421.04.899 55.5 117.6 155.7 497.0 757.0 1452.05.000 56.7 120.0 159.0 508.0 772.0 1482.05.099 57.7 122.3 162.0 518.0 788.0 1512.05.196 58.8 124.8 165.2 528.0 802.0 1539.05.292 60.0 127.0 168.4 538.0 817.0 1568.05.385 61.1 129.2 171.3 547.0 833.0 1598.05.477 62.1 131.5 174.2 557.0 846.0 1623.05.568 63.0 133.8 177.0 566.0 860.0 1651.05.657 64.0 135.9 180.0 575.0 874.0 1675.05.745 65.1 137.9 182.7 584.0 887.0 1702.05.831 66.1 140.0 185.5 593.0 900.0 1729.05.916 67.0 141.8 188.0 602.0 913.0 1751.06.000 68.0 144.0 190.8 610.0 927.0 1779.06.083 68.9 146.0 193.5 617.0 940.0 1802.06.164 69.8 148.0 196.0 626.0 952.0 1828.06.245 70.7 149.9 198.5 634.0 964.0 1850.06.325 71.7 151.9 201.0 643.0 977.0 1875.06.403 72.5 153.8 203.5 651.0 989.0 1899.06.481 73.4 155.7 206.0 659.0 1001.0 1921.06.557 74.2 157.5 208.5 666.0 1013.0 1942.06.633 75.0 159.2 211.0 674.0 1025.0 1965.06.708 75.9 161.0 213.5 681.0 1037.0 1987.06.782 76.8 162.8 215.7 689.0 1049.0 2010.06.856 77.7 164.9 218.0 696.0 1060.0 2032.06.928 78.5 166.4 220.0 704.0 1071.0 2050.07.000 79.2 168.0 222.5 712.0 1082.0 2073.07.071 80.0 169.9 224.7 718.0 1093.0 2095.07.141 80.8 171.5 227.0 725.0 1104.0 2118.07.211 81.6 173.1 229.0 732.0 1114.0 2135.07.280 82.5 174.9 231.5 740.0 1125.0 2157.07.349 83.2 176.3 233.5 747.0 1135.0 2178.07.416 83.8 178.0 235.5 753.0 1145.0 2195.07.483 84.8 179.5 238.0 761.0 1156.0 2219.07.550 85.5 181.4 240.0 767.0 1167.0 2239.07.616 86.2 182.8 242.0 773.0 1177.0 2253.07.681 86.8 184.2 244.2 781.0 1187.0 2278.07.746 87.7 186.0 246.2 787.0 1197.0 2297.0

6162

7.8107.874 89.2

88.3 187.5189.0 250.1

248.1 793.0799.0 1217.0

1207.0 2314.02332.02352.01227.0806.0252.1190.589.87.937632371.01237.0813.0254.1192.090.68.000642389.01247.0819.0256.1193.591.38.062652408.01256.0826.0258.1195.292.28.124662426.01265.0832.0260.1196.492.78.185672442.01274.0837.0262.0198.093.48.246682461.01284.0844.0264.0199.594.18.307692479.01293.0850.0265.9201.094.88.367702496.01303.0856.0267.9202.395.58.426712518.01312.0862.0269.9203.996.18.485722538.01321.0868.0271.9205.096.88.544732550.01330.0874.0273.8206.697.58.602742565.01339.0880.0275.6208.098.28.660752583.01348.0886.0277.2209.398.88.718762605.01356.0892.0279.0210.699.48.775772619.01365.0898.0280.8211.9100.18.832782632.01374.0903.0282.7213.2100.78.888792653.01383.0908.0284.0214.6101.38.944802664.01392.0914.0286.0216.0102.09.000812682.01400.0920.0287.8217.3102.69.055822700.01408.0926.0289.4218.6103.29.110832713.01416.0932.0291.0219.9103.89.165842731.01424.0937.0292.6221.2104.49.220852748.01433.0942.0294.6222.6105.29.274862764.01441.0947.0296.6223.9105.79.327872780.01449.0953.0298.2225.2106.39.381882798.01457.0958.0300.0226.4106.99.434892812.01465.0964.0301.6227.6107.59.487902827.01473.0970.0303.2228.9108.09.539912845.01481.0975.0304.8230.2108.79.592922859.01489.0980.0306.4231.5109.39.644932875.01497.0985.0308.0232.7109.89.695942890.01505.0990.0309.6233.9110.49.747952905.01513.0995.0311.2235.2111.09.798962920.01521.01000.0312.8236.5111.69.849972936.01529.01006.0314.7237.6112.29.900982950.01537.01011.0316.2238.8112.79.950992965.01545.01017.0317.7240.0113.310.0001002980.01553.01022.0319.3241.2113.910.0501012995.01560.01027.0321.0242.4114.410.1001023010.01568.01032.0322.6243.8115.010.1491033025.01573.01037.0324.0244.8115.510.1981043039.01583.01042.0325.9246.0116.210.2471053052.01591.01047.0327.0247.2116.610.2961063068.01598.01052.0328.8248.4117.210.3441073079.01606.01057.0330.0249.4117.710.3921083095.01613.01062.0332.0250.6118.310.4401093110.01620.01067.0333.6251.7118.810.4881103128.01628.01071.0335.0252.8119.410.5361113140.01635.01076.0336.5254.0119.910.5831123152.01642.01081.0338.0255.2120.410.6301133163.01650.01086.0339.5256.2121.010.6771143179.01657.01090.0341.0257.5121.310.7241153193.01664.01095.0342.5258.5122.010.7701163210.01671.01100.0344.0259.6122.510.8171173219.01678.01105.0345.5260.7123.110.8631183235.01685.41109.0347.0261.8123.610.9091193243.01693.01114.0348.3262.9124.110.955120

To arrive at capacities in Gallons per Minute when the reading of H is more than 120" use the following formulas :To arrive at capacities in Gallons per Minute when the reading of H is more than 120" use the following formulas :

G .P.M. 3" pipe 1 3/4" orifice = 11.329 x the square root of H.G .P.M. 3" pipe 1 3/4" orifice = 11.329 x the square root of H.G .P.M. 4" pipe 2 1/2" orifice = 24.00 x the square root of H.G .P.M. 4" pipe 2 1/2" orifice = 24.00 x the square root of H.G .P.M. 6" pipe 3" orifice = 31.77 x the square root of H.G .P.M. 6" pipe 3" orifice = 31.77 x the square root of H. G .P.M. 10" pipe 8" orifice = 296.50 x the square root of H.G .P.M. 10" pipe 8" orifice = 296.50 x the square root of H.

G .P.M. 8" pipe 6" orifice = 154.50 x the square root of H.G .P.M. 8" pipe 6" orifice = 154.50 x the square root of H.G .P.M. 6" pipe 4 3/4" orifice = 101.69 x the square root of H.G .P.M. 6" pipe 4 3/4" orifice = 101.69 x the square root of H.

H

Page 29Page 29

ORIFICE METHOD OFMEASURING WATERORIFICE METHOD OFMEASURING WATER

C=

(MILLIO

N)

C=

(MILLIO

N)

0 1 2 3 4 5 6 7 8 9 10 1101.0

2.03.0

4.05.0

6.07.0

8.0

3/4" - 16P

1" - 12P1" - 12P

1 3/16" - 12P

1 3/16" - 12P

1 7/16" - 12P

1 7/16" - 12P1 1/2" - 12P

1 1/2" - 12P

1 11/16" - 12P

1 11/16" - 12P

1 15/16" - 12P

1 15/16" - 12P

2 3/16" -12P

2 3/16" -12P

27/16" - 12P

27/16" - 12P

211/16" - 8P

211/16" - 8P

215/16" - 8P

215/16" - 8P

NUMB E R OF TUR NS OF ADJ US T ING NUTNUMB E R OF TUR NS OF ADJ US T ING NUT

NO

TE:P

=pitch

=threads

per inchN

OTE :

P=

pitch=

threadsper inch

For 16Peach

turn=

1/16" =.062"

For 16Peach

turn=

1/16" =.062"

For 12Peach

turn=

1/12" =.083"

For 12Peach

turn=

1/12" =.083"

For 8Peach

turn=

1/8" =.125"

For 8Peach

turn=

1/8" =.125"

P age 30Page 30

SHAFT ADJUSTMENT

The turbine pump lineshaft stretches when the pump is inThe turbine pump lineshaft stretches when the pump is inoperation due to a downward pull or hydraulic thrust. Theoperation due to a downward pull or hydraulic thrust. Thestretch due to this thrust may be determined and thestretch due to this thrust may be determined and theimpellers raised by that amount so that they will operate inimpellers raised by that amount so that they will operate inthe des ired location with respect to the bowls when the pumpthe des ired location with respect to the bowls when the pumpis running.C areful adjustment must be made, particularly with semi-openC areful adjustment must be made, particularly with semi-openimpellers where optimum performance is obtained with only aimpellers where optimum performance is obtained with only afew thousands of an inch clearance between the bottom offew thousands of an inch clearance between the bottom ofthe impeller and the bowl face. For s ide seal or combinationthe impeller and the bowl face. For s ide seal or combinationseal impellers , the location is not critical, and they are usuallyseal impellers , the location is not critical, and they are usuallyset so there is adequate clearance to prevent rubbing.set so there is adequate clearance to prevent rubbing.The E nd P lay (Lateral) - Thrust C onstant table shows theThe E nd P lay (Lateral) - Thrust C onstant table shows thethrust constant (K ) for each bowl s ize representing thethrust constant (K ) for each bowl s ize representing thepounds thrust for each foot of pumping head.pounds thrust for each foot of pumping head.Following is a curve sheet indicating the turns of theFollowing is a curve sheet indicating the turns of theadjusting nut to equal the shaft stretch as a function of "C "adjusting nut to equal the shaft stretch as a function of "C "for various shaft s izes .for various shaft s izes ."C " is the product of bowl thrust constant (K ), the total"C " is the product of bowl thrust constant (K ), the totalpumping head and the shaft length or setting.pumping head and the shaft length or setting.

The following is an example of how the shaft stretch isThe following is an example of how the shaft stretch isdetermined: Bowls 12MC

1 3/16"1 3/16"S haft S izeS haft S ize400'S etting180'Total HeadTotal Head

setting = 10.6 x 180 ft. x 400 ft. = 763,200.setting = 10.6 x 180 ft. x 400 ft. = 763,200."C " = Bowl thrust constant (K ) x total pumping head x"C " = Bowl thrust constant (K ) x total pumping head x

F rom chart for "C " on back = 763,200 and 1 3/16" shaft,F rom chart for "C " on back = 763,200 and 1 3/16" shaft,number of turns = 3.25.number of turns = 3.25.

The shaft should be raised 0.85 turns after the impellers justThe shaft should be raised 0.85 turns after the impellers justclear the bowl face to allow for the shaft stretch due toclear the bowl face to allow for the shaft stretch due tohydraulic thrust.hydraulic thrust.

THR US T BE AR ING LOADTHR US T BE AR ING LOAD

The thrust-bearing load that the driver thrust bearing mustThe thrust-bearing load that the driver thrust bearing mustcarry can be determined by adding the weight of thecarry can be determined by adding the weight of thelineshafting to the product of the thrust constant (K ) and thelineshafting to the product of the thrust constant (K ) and thetotal pumping head plus the weight of impellers .total pumping head plus the weight of impellers .The table below show the weight of the lineshafting forThe table below show the weight of the lineshafting forcommon sizes .common sizes .

S haft S izeS haft S ize 1 3/16"S etting 400'Total HeadTotal Head 180'

12MC B3BowlsE xample:

Motor 75 HpMotor 75 Hp 1750 R PM1750 R PM

Hydraulic Thrust = thrust constant (K ) times total head (ft.).Hydraulic Thrust = thrust constant (K ) times total head (ft.).Thrust constant from the table for 12MC = 10.6 Lbs . perThrust constant from the table for 12MC = 10.6 Lbs . perfoot.Hydraulic Thrust = 10.6 Lbs ./ft. x 180 ft. = 1,908 Lbs .Hydraulic Thrust = 10.6 Lbs ./ft. x 180 ft. = 1,908 Lbs .S haft weight per foot for 1 1 3/16" shafting from DataS haft weight per foot for 1 1 3/16" shafting from DataS heet E 210A = 3.8 Lbs . per foot.S heet E 210A = 3.8 Lbs . per foot.Total shaft weight = 3.8 Lbs ./ft. x 400' = 1520 Lbs .Total shaft weight = 3.8 Lbs ./ft. x 400' = 1520 Lbs .Total Impeller weight = 3 x 15 = 45 Lbs .Total Impeller weight = 3 x 15 = 45 Lbs .Total load on thrust bearing equals hydraulic thrust plus shaftTotal load on thrust bearing equals hydraulic thrust plus shaftweight plus impeller wt. 1908 Lbs . + 1520 Lbs . + 45 Lbs . =weight plus impeller wt. 1908 Lbs . + 1520 Lbs . + 45 Lbs . =3,473 Lbs .3,473 Lbs .F rom the motor manufacture's specification, allowable thrustF rom the motor manufacture's specification, allowable thrustload for 75 Hp, 1,750 R PM motor is 4,800 Lbs .load for 75 Hp, 1,750 R PM motor is 4,800 Lbs .

Therefore the thrust is well within the permiss ible load for theTherefore the thrust is well within the permiss ible load for thestandard heavy thrust motor. If the thrust load exceeded thestandard heavy thrust motor. If the thrust load exceeded themotor rating, and extra heavy thrust bearing would be required.motor rating, and extra heavy thrust bearing would be required.

S ee R everse for S haft Adjustment C hart.S ee R everse for S haft Adjustment C hart.

S haftDiameter

Weight Per FootWeight Per Foot(Lbs .)

3/4" 1.501" 2.70

1 3/16"1 3/16" 3.801 7/16" 61 1/2"1 1/2" 6

1 11/16"1 11/16" 7.601 15/16"1 15/16" 10.002 3/16"2 3/16" 132 7/16"2 7/16" 15.902 11/16"2 11/16" 19.302 15/16" 23

31

SHAFT STRETCHTHRUST LOAD

SHAFT STRETCHTHRUST LOAD

1,000 2,000 3,000 5,000 7,500 10,000 15,000 20,000S HAFTDIAME TE R

(in.)POWE R R ATING (H.P.)POWE R R ATING (H.P.)

345029002200176014601160

345029002200176014601160

345029002200176014601160880

176014601160

176014601160880700

176014601160880700

176014601160880700

30,000S PE E D(rpm)

1

1 3/161 3/16

1 15/161 15/16

2 3/162 3/16

2 7/162 7/16

1 1/21 1/2

880

1 11/16

*Determine pump thrust from the thrust constant and shaft stretch thrust load pages of this section.*Determine pump thrust from the thrust constant and shaft stretch thrust load pages of this section.

PUMP THR US T (LBS )PUMP THR US T (LBS )

176014601160880700

2 15/162 15/16

1045 S S114 140 114 140 113 111139 139 107 13495 117 94 117 94 92116 115 88 11272 89 72 89 71 7088 87 67 8557 70 57 70 57 5670 69 53 6747 58 47 58 47 4658 57 44 5538 46 37 46 37 3646 55 35 44

203 248 202 248 202 200247 245 196 243 191 238168 208 168 208 167 166207 205 162 204 158 200127 158 127 158 127 125157 156 123 154 120 151102 124 101 124 101 100124 123 98 122 96 12084 102 84 102 84 83102 102 82 101 80 9967 82 67 82 67 6682 81 65 80 63 79

433 432530 528 429 526 425 523 413 514359 357445 443 355 442 352 439 342 432272 271337 336 269 335 267 333 260 327217 217266 265 215 264 213 263 208 258180 180220 219 179 218 177 218 172 214143 143175 175 143 174 140 173 137 170106 106130 129 105 129 104 128 101 126

318 317388 388 316 387 314 386 309 381 302263 263321 321 262 321 260 320 256 316 250209 209256 256 208 255 207 254 204 251 199155 155190 189 154 189 153 188 151 186 147

493 603 492 602 490 601 486 597 578480 592409 500 408 499 407 498 403 495 479398 491 384325 397 324 397 323 396 320 394 381316 390 305241 294 240 294 239 293 237 292 282234 289 226

233 233 233 232 224229724 885 723 884 721 883 718 880 863712 876 697600 734 599 733 598 732 595 729 715591 726 578477 583 476 582 475 582 473 580 569469 577 459353 432 353 432 352 431 350 430 422348 428 340280 343 280 343 279 342 278 342 335276 340 270

951 1163 949 1162 946 1159 1144941 1155 927788 964 787 963 785 961 948782 958 769626 766 626 765 623 764 754620 761 611464 568 464 567 462 566 558460 560 453369 568 369 450 367 450 443365 445 360

2106 2103 209121001746 1744 173417411387 1385 137713831053 1051 10451050837 836 831835

1045 S S 1045 S S 1045 S S 1045 S S 1045 S S 1045 S S 1045 S S 1045 S S

880 N/A 34 N/A 34 N/A N/A34 33 N/A 32

770 48880 61

47 47 4760 60 60

46 4659 58

700 103 102 101 101 1002200

700

485 485 483 482 476

151 150 150 149 147

Page 32Page 32

SHAFT SELECTION CHART

HYDR AULICTHR US T

500

3/4

0.047 0.026

1

0.018

1 3/161 3/16

0.012

1 1/21 1/2

0.009

1 11/161 11/16

0.007

1 15/16 2 3/16 2 7/16 2 11/162 11/16 2 15/16 3 3/16 3 7/163 7/16 3 11/16 3 15/163 15/16

S HAFT DIAME TE RS HAFT DIAME TE R

600800

100012001400160018002000240028003200360040004400480052005600600065007000750080009000

10,00012,00014,00016,00018,00020,00022,00024,00026,00028,00030,00032,00034,00036,00038,00040,000

0.2620.2250.1870.1690.1500.1310.1310.1120.0940.0750.056 0.032

0.0420.0530.0630.0740.0840.0950.1050.1270.148

0.2740.2530.2400.2110.1900.169 0.119

0.1350.1500.1640.1790.194

0.1050.0900.0750.0670.0600.0520.0450.0370.0300.022 0.014

0.0190.0240.0280.0330.0380.0420.0470.0560.066

0.1220.1130.1030.0940.0850.075

0.0110.0150.0190.0220.0260.0300.0330.0370.0440.052

0.0960.0890.0810.0740.0670.059

0.0080.0110.0140.0170.0200.0220.0250.0280.0340.039

0.0730.0670.0620.0560.0510.045

0.0060.0090.0110.0130.0150.0180.0200.0220.0260.030

0.0570.0530.0480.0440.0400.035

0.2600.260

0.281

0.296

0.280

0.286

0.2430.2240.2090.209 0.131

0.1410.1530.164

0.1070.1110.1200.129

0.0790.0840.0910.098

0.0620.0660.0710.077

0.2340.2110.1880.176 0.139

0.1480.1670.1850.222 0.168

0.1400.1260.1120.105

0.1320.1100.0980.0880.082

0.259 0.1960.2240.252

0.1760.1980.2200.2420.264

0.154

0.283

0.2130.1950.176

0.230

0.2660.248

0.009

0.010

0.0120.0120.012

0.014

0.016

0.016

0.124

0.1600.142

0.0670.0710.0800.0890.106

0.0620.0580.0530.050

0.0280.0320.0360.0390.0430.046

0.0250.0210.0180.0160.0140.0120.011

0.0120.0130.0150.0180.020

0.0380.0350.0320.0290.0260.023

0.0410.0440.0470.051

0.0880.0730.0660.0580.055

0.1170.131

0.102

0.2040.219

0.190

0.1460.1600.175

0.233

0.2920.2770.2620.248 0.208

0.2200.2320.2450.245

0.196

0.1470.1340.122

0.159

0.1830.171

0.086

0.1100.098

0.0460.0490.0550.0610.0730.073

0.0430.0400.0370.034

0.0200.0220.0250.0270.0290.032

0.0170.015

0.0150.015

0.0270.0250.0240.0210.0190.017

0.0290.0310.0340.036

0.0620.0520.0470.0420.039

0.0830.093

0.073

0.1450.156

0.135

0.1040.1140.124

0.166

0.2070.1970.1870.176 0.152

0.1600.1700.178

0.143

0.1070.0980.0980.089

0.116

0.1340.125

0.0620.062

0.0800.071

0.0330.0360.0400.0450.054

0.0310.0290.0270.025

0.0160.0180.0200.0210.023 0.020

0.0190.017

0.0220.0230.0250.027

0.0470.0390.0350.0310.029

0.0620.070

0.055

0.1090.117

0.102

0.0780.0860.094

0.125

0.1560.1480.1400.133 0.116

0.1220.1290.136

0.1090.109

0.0820.0740.068

0.088

0.1040.095

0.048

0.0610.054

0.0260.0270.0310.0340.041

0.0240.0220.0200.0190.018

0.011

Inches per 100 F t. of S haftInches per 100 F t. of S haftUS E OF THIS TABLE IS LIMITE D TO 500 FT. S E TT ING . FOR DE E PE R S E TT ING , C ONS ULT THE FAC TOR YUS E OF THIS TABLE IS LIMITE D TO 500 FT. S E TT ING . FOR DE E PE R S E TT ING , C ONS ULT THE FAC TOR Y

Downthrust due to the hydraulic thrust of the pump causes the shaft and column to stretch after the pump is in operation. Unless the impellers can be andDownthrust due to the hydraulic thrust of the pump causes the shaft and column to stretch after the pump is in operation. Unless the impellers can be andare raised off the impeller fit in the bowls enough to allow for this stretch plus some running clearance, the impellers will rub, caus ing the pump to wear andare raised off the impeller fit in the bowls enough to allow for this stretch plus some running clearance, the impellers will rub, caus ing the pump to wear andincrease the horsepower required. With the total hydraulic downthrust known and the C olumn E longation determined from this C hart the total stretch of theincrease the horsepower required. With the total hydraulic downthrust known and the C olumn E longation determined from this C hart the total stretch of thecolumn tube for the setting in question can be determined. To find the net elongation subtract the shaft elongation from column elongation.column tube for the setting in question can be determined. To find the net elongation subtract the shaft elongation from column elongation.

e = L x 12 x H.T.L x 12 x H.T.E x G .S .A.E x G .S .A.

Where:e = E longation (in inches)e = E longation (in inches)L = S haft Length (feet)E = Modulus of E lasticity (29,000,000)E = Modulus of E lasticity (29,000,000)H.T. = Hydraulic Thrust (pounds)G .S .A. = Gross S haft Area (sq. inches)G .S .A. = Gross S haft Area (sq. inches)

Page 33

SHAFT ELONGATION

HYDRAULICTHRUST

500

3"

0.007 0.005

4"

0.004

5"

0.003

6" 8" 10" 12" 14" 16"

600800

100012001400160018002000240028003200360040004400480052005600600065007000750080009000

10,00012,00014,00016,00018,00020,00022,00024,00026,00028,00030,00032,00034,00036,00038,00040,000

0.0370.0320.0270.0240.0210.0190.0160.0130.0110.0110.008 0.006

0.0080.0100.0120.0140.0160.0180.0200.0230.027

0.0510.0470.0430.0390.0350.031

0.0280.0310.0340.0370.0400.043

0.0250.0220.0190.0150.0140.0120.0110.009

0.0060.005 0.004

0.0050.0060.0070.0080.0090.0110.0120.0140.016

0.0300.0280.0260.0230.0210.019

0.0040.0050.0060.0070.0080.0090.0100.012

0.0230.0210.0190.0170.0160.014

0.0050.0060.0070.0080.010

0.0180.0160.0150.0140.0120.011

0.0060.007

0.0140.0130.0110.0100.0090.008

0.058

0.070

0.070

0.068

0.068

0.0540.0500.046

0.0330.0350.0380.041

0.0240.0260.0280.030

0.0190.0200.0220.024

0.0150.0160.0170.018

0.0590.0530.0470.044 0.033

0.0350.0390.0430.052 0.041

0.0340.0300.0270.025

0.0310.0260.0230.0210.020

0.061 0.0480.0540.061

0.0420.0470.0520.0570.063

0.036

0.067

0.0500.0460.042

0.055

0.0630.059

0.029

0.0380.034

0.0160.0170.0190.0210.025

0.0150.0140.0130.012

0.0080.0080.0090.0100.011 0.010

0.009

0.0110.0110.0120.013

0.0230.0190.0170.0150.014

0.0300.034

0.026

0.0520.056

0.049

0.0370.0410.045

0.060

0.0750.0710.0680.064

Inches per 100 Ft. of Column (For open Line Shaft Column multiply values by 1.3)Inches per 100 Ft. of Column (For open Line Shaft Column multiply values by 1.3)USE OF THIS TABLE IS LIMITED TO 500 FT . SETTING. FOR DEEPER SETTING, CONSUL T THE FOACT OR YUSE OF THIS TABLE IS LIMITED TO 500 FT . SETTING. FOR DEEPER SETTING, CONSUL T THE FOACT OR Y

Downthrust due to the hydraulic thrust of the pump causes the shaft and column to stretch after the pump is in operation. UnlessDownthrust due to the hydraulic thrust of the pump causes the shaft and column to stretch after the pump is in operation. Unlessthe impellers can be and are raised off the impeller fit in the bowls enough to allow for this stretch plus some running clearance, thethe impellers can be and are raised off the impeller fit in the bowls enough to allow for this stretch plus some running clearance, theimpellers will rub, causing the pump to wear and increase the horsepower required. With the total hydraulic downthrust known and theimpellers will rub, causing the pump to wear and increase the horsepower required. With the total hydraulic downthrust known and theColumn Elongation determined from this Chart the total stretch of the column tube for the setting in question can be determined. ToColumn Elongation determined from this Chart the total stretch of the column tube for the setting in question can be determined. Tofind the net elongation subtract the shaft elongation from column elongation.find the net elongation subtract the shaft elongation from column elongation.

e =e = L x 1 2 x H .T.L x 12 x H.T .E x G.S.A.E x G.S.A.

e = Elongation (in inches)e = Elongation (in inches)L = Shaft Length (feet)L = Shaft Length (feet)E = Modulus of Elasticity (29,000,000)E = Modulus of Elasticity (29,000,000)H.T . = Hydraulic Thrust (pounds)H.T . = Hydraulic Thrust (pounds)G.S.A. = Gross Shaft Area (sq. inches)G.S.A. = Gross Shaft Area (sq. inches)

COLUMN DIAMETERCOLUMN DIAMETERStandard pipe, nominal I.D. except as indicated by*Standard pipe, nominal I.D. except as indicated by*

0.0430.048

0.0710.0760.0800.0840.104

0.0990.0940.089

0.0730.0780.0830.109

0.1020.095

0.1150.1220.1290.136

0.0820.075

0.088

0.055

0.094

0.113

0.0960.104

0.0780.087

0.082

0.062

0.008

Page 34Page 34

COLUMN AND TUBEELONGATION

COLUMN AND TUBEELONGATION

The published efficiencies of drivers do not include anyThe published efficiencies of drivers do not include anyexternal thrust on rotor. The thrust load as a unit operatingexternal thrust on rotor. The thrust load as a unit operatingloss must be added to the brake horsepower along withloss must be added to the brake horsepower along withmechanical friction in BHP to arrive at the actual pump brakemechanical friction in BHP to arrive at the actual pump brakehorsepower requirements of a pump (field BHP ).horsepower requirements of a pump (field BHP ).

FOR MULA:

C onvert total thrust to loss in H.P. by the following formula:C onvert total thrust to loss in H.P. by the following formula:

Thrust Bearing H.P. = 0.0075 x xThrust Bearing H.P. = 0.0075 x x R PM100

THR US T1000

E xample:

10004457.3

1001770Thrust Bearing H.P. = 0.0075 x xThrust Bearing H.P. = 0.0075 x x

= 0.6 Thrust Bearing H.P. Loss .= 0.6 Thrust Bearing H.P. Loss .

THR US T BE AR ING LOS S E STHR US T BE AR ING LOS S E S

0.660.8810,000

9000

8000 0.700 0.528

0.4600.6157000

6000 0.525 0.396

0.438 0.3305000

4000

3000 0.790 0.400 0.263 0.198

0.1320.1750.2680.5252000

1000 0.262 0.133 0.088 0.066

3500 1770 1170 880

TOTALTHR US T

INPOUNDS

THR US T BE AR ING LOS STHR US T BE AR ING LOS S

R PM

15,000

20,000

25,000

30,000

35,000

40,000

45,000

50,000

1.05

1.32

1.58

1.84

2.10

2.36

2.62

3.95

5.25

0.532

0.665

0.796

0.930

1.06

1.20

1.33

1.98

2.68

3.32

4.00

4.65

5.32

5.98

0.350

0.79

1.40

1.75

2.20

2.63

3.07

3.50

3.95

4.38

1.32

1.65

1.98

2.30

2.64

2.97

3.30

0.99

0.593

0.264

NOTE :THE ABOVE E XPR E S S ION IS BAS E D ON ANGULARTHE ABOVE E XPR E S S ION IS BAS E D ON ANGULARC ONTAC T ANTI-FR IC T ION BE AR INGS ONLY.C ONTAC T ANTI-FR IC T ION BE AR INGS ONLY.

Total Thrust of 4457.3Total Thrust of 4457.3

Page 35Page 35

THRUST BEARINGHORSEPOWER

THRUST BEARINGHORSEPOWER

POWE R C ONS UMPTION OF E LE C TR IC MOTOR SPOWE R C ONS UMPTION OF E LE C TR IC MOTOR SThere are two methods commonly used to check the powerThere are two methods commonly used to check the powerconsumption of an electric motor.consumption of an electric motor.

The firs t of these requires the use of an ammeter andThe firs t of these requires the use of an ammeter andvoltmeter. The following formula is then used utilizing thevoltmeter. The following formula is then used utilizing theinstrument readings :instrument readings :

K ilowatts = I x E x P.F. x CK ilowatts = I x E x P.F. x C1000

where I = amperes (meter reading)where I = amperes (meter reading)E = volts (meter reading)E = volts (meter reading)

P.F. = Power Factor (S ee manufacturer'sP.F. = Power Factor (S ee manufacturer'spublished operating characteris tics forpublished operating characteris tics forvertical motors .)vertical motors .)

= 1.73 for three phase current= 1.73 for three phase current= 2 for two phase, four wire control= 2 for two phase, four wire control

C = 1 for s ingle phase currentC = 1 for s ingle phase current

The second method commonly used to determine powerThe second method commonly used to determine powerconsumption utilizes the watt-hour meter in the power line.consumption utilizes the watt-hour meter in the power line.The exact time for a given number of revolutions of the meterThe exact time for a given number of revolutions of the meterdisc is measured with a stopwatch and the following formuladisc is measured with a stopwatch and the following formulaused:

transformer is not used the equivalent ratiotransformer is not used the equivalent ratiopotential transformer ratio. (When eitherpotential transformer ratio. (When either

M = P roduct of current transformer ratio andM = Product of current transformer ratio and

where K = Disc constant, representing watt-hours perwhere K = Disc constant, representing watt-hours perK ilowatts = 3.6 x K x M x R /tK ilowatts = 3.6 x K x M x R /t

revolution. This factor is found on the meterrevolution. This factor is found on the meternameplate or painted on the disc.nameplate or painted on the disc.

is 1.)R = Total revolutions of watt-hour meter disc.R = Total revolutions of watt-hour meter disc.t = Time for total revolutions of disc in seconds .t = Time for total revolutions of disc in seconds .

C OS T OF PUMP ING US ING AN E LE C TR IC MOTORC OS T OF PUMP ING US ING AN E LE C TR IC MOTORThe cost of operating a vertical turbine pump may beThe cost of operating a vertical turbine pump may bedetermined by several different methods .determined by several different methods .

1. If the cost of operation per hour is des ired, the power1. If the cost of operation per hour is des ired, the powerconsumption as determined by use of the methodsconsumption as determined by use of the methodsprevious ly described may be used:previous ly described may be used:

2. The cost of operation may be estimated by determining2. The cost of operation may be estimated by determiningthe input horsepower and converting it to kilowatts :the input horsepower and converting it to kilowatts :

C ost/hour of operation = 1 HP x 0.746 x cost per KWh.C ost/hour of operation = 1 HP x 0.746 x cost per KWh.

3. A somewhat less accurate estimate may be made by3. A somewhat less accurate estimate may be made byusing the following formula:us ing the following formula:

C ost/hr. of operation = GPM x Tot. Hd. x 0.746 x C ost/KWhC ost/hr. of operation = GPM x Tot. Hd. x 0.746 x C ost/KWh3960 x Pump E ff. x Motor E ff.3960 x Pump E ff. x Motor E ff.

4. It is often des irable to express the cost of operating a4. It is often des irable to express the cost of operating apump in terms of "cost per 1000 gallons". To do this thepump in terms of "cost per 1000 gallons". To do this theabove figures of cost per hour of operation may be usedabove figures of cost per hour of operation may be usedwith the rated capacity of the pump as follows:with the rated capacity of the pump as follows:

C ost per 1000 Gallons = C ost per HourC ost per 1000 Gallons = C ost per Hour1000

5. For convenience the following table may be used to5. For convenience the following table may be used toestimate power consumption and cost of operation whenestimate power consumption and cost of operation whenthe overall efficiencies are known. The table gives powerthe overall efficiencies are known. The table gives powerconsumed pumping 1000 GPM at one foot total head atconsumed pumping 1000 GPM at one foot total head atvarious overall pump efficiencies .various overall pump efficiencies .

OVE R ALLE FF IC IE NC Y

PUMPUNIT

K ILOWATTSPE R 1000

GALLONS ATGALLONS ATONE FOOT TDH

323334

0.009800.009510.00922

0.008480.008710.00896

373635

383940

0.008260.008040.00784

0.007300.007470.00765

434241

444546

0.007130.006970.00682

494847

0.006400.006530.00667

505152

0.006270.006150.00603

555453

0.005700.005810.00592

565758

0.005600.005500.00541

616059

0.005140.005230.00532 0.00352

0.003488990

0.003560.003600.00365

888786

0.003780.003730.00369

838485

0.003820.003870.00392

828180

0.004070.004020.00397

777879

0.004130.004180.00424

767574

717273

0.004420.004350.00430

0.004480.004540.00461

706968

656667

0.004820.004750.00468

0.004900.004980.00506

646362

ONE FOOT TDHONE FOOT TDHGALLONS ATGALLONS AT

PE R 1000K ILOWATTSK ILOWATTS

UNITPUMP

E FF IC IE NC YOVE R ALL

Overall efficiency as indicated is the input-output efficiencyOverall efficiency as indicated is the input-output efficiencyincluding all losses in the pump unit, pumping 1000 gallonsincluding all losses in the pump unit, pumping 1000 gallonsof clear water one foot of total head. Therefore, inof clear water one foot of total head. Therefore, indetermining the kilowatts per 1000 gallon pumped, it isdetermining the kilowatts per 1000 gallon pumped, it isonly necessary to multiply the factor corresponding to theonly necessary to multiply the factor corresponding to theoverall efficiency by the number of feet head at which theoverall efficiency by the number of feet head at which thetotal dynamic head has been calculated.total dynamic head has been calculated.

E XAMPLE : Assume an overall efficiency of 65% and a totalE XAMPLE : Assume an overall efficiency of 65% and a totalhead of 200 feet.head of 200 feet.

K ilowatts per 1000 gallons = 0.00482 x 200 = 0.964K ilowatts per 1000 gallons = 0.00482 x 200 = 0.964

C ost/hour of operation = KW's consumed x cost per KWh.C ost/hour of operation = KW's consumed x cost per KWh.

Page 36Page 36

POWER CONSUMPTIONAND COST

POWER CONSUMPTIONAND COST

0

10

20

30

40

50

60

70

80

0 10 20 30 40 50 60 70 80 90 100

100

90

The driver must be capable of supplying more torque at each successive speed fromThe driver must be capable of supplying more torque at each successive speed fromzero to full load RPM than what is required by the pump in order to reach rated speed.zero to full load RPM than what is required by the pump in order to reach rated speed.This means that the Speed - Torque curve of the driver must not intersect the pumpThis means that the Speed - Torque curve of the driver must not intersect the pumptorque curve anywhere on the curve before 100% speed is reached.torque curve anywhere on the curve before 100% speed is reached.

Torque varies as the square of the speed; therefore, to obtain torque at:Torque varies as the square of the speed; therefore, to obtain torque at:3/4 speed - multiply full speed torque by 0.5633/4 speed - multiply full speed torque by 0.5631/2 speed - multiply full speed torque by 0.2501/2 speed - multiply full speed torque by 0.2501/4 speed - multiply full load speed torque by 0.0631/4 speed - multiply full load speed torque by 0.0631/8 speed - multiply full load speed torque by 0.0161/8 speed - multiply full load speed torque by 0.016

Torque (ft.Torque (ft. lbs.) =lbs.) =(5250) (BHP)(5250) (BHP)

RPM

NOTE: If the pump starts against a closed valve, use the shut off BHP for torque calculation.NOTE: If the pump starts against a closed valve, use the shut off BHP for torque calculation.

% SPEED% SPEED

%T

OR

QU

E%

TO

RQ

UE

*Based on Hydraulic Institute Standards.*Based on Hydraulic Institute Standards.Page 37Page 37

PUMP SPEED TORQUE

CURVE AND FORMULA

PUMP SPEED TORQUE

CURVE AND FORMULA

Webster defines it as the "action or process or effect of corroding" and corroding is defined as "eating away bydegrees by chemical action". Pertaining to pumps, we should think of corros ion as any action which is detrimentaltoits performance. Thus , a pump's performance can be destroyed by corros ion, abras ion or plugging action of solids ,or a combination of the above.

The usual is to think in terms of only one of theseconditions being present and affecting the pump'sperformance. In the case of metallic corros ion wherethis is true, the solution is one of selection ofmaterials in contact with the fluid which will corrodevery s lowly. Vertical pumps present additionalcons iderations in that because of costs , furtherrefinement between rotating and non-rotating, wettedparts may require examination. Many coatings havebeen developed and we will not attempt to adviseon the proper selection or application in this writing.The area where we notice the greatest difficulties arethose where corros ion and abras ion are present. Allmetals gain their projection against corros ive agentsby a thin skin of corros ion. If this skin is wipedclean, the metal will recorrode, forming a new skin.Thus , if minor amounts of abras ion are found in thecorros ive fluid, it is poss ible for these to cause thiswiping action. This will occur whenever the pumpedfluid abras ive content is harder than the skin corros ionor coating when it is used. Thus , soft abras ives canbe present in large quantities without caus ing excess ivewear. This condition is further activated by the velocitywithin the pump. By s lowing the pump speed orovers izing the pump for the des ign conditions , theinternal velocity is lowered. This will reduce theabras ive wear and can be considered on somecorros ion-abras ion problems.This brings us to the second combination which cancause difficulties . A vertical pump utilizes s leevebearings ins ide a bearing retainer for proper shaftsupport. The straightness of this shafting is the secretof long vertical pump life. E ach shaft runs with athin film of fluid around it. By centrifugal force, thisfilm is kept even in all bearings , thus assuringlubrication and balance in the pump. Anything whichupsets this balance can cause difficulties . Thus ,abras ion can wipe away bearing surfaces caus ing thebearing to become elliptical. The shaft then tends todestroy all bearings by its own out-of balance actionand the pump fails . This same difficulty can developin chemical fluids which tend to precipitate out. Thenthis solid material falling into the pump's path in largequantities causes an imbalance within the pump. Thiswill destroy it over a period of time even when thematerial has a lower brinell number than the pumpcomponents .The lack of lubricating qualities within the fluid cancause the same difficulties in the bearings . This isovercome by injection of a fluid with good lubricatingqualities at each bearing journal. This injected fluidmust be compatible with the fluid being pumped eventhough only small quantities are used. When abras ivesare present in corros ive fluids , this system can beutilized by taking the pumped fluid through a smallcentrifugal separator, building the pressure with a smallpump and lubricating the packing nut and the enclosedline shaft. This pressure should be approximately

12/15 PS I above the maximum design pressure. The shaftshould be in an enclosed tube or with fluid injectedthrough the spider to the line shaft bearing. By bringing aflushing line down to the tail bearing and rifle drilling theshaft, bearing holes can be bored at each of the bowlbearings . This will insure that clean fluid is being used forlubrication at each bearing. This flow will be away fromthe bearing, thus keeping all abras ives out in the mainfluid flow passage.One of the most difficult corros ive fluids to handle andunderstand is sea water. This is because of severalvariables which can alter the effects of this fluid upondifferent metals being employed. The firs t cons iderationis temperature. All corros ive fluids are more active as thetemperature is elevated. Therefore, where cast iron mightbe used successfully at 30°F, the story changes at 90°F.The other chemicals in sea water can cause difficultyif their presence is not known. Around oil docks , drilling,etc., sulfides might be present. E ven though found insmall quantities , this can cause the fluid to be much morecorros ive than just the primary fluid. The othercons ideration is the quantity of sand present. Offshoreinstallations are subject to tides and wave action. Thiscan cause the sand content to continually change andtherefore, present a difficult system to analyze. Theelectolitic action of diss imilar metals in the presence ofthe sea water must also be taken into account.The best corros ive defense is your own experience on anygiven unit. Thus , good records are a necess ity. E achpump should be checked for vibration and amperageperiodically. This information, along with the shut-offhead, should be noted in the permanent record. Anychanges should be cause for investigation. Any repairsshould be noted with complete description of parts used,materials and conditions of the parts being replaced.With this type of record, it is poss ible to ascertainimprovements in performance and be aware of whatmaterials or action brought them about. Without thisinformation it is not poss ible to be certain that thesolution is correct for a particular application andexpensive parts can be lost. C orros ion is a never-ceas ingbattle to extend the life of equipment to acceptableeconomic limits , and good records are essential forproper determination. A qualified J -Line sales engineerstands ready to ass is t you in this endeavor at all times -give us a call.

P age 38

CCORROSION

UUNITS PHE R E SATMOS -FE E T

OFWATE R

K ILOGR AMSPE R

S Q. C .M.

1 LB . PE R S Q. INC H1 LB . PE R S Q. INC H 1. 2.31 0.704 2.04 0.0681 0.0703

0.03050.029470.8820.3051.0.4331 FT. OF WATE R1 FT. OF WATE R

1 ME TE R OF WATE R1 ME TE R OF WATE R 1.421 3.28 1. 2.89 0.0967 0.1

0.03450.03341.0.34561.1340.4911 INC H OF ME R C UR Y1 INC H OF ME R C UR Y

14.70 33.93 10.34 29.92 1. 1.033

1 K ILOGR AM PE R S Q. C .M.1 K ILOGR AM PE R S Q. C .M. 14.22 32.8 10. 28.96 1.0.968

UNITS OF PR E S S UR E AND HE AD

INC HS QUAR ELBS . PE RLBS . PE R

WATE ROF

ME TE R S

ME R C UR YOF

INC HE S

1 ATMOS PHE R E1 ATMOS PHE R E(AT S E A LE VE L)(AT S E A LE VE L)

E quivalent units are based on density of fresh water from 32° to 62°F.E quivalent units are based on density of fresh water from 32° to 62°F.E quivalent units are based on density of mercury from 32° to 62° F. - sufficient accuracy.E quivalent units are based on density of mercury from 32° to 62° F. - sufficient accuracy.E ach 1000 ft. of ascent decreases pressure about 1/2 lb./sq. in.E ach 1000 ft. of ascent decreases pressure about 1/2 lb./sq. in.

UNITS OF VOL UME AND WE IGHTUNITS OF VOL UME AND WE IGHT

1 C UBIC FOOT1 C UB IC FOOT 7.48 6.23 1728. 1. 0.0000230 62.4

0.03610.0005791.0.003600.004331 C UB IC INC H1 C UB IC INC H

1 IMPE R IAL GALLON1 IMPE R IAL GALLON 1.201 1. 277.4 0.1605 0.00000369 10.02

8.350.000003070.1337231.0.8331.1 U.S . GALLON1 U.S . GALLON

AC R EFE E TUNITS FE E T

C UB ICINC HE SC UB IC

GALLONSIMPE R IAL

GALLONSU.S .

0.003785

0.004546

0.02832 28.32

0.0164

4.546

3.785

LITE R SPOUNDS* C UB IC

ME TE R S

1233.51.43.560271.335325.8501 AC R E - FOOT1 AC R E - FOOT

0.4541.0.016027.70.09980.1201 POUND1 POUND

1000.1.2205.0.00081135.31461.023220.264.21 C UB IC ME TE R1 C UB IC ME TE R

1.2.2050.03530.0610230.2200.26421 LITE R1 LITE R

*WTS . S hown based on maximum density of fresh water at 39° Fahrenheit.*WTS . S hown based on maximum density of fresh water at 39° Fahrenheit.

1 HE C TAR E1 HE C TAR E 107,639. 11,960. 2.471 1.

1 S QUAR E ME TE R1 S QUAR E ME TE R 1549. 10.76 1.196 0.000247

0.00386

10.000 1.

1 S QUAR E C E NTIME TE R1 S QUAR E C E NTIME TE R 0.155 0.001076 1.

1 S QUAR E MILE1 S QUAR E MILE 27,878,400. 640. 1.

ME TE R SS QUAR E HE C TAR E S

0.4054049.

0.0929

S QUAR EINC H

S QUAR EFE E T

S QUAR EYAR DUNITS MILE S

S QUAR E

1 S QUAR E INC H1 S QUAR E INC H 1. 0.00694 0.00077 6.452

929.0.1111.144.1 S QUAR E FOOT1 S QUAR E FOOT

1 S QUAR E YAR D1 S QUAR E YAR D 1296. 9 1. 0.000207 8361.

0.001561.4840.43,560.1 AC R E1 AC R E

UNITS OF AR E AUNITS OF AR E A

AC R E SS QUAR E

ME TE RC E NTI-

3,097,600.

0.836

0.0001

10,000.

258.

0.0001

99,996,631.

2,593,388.16

Page 39Page 39

CONVERSION TABLES

1 U.S . GALLON1 U.S . GALLONPE R MINUTE

U.S .GALLONS

PE RMINUTE

UNITSPE R DAYPE R DAYGALLONS

U.S .MILLION C UB IC

FE E TPE R

S E C OND HOURPE R

ME TE R SC UB IC LITE R S

PE RS E C OND

MINE R 'S INC H*MINE R 'S INC H*

I II III

1. 0.001440 0.00223 0.2270 0.0631 0.0891 0.1114 0.0856

59.477.461.943.8157.731.5471.694.5PE R DAYPE R DAY

1 MILLION U.S . GALLONS1 MILLION U.S . GALLONS

1 C U. FOOT PE R S E C .1 C U. FOOT PE R S E C . 448.8 0.646 1. 101.9 28.32 40. 50. 38.4

0.27781.0.009810.006344.4031 C U. ME TE R PE R HOUR1 C U. ME TE R PE R HOUR

1 LITE R PE R S E C .1 LITE R PE R S E C . 15.85 0.0228 0.0353 3.60 1.

0.02500.0161811.22I

1 MINE R 'S INC H*1 MINE R 'S INC H* 8.98 0.01294 0.0200II

11.69 0.01682 0.0260III

IV 0.02800.0181112.58

UNITS OF FLOWUNITS OF FLOW

*The Miner's Inch varies in definition in different areas . S tate laws have set the value as follow:*The Miner's Inch varies in definition in different areas . S tate laws have set the value as follow:I. 40 M.I. = 1 C FS . in Arizona, C alifornia, Montana and OregonI. 40 M.I. = 1 C FS . in Arizona, C alifornia, Montana and OregonII. 50 M.I. = 1 C FS . in Idaho, Nebraska, Nevada, New Mexico, Utah, Kansas , S . Dakota, N. DakotaII. 50 M.I. = 1 C FS . in Idaho, Nebraska, Nevada, New Mexico, Utah, Kansas , S . Dakota, N. Dakota

III. 38.4 M.I. = 1 C FS . in C oloradoIII. 38.4 M.I. = 1 C FS . in C oloradoIV. 35.7 M.I. = 1 C FS . in B ritish C olumbiaIV. 35.7 M.I. = 1 C FS . in B ritish C olumbiaUsual practice in S outhern C alifornia, 50 M.I. = 1 C FS = 448.8 GPMUsual practice in S outhern C alifornia, 50 M.I. = 1 C FS = 448.8 GPM

POWE RHOR S E -ME TR IC

UNITS POWE RHOR S E - K ILOWATTSWATTS

FT.-LBS .PE R

MINUTE

B .T.U.PE R

MINUTE

1 HOR S E POWE R 1. 33,000. 746. 0.746 1.014 42.4

0.0012850.00003070.00002260.02261.0.00003031 FT.-LB . PE R MINUTE1 FT.-LB . PE R MINUTE

1 WATT1 WATT 0.001340 44.2 1. 0.001 0.001360 0.0568

56.81.3601.1000.44,250.1.3411 K ILOWATT1 K ILOWATT

1 ME TR IC HOR S E POWE R1 ME TR IC HOR S E POWE R 0.986 32,550. 736. 0.736 1. 41.8

1 BTU PE R MINUTE1 BTU PE R MINUTE 0.0236 778.4 17.6 0.0176 1.0.0239

UNITS OF POWE RUNITS OF POWE R

UNITS OF LE NGTHUNITS OF LE NGTH

1 Inch = 0.0833 ft. = 0.0278 yd. = 25.4 millimeters = 2.54 centimeters1 Inch = 0.0833 ft. = 0.0278 yd. = 25.4 millimeters = 2.54 centimeters1 Foot = 12 inches = 0.333 yd. = 30.48 centimeters = 0.3048 meters1 Foot = 12 inches = 0.333 yd. = 30.48 centimeters = 0.3048 meters1 Yard = 36 inches = 3 feet = 91.44 centimeters = 0.9144 meters1 Yard = 36 inches = 3 feet = 91.44 centimeters = 0.9144 meters1 Mile = 5280 ft. = 1760 yds . = 1.61 kilometer = 1609 meters1 Mile = 5280 ft. = 1760 yds . = 1.61 kilometer = 1609 meters1 Meter = 3.281 ft. = 39.37 in. = 0.000622 miles = 0.001 kilometers1 Meter = 3.281 ft. = 39.37 in. = 0.000622 miles = 0.001 kilometers1 K ilometer = 1000 meters = 1093.61 yds . = 0.62137 miles = 3281 feet1 K ilometer = 1000 meters = 1093.61 yds . = 0.62137 miles = 3281 feet

Page 40Page 40

CONVERSION TABLES

COL.

S IZE

S IZE

S HAF

T

S IZE

TUBE G.P.M

.25 50 75

3" 3/4" 11/

4"1

1/4"

4"

3/4" 11/

4"1

1/4"

11/

2"

1"

2"13/

16"

13/

16"

13/

16"

2"

1" 11/

2"1

1/4"

11/

4"

3/4"

5"6"

1" 11/

2"1

1/2"

2"13/

16"

21/

2"

11/

2"1

3/16

"

2"2

1/2"

21/

2"

11/

2"1

1/2"

3"115

/16"

115

/16"

23/

16"

23/

16"

31/

2"3

1/2"

12"

S IZE

COL.

S HAF

TS I

ZETU

BES I

ZEG.

P.M.

1.8

4.6

9.0

1.3

0.65

0.86 1.7

3.3

1.6

100

125

150

175

275

250

225

200

375

350

325

300

550

500

450

400

750

700

650

600

950

900

850

800

1000

1200

1400

1600

1800

2800

2600

2400

2200

2000

3800

3600

3400

3200

3000

4800

4600

4400

4200

4000

14.0

2.2

2.8

5.3

0.54

0.65

0.94 1.4

0.96

0.81

7.8

4.2

3.2

4.4

5.8

10.6

1.1

1.3

1.9

2.5

1.7

1.5

13.8

7.5

5.8

7.3

9.4

17.1

1.8

2.2

3.1

1.4

0.96

0.73

0.90

1.2

1.7

3.9

2.7

2.3

21.1

12.0

9.0

13.0

16.8

14.0

10.9

2.7

3.3

4.7

2.0

1.4

1.1

3.3

3.9

5.6

2.4

1.7

1.3

15.2

19.2

19.8

1.5

2.0

2 .8

6.4

4.5

3.8

1.7

2.3

3.2

7.4

5.2

4.4

2.0

2.6

3.6

8.4

6.0

5.0

2.2

2.9

4.1

9.5

6.7

5.6

6.3

7.5

10.6

4.6

3.3

2.5

7.8

9.3

13.1

5.7

4.1

3.1

9.2

11.2

15.7

6.9

5.0

3.7

11.0

13.2

18.6

8.1

5.8

4.4

19.0

16. 8

14.8

12.9

15.5

20.3

7.9

10.3

14.1

6.9

9.1

12.5

6.0

7.9

11.0

5.2

6.8

9.5

15.7

11.5

8.8

17. 7

12. 8

9.9

19.5

14.3

11.0

21.5

15.8

12.1

10"

13/

16"

2"2

1/2"

21/

2"

11/

2"

3'115

/16"

115

/16"

115

/16"

3"

11/

2"1

1/2"

21/

2"2

1/2"

2"13/

16"

13/

16"

8"

25 50 75 100

125

150

175

225

200

275

250

375

350

325

300

550

500

450

400

750

700

650

600

950

900

850

800

1000

1200

1400

1600

1800

280 0

2600

2400

2200

2000

3800

3600

3400

3200

3000

4800

4600

4400

4200

4000

The

follo

wing

table

will s

erve

asa

guide

inTh

efo

llowi

ngta

blewi

llser

veas

agu

idein

figur

ingco

lumn

fricti

onlos

ses t

oall

owfo

rfig

uring

colum

nfri

ction

losse

s to

allow

for

cond

ition

ofpip

e:co

nditio

nof

pipe:

Cond

ition

ofPi

peof

Pipe

Insid

e

Appr

ox. A

geof

Appr

ox. A

geof

Pipe

inOr

dina r

yPi

pein

Ordin

ary

Use

for C

oldUs

efo

r Cold

Clea

r Wat

erCl

ear W

ater

follo

wing

facto

rfo

llowi

ngfa

ctor

mult

iplied

byth

em

ultipl

iedby

the

Figu

res f

rom

table

Figu

res f

rom

table

Use

Frict

ionLo

ssUs

eFr

iction

Loss

Very

Smoo

th

Smoo

thFa

irly

6or

mor

e6

orm

ore

year

s

New

1.00

1.5 1

1- 5

year

s1

- 5ye

ars

2.35

Roug

h

COLU

MN

FRIC

TION

LOSS

(INFE

ET) P

ER10

0FE

ETOF

COLU

MN

COLU

MN

FRIC

TION

LOS S

(INFE

E T) P

E R10

0FE

E TOF

COLU

MN

10.7

11.8

12.9

13.9

15.0

17.2

15.8

14.6

13.4

12.2

21.0

19.3

17.9

16.4

15.0

6.0

5.6

5.1

4.7

4.3

6.8

6.3

5.8

5.3

4.9

7.9

7.4

6.7

6.2

5.6

9.0

8.4

7.7

7.1

6.4

6.4

7.1

7.9

8.8

9.8

11.1

10.0

9.0

8.1

7.4

13.7

12.4

11.1

9.9

8.8

3.9

3.5

3.2

2.8

2.5

4.4

4.0

3.6

3.2

2.9

5.1

4.7

4.2

3.7

3.3

5.9

5.3

4.8

4.3

3.8

1.8

2.1

2.5

2.9

3.3

1.6

1.9

2.2

2.5

2.8

1.4

1.6

1.9

2.2

2.5

1.2

1.4

1.7

1.9

2.2

4.2

5.0

5.8

6.8

7.8

3.5

4.1

4.9

5.6

6.4

5.6

4.9

4.2

3.6

3.0

19.2

22.9

22.4

19.3

16.5

13.0

11.0

13.2

15.5

17.9

20. 5

0.50

0.71

0.94 1.2

1.5

0.44

0.62

0.82 1.1

1.3

0.38

0.54

0.71

0.90 1.1

0.34

0.47

0.62

0.80

0.99

1.2

1.6

2.2

2.8

3.4

0.97 1.4

1.8

2.3

2.8

0.85 1.2

1.6

2.0

2.5

5.4

7.6

10.0

13.0

15. 7

3.9

5.4

7.2

9.1

11.0

9.4

7.6

6.0

4.5

3.2

1.1

0.88

0.77

0.96

0.80

0.70

0.86

0.72

0.63

0.77

0.65

0.57

2.2

2.6

3.6

2.4

2.9

4.0

2.7

3.2

4.5

2.9

3.5

4.9

3.2

2.3

1.9

2.8

2.0

1.7

2.5

1.8

1.5

2.1

1.5

1.3

0.61

0.74

1.0

0.77

0.91

1.3

0.93

1.1

1.5

1.1

1.3

1.8

P age 41Page 41

TURBINE COLUMNFRICTION LOSS TABLE

TURBINE COLUMNFRICTION LOSS TABLE

227.421.416.111.59.447.605.934.463.192.111.240.890.580.340.161.11

1.672.222.773.334.445.556.667.788.9010.011.113.315.617.81600

140012001000900800700600500400300250200150100

6" 6.065 I.D.

VE LOC ITYFT. PE R

S E C ONDPE R MIN.GALLONS

U.S .

6 INC H6 INC H

0.070.160.280.420.580.991.502.102.793.604.465.447.6210.113.0

S TE E LC =100

FT. HE AD/100 FT. P IPEFT. HE AD/100 FT. P IPEFR IC T ION LOS S

C =150PVCPVC

C =150

FR IC T ION LOS SFR IC T ION LOS SFT. HE AD/100 FT. P IPE

C =100S TE E L

33.627.021.115.911.37.525.824.413.122.081.220.870.580.340.16

41.129.419.415.211.78.155.393.172.271.501.170.880.630.420.241.22

1.632.042.452.863.274.094.906.548.179.8011.413.116.319.61200

100080070060050040030025020017515012510075

5" 5.00 I.D.

100 FT.100 FT.FT. HE AD/

HE AD LOS SVE LOC ITYFT. PE RFT. PE R


U.S .

5 INC H5 INC H4 INC H4 INC H

U.S .GALLONSPE R MIN. S E C OND

FT. PE RFT. PE RVE LOC ITY

4" 4.026 I.D.

5075

100125150200250300350400500600700800900 22.7

20.217.615.112.610.18.827.576.305.053.783.152.521.891.26 0.33

0.701.191.802.534.296.459.0912.015.523.432.843.655.869.3

97.880.564.750.538.027.118.014.811.99.286.984.983.301.940.911.82

2.723.634.545.456.357.268.169.0811.313.615.918.220.522.7500

450400350300250200180160140120100806040

3" 3.00 I.D.3" 3.00 I.D.

100 FT.FT. HE AD/

HE AD LOS SVE LOC ITYFT. PE R


U.S .

3 INC H3 INC H

750070006500

2400260028003000320034003600380040004500500055006000

220020001900180017001600150014001300120011001000900800

100 FT.100 FT.FT. PE RHE ADVE LOC ITY

HE ADFT.

10 INC H10 INC H

FLOWGALLONSPE R MIN. S E C OND


10" S TD. WT. S TE E L 10.02" I.D.10" S TD. WT. S TE E L 10.02" I.D.

180200220240260280300350400450500550600650700 2.85

2.642.442.242.041.831.631.421.221.141.060.980.890.810.73

3.253.664.074.484.895.305.706.106.516.927.327.738.148.95

18.3016.3015.5014.6013.8013.0012.2011.4010.609.76

20.3022.4024.4026.4028.5030.50

0.130.110.090.080.060.050.040.030.020.020.020.010.010.010.01

0.160.210.260.310.370.440.500.580.660.740.830.931.031.24

10.89.307.806.405.204.103.703.303.002.702.302.001.701.48

12.614.5 41.500

36.500

5.0405.8406.7007.6108.5809.600

10.70011.80013.00016.10019.60023.40027.50031.800

4.2903.6003.2702.9602.6602.3802.1101.8601.6201.4001.1900.9980.8210.660

0.0420.0510.0610.0710.0830.0950.1080.1430.1830.2280.2770.3300.3880.4500.5160.554

0.4330.3250.2860.2500.2150.1830.1540.1400.1260.1140.1020.0910.0790.069

0.6890.8380.9991.1701.3601.5601.7701.9902.2302.4802.7403.0203.6004.230

48.80039.20030.60023.00020.30017.70015.20013.00010.9008.9507.2006.3905.6204.900

59.30070.70019.40

15.90

1.081.251.441.702.102.503.103.704.305.005.707.80

10.2012.90

0.920.770.640.580.520.460.410.360.310.270.230.190.160.13

0.010.010.010.020.020.020.020.030.030.040.040.050.060.080.10

35.3032.0028.8025.6022.4019.20

8.338.979.61

10.3011.5012.8014.1015.4016.7018.00

7.697.056.416.095.775.455.134.814.494.173.853.523.202.88

0.830.900.961.031.091.151.221.281.411.541.671.801.922.242.57400

350300280260240220200190180170160150140130


VE LOC ITYFT. PE R


FLOW

8 INC H8 INC H

FT.HE AD

VE LOC ITY HE ADFT. PE R100 FT.

450500550600650700750800850900950

100011001200

4000350030002800260024002200200018001600150014001300

450050005500

1100012000130001400015000160001700018000200002200024000

100009000800070006000500045004000350030002500200019001800


HE ADFT.

14 INC H14 INC H

FLOWGALLONSPE R MIN.PE R MIN. S E C OND

FT. PE RVE LOC ITY

14" S TD. WT. S TE E L 13.25" I.D.

300400500600700800900

10001100120013001400150016001700 3.95

3.723.493.263.022.792.562.332.091.861.631.401.160.930.70

4.194.424.655.816.988.159.3110.511.614.016.318.620.923.3

51.246.541.939.537.234.932.630.227.925.6

55.8

0.240.220.190.170.140.120.100.080.070.050.040.030.020.010.01

0.270.300.340.520.761.031.351.702.103.004.105.406.808.40

48.440.733.627.324.221.518.916.514.212.110.2 21.600

25.40029.50033.80038.40043.30048.40053.80065.40078.00091.600

18.10014.90012.000

9.3807.0505.0304.1303.3202.6001.9601.4000.9240.8400.760

0.0280.0470.0710.1000.1320.1700.2110.2560.3060.3590.4160.4770.5420.6110.6840.581

0.4950.4150.3410.2750.2140.1610.1370.1150.0950.0760.0590.0450.0320.021

0.6740.7730.8780.9901.2301.5001.7802.1002.4302.7803.1704.2105.3906.700

47.70041.20035.00029.40026.70024.20021.70019.40017.30015.20013.20011.4009.7208.150

54.70062.20028.2

24.6

3.103.804.505.306.207.108.009.1010.211.312.515.118.121.2

2.502.001.541.130.980.850.720.610.500.410.320.280.250.21

0.010.010.010.020.020.030.030.040.050.060.080.100.130.150.18

42.639.836.934.131.228.4

14.215.617.018.419.921.322.724.225.627.0

12.811.49.958.527.957.386.816.255.685.114.554.263.983.69

0.570.710.850.991.141.281.421.561.701.992.272.562.843.123.411200

11001000900800700600550500450400350300250200


VE LOC ITYFT. PE RFT. PE R


FLOW

12 INC H12 INC H

FT.HE AD

VE LOC ITY HE ADFT. PE R

100 FT.100 FT.

13001400150016001800200022002400260028003000350040004500

1200011000100009500900085008000750070006500600055005000

130001400015000

Page 42

FRICTION LOSSES IN STEELPIPES-3 THROUGH 36 INCHFRICTION LOSSES IN STEELPIPES-3 THROUGH 36 INCH

22000022000240002500026000280003000032000340003600038000

1800016000150001400013000120001100010000900080007000600050004500


HE ADFT.

16 INC H16 INC H

FLOWGALLONSPE R MIN. S E C OND



500600700800900

1000120014001600180020002500300035004000 7.03

6.155.274.393.513.162.812.462.111.761.581.411.231.050.88

7.918.7910.512.314.115.817.619.321.122.824.626.328.131.6

63.359.856.252.749.245.743.942.238.735.1

66.8

0.770.590.430.300.190.160.120.090.070.050.040.030.020.020.01

0.971.201.702.403.103.904.805.806.908.109.4010.712.315.5

69.362.355.649.143.237.632.630.027.723.319.1 33.000

39.30046.20049.90053.60061.50069.80078.70088.30097.600

108.000

27.10021.80019.20017.10014.90012.80010.9009.1507.5306.0604.7303.5602.5402.090

0.0360.0500.0670.0860.1060.1290.1810.2410.3080.3830.4660.7040.9871.3101.680 0.941

0.7350.5530.3940.2610.2150.1730.1350.1010.0720.0600.0480.0370.0280.020

1.1701.4201.9902.6503.3904.2205.1207.1809.550

12.20015.20018.50022.00025.900

86.30079.40072.90066.60060.60054.80049.40044.10039.10034.40030.00020.1

23.426.830.534.538.743.047.152.657.863.0

17.114.311.99.607.605.804.303.002.401.901.501.100.740.60

0.010.010.010.020.020.030.040.060.080.100.120.190.270.370.48

63.7

36.038.841.544.347.149.952.655.458.261.0

33.230.327.724.922.119.416.613.812.511.19.708.316.926.23

0.690.830.971.111.251.381.661.942.212.492.773.464.154.855.544000

350030002500200018001600140012001000900800700600500




FLOW

18 INC H18 INC H

FT.HE AD


450050006000700080009000

1000012000140001600018000200002200024000

4600044000420004000038000360003400032000300002800026000 14000

1500016000180001900020000

1300012500120001100010000970090008300760069006500620059005500


HE ADFT.

24 INC H24 INC H


FT. PE RVE LOC ITY

24" S TD. WT. S TE E L 24" I.D.24" S TD. WT. S TE E L 24" I.D.

350700

1000140017002000240027003100340038004200450048005200 3.690

3.4103.2002.9902.7002.4102.2101.9201.7001.4201.2100.9990.7120.4950.252

3.9104.1904.4104.6204.9005.4005.9006.4006.9007.1107.8208.5508.8609.250

14.20013.50012.80011.38010.6309.950

0.2100.1800.1600.1300.1130.0900.0800.0600.0450.030.020.010.010.000.00

0.2400.2700.3200.3300.3700.5000.5400.6400.7400.7900.9501.1401.2201.340

3.1602.8502.5702.0201.7701.540 1.860

2.1102.4202.9803.2803.610

1.6301.5201.4001.1901.0000.9500.8200.7130.6030.5020.4500.4130.3770.329

0.0020.0070.0140.0260.0380.0510.0710.0890.1140.1360.1670.2000.2260.2550.2981.980

1.5501.1700.8320.5510.4300.3230.2310.1530.1260.1010.0790.0590.0420.028

3.0004.2005.5906.3507.1508.900

10.80012.90015.10016.30017.60020.10022.90025.800

110.00095.70082.30070.30058.90048.50039.00035.40032.10030.40028.90022.2

23.524.927.730.838.947.958.069.081.094.0

19.717.215.013.012.011.19.307.706.204.904.303.702.701.90

0.010.020.030.040.050.060.080.120.170.240.310.480.690.941.20

77.8

37.838.940.042.244.550.055.561.166.772.2

35.633.331.128.927.826.724.422.220.017.816.715.513.311.1

0.891.111.331.551.782.002.222.783.333.894.455.556.677.788.898000

7000600050004000350030002500200018001500140012001000800




FLOW

20 INC H20 INC H

FT.HE AD


1000012000140001500016000180002000022000240002500026000280003000032000

7000065000600005500050000450004000038000360003500034000

260002800030000340003800042000

2400023000220002100020000190001800016000150001400013000120001100010000


HE ADFT.

36 INC H36 INC H


FT. PE RVE LOC ITY


140017002000240028003400400048005600620070007600830090009700 3.05

2.832.612.392.201.951.761.511.261.070.880.750.630.530.44

3.143.463.784.094.404.715.035.665.986.306.606.927.247.55

13.2011.9510.709.448.808.18

0.140.120.100.090.070.060.050.040.020.020.010.010.010.000.00

0.160.190.220.260.300.340.390.500.560.610.670.740.810.88

2.702.201.771.381.201.04 0.806

0.9351.0651.3401.6501.990

0.6950.6400.5900.5440.5040.4540.4120.3300.2940.2600.2260.1930.1640.139

0.0040.0050.0070.0100.0150.0190.0260.0360.0480.0570.0720.0840.0980.1140.1310.112

0.1010.0870.0770.0650.0570.0460.0390.0300.0230.0170.0130.0080.0040.002

0.1270.1390.1700.2030.2400.2780.3190.3370.4010.4730.5100.5500.6300.710

2.2701.7301.2201.1101.0000.8100.83

1.051.171.301.892.46

0.730.640.550.510.47

0.3920.3250.3060.260.220.180.150.120.11

0.000.000.010.010.010.020.020.030.040.050.060.070.080.090.10

7.3008.2008.6709.120

10.09012.750

6.8506.4005.9405.7005.4705.0104.5604.4204.1003.7903.4703.1202.8302.690

0.3220.4500.5900.7800.9101.0951.2301.4301.5501.7401.8702.0502.1902.3702.5105500

5200480045004100380034003100270024002000170013001000700




FLOW

30 INC H30 INC H

FT.HE AD


5900620069007600830090009700

10000110001200012500130001400015000

280002400020000190001800016000

Page 43

FRICTION LOSSES IN STEELPIPES-3 THROUGH 36 INCH (CONT.)

FRICTION LOSSES IN STEELPIPES-3 THROUGH 36 INCH (CONT.)

FR IC T ION LOS S E S AS E QUIVALE NT LE NGTHS OF P IPE - FE E TFR IC T ION LOS S E S AS E QUIVALE NT LE NGTHS OF P IPE - FE E TNominal S ize of P ipe and F ittingNominal S ize of P ipe and F itting

Type of fitting and applicationType of fitting and application 3" 4" 5" 6" 8" 10" 12" 14" 16" 20" 24" 30"E LBOWS -E LBOWS -90° S tandard E lbow - or R un of Tee reduced by 1/290° S tandard E lbow - or R un of Tee reduced by 1/290° Long R adius - or R un of S tandard Tee90° Long R adius - or R un of S tandard Tee45° S tandard45° S tandard

76615040353025201513107.75040342724201714108.56.85.2352824191714129.47.15.94.73.6

S tandard Tee through S ide OutletS tandard Tee through S ide Outlet 16 20 26 31 40 51 61 71 81 101 121 151

Ordinary E ntranceOrdinary E ntranceS wing C heck Valve (fully open)S wing C heck Valve (fully open)Gate Valve (fully open)Gate Valve (fully open)

4.5 6.0 7.3 9.0 12 15 17 20 22 28 35 4320 26 33 39 52 65 77 90 104 129 155 1931.6 2.1 2.7 3.2 4.3 5.3 6.4 7.5 8.5 11 13 16

129.47.15.94.7-3.632.62.11.71.3-1313-9-765432.5-9.47.15.94.74.13.632.62.11.71.3

S tandard Tee withS tandard Tee withflow through branchflow through branch

45° E lbow45° E lbow

3 4 4 5 6 8 9 10 13 15 20 -6 7 8 9 10 14 - 17 - 25 - -3 4 4 5 6 8 - 10 13 15 20 25

to half s izeto half s izeor run of tee reducedor run of tee reduced90° S tandard E lbow,90° S tandard E lbow,

10"8"6"5"4"3 1/2"3 1/2"3"2 1/2"2 1/2"2"1 1/2"1 1/2"1 1/4"1 1/4"1"Type of F ittingType of F itting

F ITT INGS - F riction losses expressed as equivalent lengths of pipe (feet)F ITT INGS - F riction losses expressed as equivalent lengths of pipe (feet)

12"30--

--

14

MaterialS teel

P lasticC opper

S teelP lasticC opper

C opperP lasticS teel 61

--6 8 9 11 14 16 18 20 26 31 40 -

9 12 13 17 20 23 - 29 - 45 - -6 8 9 11 14 16 - 20 26 31 40 51

90° long radius90° long radiuselbow, or run ofelbow, or run of

1714108.56.8-5.24.23.62.82.31.7--17-12-1087543-14108.56.86.15.24.23.62.82.31.7 -

-20S teel

P lasticC opper

standard teestandard tee

Insert couplingInsert couplingC opperP lasticS teel -

--3 3 3 3 3 3 - 3 - 3 - -

1 1 1 1 1 1 1 1 1 1 1 -3 3 3 3 3 3 - 3 - 3 - -

fitting to threadfitting to threadAdapter-s lip/solder

Gate Valve (fully open)Gate Valve (fully open)S wing C heck ValveS wing C heck ValveOrdinary entranceOrdinary entrance

5.34.33.22.72.11.851.61.41.150.950.800.60675239332623201613119715129.07.36.05.24.53.73.02.42.01.5 17

776.4

Page 44Page 44

FRICTION LOSSES IN STEELPIPES-3 THROUGH 30 INCHFRICTION LOSSES IN STEELPIPES-3 THROUGH 30 INCH

C AS T DIS C HAR GE HE AD FR IC T ION LOS S C HAR TC AS T DIS C HAR GE HE AD FR IC T ION LOS S C HAR T

Discharge S izeDischarge S ize

6"100

8"

200 300 400 500 600 700 800 1000 1200 1400C apacity in Gallons Per MinuteC apacity in Gallons Per Minute

0.016 0.062 0.140 0.2480.078

0.3880.125

0.5580.176

0.7600.226

0.9220.312

1.5500.488 0.703 0.958

C apacity in Gallons Per MinuteC apacity in Gallons Per Minute500045004000350030002500200015001000500

10" 1.7311.2020.7690.4330.1920.04812"14"

0.091 0.204 0.363 0.565 0.861 1.110 1.1450.201 0.314 0.452 0.615 0.803 1.017 1.255

2.2421.5570.9960.8070.6380.4883.4092.1821.7671.3961.0690.7860.545

12"10"

0.812 1.216 1.827 2.487 3.2488"800 1000 1200 1400 1600 1800 2000 2500 3000 4000

C apacity in Gallons Per MinuteC apacity in Gallons Per Minute

2.6202.1221.2830.6550.4193.2332.0690.517

C apacity in Gallons Per MinuteC apacity in Gallons Per Minute70060050040030020018014010080

3"

402"

Discharge S izeDischarge S ize

VE R T IC AL TUR B INE FAB DIS C HAR GE HE AD FR IC T ION LOS S C HAR TVE R T IC AL TUR B INE FAB DIS C HAR GE HE AD FR IC T ION LOS S C HAR T

4" 0.534 0.675 0.834 1.875 3.3331.9321.4190.9900.6300.3550.2206"

14" 0.523 0.646 1.009 1.453 2.58416" 0.554 0.798 1.419

5000

2.217

Page 45Page 45

CAST DISCHARGE HEADFRICTION LOSS CHART

CAST DISCHARGE HEADFRICTION LOSS CHART

ME C HANIC AL FR IC T ION IN TUR B INE PUMP LINE S HAFTSME C HANIC AL FR IC T ION IN TUR B INE PUMP LINE S HAFTS(HOR S E POWE R /100 FE E T S HAFT LE NGTH)(HOR S E POWE R /100 FE E T S HAFT LE NGTH)

S HAFT DIA.S HAFT DIA.(inches)

B .H.P. AT R .P.M.B .H.P. AT R .P.M.3450 2900 2200 1760 1460 1160 880 700

3/41

1 3/161 3/161 1/2

1 11/161 11/161 15/161 15/162 3/162 3/162 7/162 7/16

0.220.250.300.380.65 0.52 0.45 0.350.871.04

1.44 1.20 0.440.600.720.901.44 1.15 0.95 0.741.922.30 0.56

0.700.921.201.401.80 1.50 1.20 0.90 0.72

0.921.151.501.902.302.85 2.40 1.85 1.40 1.13

S HAFT WE IGHTS (WT./FT. - LBS .)S HAFT WE IGHTS (WT./FT. - LBS .)S HAFT DIAME TE RS HAFT DIAME TE R E NC LOS E D *(1)E NC LOS E D *(1) OPE N

3/4 1.50 1.302.302.6013.303.801 3/161 3/165.306.001 11/161 11/166.307.601 15/161 15/168.8010.002 3/162 3/1611.2012.802 7/162 7/16

*NOTE : (1) Oil lubricated shaft does not displace*NOTE : (1) Oil lubricated shaft does not displaceliquid above the pumping water level and thereforeliquid above the pumping water level and thereforehas a greater net weight.has a greater net weight.

Page 46Page 46

MECHANICAL FRICTION INTURBINE PUMP LINE SHAFTS

MECHANICAL FRICTION INTURBINE PUMP LINE SHAFTS

Hardness is one of the phys ical properties generally cons idered to be an important factor in the selection of theHardness is one of the phys ical properties generally cons idered to be an important factor in the selection of thebestmaterial for given service. Numerous methods have been developed to describe the degree of hardness of a material.material for given service. Numerous methods have been developed to describe the degree of hardness of a material.B rinell, R ockwell, Vickers and S hore are the most widely used scales and can be compared by use of the convers ionBrinell, R ockwell, Vickers and S hore are the most widely used scales and can be compared by use of the convers iontables on the following pages . As you will note, various scales must be used with the Brinell and R ockwell methodstables on the following pages . As you will note, various scales must be used with the Brinell and R ockwell methodsin order to cover the full range of hardness . Only the more commonly used scales are lis ted in the table. A hardin order to cover the full range of hardness . Only the more commonly used scales are lis ted in the table. A hardmaterial (high hardness number) is likely to have a high tens ile strength and be somewhat brittle. The tens ilematerial (high hardness number) is likely to have a high tens ile strength and be somewhat brittle. The tens ilestrengthof steel can be roughly approximated by multiplying the Brinell hardness by 500.of steel can be roughly approximated by multiplying the Brinell hardness by 500.The approximate range of B rinell hardness for a number of the metals commonly used are:The approximate range of B rinell hardness for a number of the metals commonly used are:

ME TAL TE NS ILE S TR E NGTH (PS I)TE NS ILE S TR E NGTH (PS I) BR INE LL HAR DNE S S R ANGEBR INE LL HAR DNE S S R ANGEC AS T IR ONC AS T IR ON 30,000 190 - 210190 - 210

40,00050,00075,000 - 135,00075,000 - 135,000410 - 416 S TAINLE S S S TE E L410 - 416 S TAINLE S S S TE E L

DUC TILE IR ONDUC TILE IR ON 60,000

210 - 250210 - 250230 - 280230 - 280155 - 290155 - 290

132

1045 S TE E L1045 S TE E L 80,000 - 120,00080,000 - 120,000 160 - 240160 - 240316 S TAINLE S S S TE E L316 S TAINLE S S S TE E L 80,000 - 90,00080,000 - 90,000 150 - 190150 - 190304 S TAINLE S S S TE E L304 S TAINLE S S S TE E L 85,000 - 125,00085,000 - 125,000 212 - 277212 - 277MONE L 400MONE L 400 84,000 - 120,00084,000 - 120,000 160 - 225160 - 225K MONE LK MONE L 135,000 - 185,000135,000 - 185,000 255 - 370255 - 370

17-4 PH S TAINLE S S S TE E L17-4 PH S TAINLE S S S TE E L 145,000 - 200,000145,000 - 200,000 311 - 420311 - 420ALUMINUM BR ONZEALUMINUM BR ONZE 80,000 - 110,00080,000 - 110,000 150 - 250150 - 250S AE 40 BR ONZES AE 40 BR ONZE 26,000 - 42,00026,000 - 42,000 60 - 8060 - 80

NIC KE L ALUMINUM BR ONZENIC KE L ALUMINUM BR ONZE 85,000 159

The hardness and tens ile strength of many materials can be changed considerably by heat-treating or cold-working.The hardness and tens ile strength of many materials can be changed considerably by heat-treating or cold-working.An example of the latter is cold-drawn shafting which has harder and stronger metal near the surface of the shaftAn example of the latter is cold-drawn shafting which has harder and stronger metal near the surface of the shaftthan in the center.than in the center.It is difficult to obtain accurate hardness measurements of thin sections of materials such as coatings and overlaysIt is difficult to obtain accurate hardness measurements of thin sections of materials such as coatings and overlaysapplied over a softer material. The actual hardness is not of great importance in this instance as the wearapplied over a softer material. The actual hardness is not of great importance in this instance as the wearcharacteris tics of a material are more likely to be related to its "toughness" or the mating surface than to thecharacteris tics of a material are more likely to be related to its "toughness" or the mating surface than to thehardness . This is not to say that materials with low hardness ratings have excellent wear res is tance.hardness . This is not to say that materials with low hardness ratings have excellent wear res is tance.

(Typic a l)

Page 47Page 47

HARDNESS OF MATERIALHARDNESS OF MATERIAL

1. S peed too s low (check voltage.)1. S peed too s low (check voltage.)2. Impeller trimmed incorrectly.2. Impeller trimmed incorrectly.3. Impeller loose.3. Impeller loose.4. Impeller plugged.4. Impeller plugged.5. Wear rings worn.5. Wear rings worn.6. E ntrained air in pump.6. E ntrained air in pump.7. Leaking joints or bowl cas ings .7. Leaking joints or bowl cas ings .8. Wrong rotation.8. Wrong rotation.9. Incorrect impeller adjustment.9. Incorrect impeller adjustment.

INS UFF IC IE NT PR E S S UR EINS UFF IC IE NT PR E S S UR E

NO LIQUID DE LIVE R E DNO LIQUID DE LIVE R E D1. Pump suction broken (water level)1. Pump suction broken (water level)

below inlet.)2. S uction valve closed.2. S uction valve closed.3. Impeller plugged.3. Impeller plugged.4. S trainer clogged.4. S trainer clogged.5. Wrong rotation.5. Wrong rotation.6. S haft broken or unscrewed.6. S haft broken or unscrewed.7. Impeller loose.7. Impeller loose.8. Barrel or discharge not vented.8. Barrel or discharge not vented.9. Driver inoperative.9. Driver inoperative.

V IBR ATION1. Motor imbalance-electrical.1. Motor imbalance-electrical.2. Motor bearing not properly seated2. Motor bearing not properly seated

or worn.or worn.3. Motor drive coupling out of3. Motor drive coupling out of

balance or alignment.balance or alignment.4. Misalignment of pump, cas ings ,4. Misalignment of pump, cas ings ,

discharge head column, or bowls .discharge head column, or bowls .5. Discharge head misaligned by5. Discharge head misaligned by

improper mounting or pipe strain.improper mounting or pipe strain.6. Bent shafting.6. Bent shafting.7. Worn pump bearings .7. Worn pump bearings .8. C logged impeller or foreign8. C logged impeller or foreign

material in pump.material in pump.9. Improper impeller adjustment.9. Improper impeller adjustment.10. Vortex problems in sump.10. Vortex problems in sump.11. R easonance-system frequency at11. R easonance-system frequency at

or near pump speed.or near pump speed.12. C avitation.12. C avitation.13. Impeller out of balance.13. Impeller out of balance.

INS UFF IC IE NT C APAC ITYINS UFF IC IE NT C APAC ITY1. S peed too s low.1. S peed too s low.2. Impeller trimmed incorrectly.2. Impeller trimmed incorrectly.3. Impeller loose.3. Impeller loose.4. Impeller or bowl partially plugged.4. Impeller or bowl partially plugged.5. Leaking joints .5. Leaking joints .6. S trainer or suction pipe clogged.6. S trainer or suction pipe clogged.7. S uction valve throttled.7. S uction valve throttled.8. Low water level.8. Low water level.9. Wrong rotation.9. Wrong rotation.

10. Insufficient submergence.10. Insufficient submergence.11. Insufficient N.P.S .H.A.11. Insufficient N.P.S .H.A.12. Incorrect impeller adjustment.12. Incorrect impeller adjustment.13. Worn pump.13. Worn pump.14. S ystem pressure higher than14. S ystem pressure higher than

des ign.

1. S peed too high.1. S peed too high.2. Improper impeller adjustment.2. Improper impeller adjustment.3. Improper impeller trim.3. Improper impeller trim.4. Pump out of alignment.4. Pump out of alignment.5. C oupling out of alignment.5. C oupling out of alignment.6. Pumping sand, s ilt, or foreign6. Pumping sand, s ilt, or foreign

material.7. Lubricating oil too heavy.7. Lubricating oil too heavy.8. Bent shaft.8. Bent shaft.9. Tight bearing or packing.9. Tight bearing or packing.

10. S pecific gravity or viscos ity of10. S pecific gravity or viscos ity offluid higher than des ign.fluid higher than des ign.

11. Worn pump.11. Worn pump.12. Damaged pump.12. Damaged pump.13. Partial freezing of pump liquid.13. Partial freezing of pump liquid.

US ING TOO MUC H POWE RUS ING TOO MUC H POWE R

ABNOR MAL NOIS EABNOR MAL NOIS E1. Motor noise.1. Motor noise.2. Pump bearing running dry.2. Pump bearing running dry.3. B roken column bearing retainers .3. B roken column bearing retainers .4. B roken shaft or shaft enclos ing4. B roken shaft or shaft enclos ing

tube.5. Impellers dragging on bowl case.5. Impellers dragging on bowl case.6. C avitation due to insufficient6. C avitation due to insufficient

N.P.S .H.A. and/or submergence.N.P.S .H.A. and/or submergence.7. Foreign material in pump.7. Foreign material in pump.8. E xcess ive fluid velocity in pipe8. E xcess ive fluid velocity in pipe

system.

Page 48Page 48

TROUBLE SHOOTINGOPERATING SYMPTOMS

TROUBLE SHOOTINGOPERATING SYMPTOMS

TR OUBLE S OUR C ETR OUBLE S OUR C EBE AR INGS

PR OBABLE C AUS EPR OBABLE C AUS E R E ME DYC onsider converting to fresh water flushingC onsider converting to fresh water flushingon all bearings or pressure grease or oilon all bearings or pressure grease or oillubrication.

P remature bearing wearP remature bearing wear Abras ive actionAbras ive action

on shafton shaftBearing seized or gallingBearing seized or galling C heck lubrication, look for plugged suctionC heck lubrication, look for plugged suction

or evidence of flashing.or evidence of flashing.Bearing failure or bearingBearing failure or bearingseized

High temperature failure.High temperature failure.temperature limits .temperature limits .C heck pump manufacturer for bearingC heck pump manufacturer for bearing

R unning dry without lubrication.R unning dry without lubrication.

rubber bearingsrubber bearingsE xcess ive shaft wear underE xcess ive shaft wear under R ubber bearings will swell in hydro-carbon,R ubber bearings will swell in hydro-carbon,

H S & High temperature.H S & High temperature.2C hange bearing material.C hange bearing material.

C heck mounting & discharge pipeC heck mounting & discharge pipeconnection, dirt between column joints .connection, dirt between column joints .C orrect misalignment, replace bearings &C orrect misalignment, replace bearings &repair or replace shaft.repair or replace shaft.

Uneven wear on bearings ,Uneven wear on bearings ,uniform wear on shaft.uniform wear on shaft. misaligned.

Pump non-rotating partsPump non-rotating parts

R eplace parts , cons ider changing materialR eplace parts , cons ider changing materialor means of lubrication.or means of lubrication.

Abras ive action.Abras ive action.and shaftand shaftUniform wear on bearingUniform wear on bearing

1. S haft runnout caused by bent shafts ,1. S haft runnout caused by bent shafts ,shafts not butted in couplings , dirt orshafts not butted in couplings , dirt orgrease between shafts .grease between shafts .2. S haft ends not properly faced.2. S haft ends not properly faced.

Uniform wear on bearings ,Uniform wear on bearings ,uneven wear on shaftuneven wear on shaft

2. Face parallel & concentric.2. Face parallel & concentric.assemble correctly.assemble correctly.1. S traighten shaft or replace, clean &1. S traighten shaft or replace, clean &

Bent shaftBent shaftS HAFT AND C OUPLINGSS HAFT AND C OUPLINGS

Mishandling in trans it or assembly.Mishandling in trans it or assembly.total runout or replace.total runout or replace.C heck straightness . C orrect to 0.0005/ft.C heck straightness . C orrect to 0.0005/ft.

S haft coupling unscrewed.S haft coupling unscrewed.rotation.Pump started in reversePump started in reverse S hafts may be bent; check shafts &S hafts may be bent; check shafts &

couplings . C orrect rotation.couplings . C orrect rotation.

and Upthrusting.and Upthrusting.5. S ee S ections on Impeller Adjustment5. S ee S ections on Impeller Adjustmentcomponents to eliminate vibration.components to eliminate vibration.4. C heck alignment of pump4. C heck alignment of pump3. Add strainers or screens .3. Add strainers or screens .2. S ame as above for bearing seizure.2. S ame as above for bearing seizure.1. S ame as above.1. S ame as above.

impeller to drag.impeller to drag.continuous upthrust conditions , caus ingcontinuous upthrust conditions , caus ing5. Improper impeller adjustment or5. Improper impeller adjustment or4. Metal fatigue due to vibrations .4. Metal fatigue due to vibrations .or galling wear rings .or galling wear rings .3. Foreign material locking impellers3. Foreign material locking impellersseized due to lack of lubrication.seized due to lack of lubrication.2. C an also be caused by bearings2. C an also be caused by bearingslis ted for coupling elongation.lis ted for coupling elongation.1. C an be caused by same reasons1. C an be caused by same reasonsB roken shaft or coupling.B roken shaft or coupling.

4. C heck for galling on shaft ends .4. C heck for galling on shaft ends .3. R eplace couplings .3. R eplace couplings .2. R eplace couplings .2. R eplace couplings .improper starting timers .improper starting timers .also be momentary power failure oralso be momentary power failure or1. Look for faulty check valve. C ould1. Look for faulty check valve. C ould

are not butted in coupling.are not butted in coupling.4. Power being applied to shafts that4. Power being applied to shafts thatcouplings .3. P ipe wrench fatigue on reused3. P ipe wrench fatigue on reused2. C orros ion.running in reverse.running in reverse.1. Motor started while the pump was1. Motor started while the pump was

(neck down)(neck down)S haft coupling elongated.S haft coupling elongated.

INNE R C OLUMNINNE R C OLUMNWater in inner columnWater in inner column 1. Bypass ports plugged.1. Bypass ports plugged.

2. Badly worn bypass seal or bearings .2. Badly worn bypass seal or bearings .3. Tubing joint leaking.3. Tubing joint leaking.4. C rack or hole in tubing.4. C rack or hole in tubing.

1. R emove cause.1. R emove cause.2. R eplace worn parts .2. R eplace worn parts .3. E nsure tubing joint face is clean and3. E nsure tubing joint face is clean andbutted squarely.butted squarely.4. R eplace section affected.4. R eplace section affected.

Page 49Page 49

COMPONENT PROBLEMSOLVING


TR OUBLE S OUR C ETR OUBLE S OUR C EIMPE LLE R S

R eplace impeller if excess ive. C onsider coatingR eplace impeller if excess ive. C onsider coatingor upgrading material.or upgrading material.

Wear on exit vanes andWear on exit vanes andshrouds

Abras ive actionAbras ive action

of impellerof impellerP itting on entrance vanesP itting on entrance vanes C avitation: C orrect condition or upgrade material to extendC orrect condition or upgrade material to extend

P itting on impellers andP itting on impellers andbowl casting.bowl casting.

C orros ion/E ros ion.frequency of replacements .frequency of replacements .Investigate cost of different materials vs .Investigate cost of different materials vs .

1. Abras ive action or excess wear1. Abras ive action or excess wearallowing impeller skirts to function asallowing impeller skirts to function asbearing journal.bearing journal.2. Impellers set to high.2. Impellers set to high.

Wear on impeller skirtsWear on impeller skirtsand/or bowl seal ringand/or bowl seal ringarea.

1. Install new bearings and wear rings .1. Install new bearings and wear rings .Upgrade material if abras ive action.Upgrade material if abras ive action.2. R e-ring & adjust impellers correctly.2. R e-ring & adjust impellers correctly.

Impeller loose on shaftImpeller loose on shaft(extremely rare occurrence)(extremely rare occurrence)

1. R epeated shock load by surge in1. R epeated shock load by surge insuction or discharge line. (C ansuction or discharge line. (C anloosen firs t or last stage impellers .)loosen firs t or last stage impellers .)2. Foreign material jamming2. Foreign material jammingimpeller. (May break shaft or tripimpeller. (May break shaft or tripoverloads before impeller becomesoverloads before impeller becomesloose.)3. Differential expansion due to3. Differential expansion due totemperature.4. Parts improperly machined4. Parts improperly machinedand/or assembled.and/or assembled.5. Tors ion loading on submers ible5. Tors ion loading on submers iblepumps.

1. R e-fit impellers . If collet mounted, cons ider1. R e-fit impellers . If collet mounted, cons iderchanging to key mounting.changing to key mounting.2. R emove cause of jamming.2. R emove cause of jamming.3. If collet mounted, cons ider changing to key3. If collet mounted, cons ider changing to keymounted. Avoid sudden thermal shock.mounted. Avoid sudden thermal shock.4. C orrect parts if necessary and re-fit.4. C orrect parts if necessary and re-fit.5. Add keyway to collet mounting.5. Add keyway to collet mounting.

PR OBABLE C AUS EPR OBABLE C AUS E R E ME DY

E xcess ive leakageE xcess ive leakage 1. Improper packing procedure.1. Improper packing procedure.2. Incorrect type of defective2. Incorrect type of defectivepacking.

1. R epack correctly.1. R epack correctly.2. R epack with correct grade for service.2. R epack with correct grade for service.3. R emachine or replace scored parts .3. R emachine or replace scored parts .

5. R emove source of abras ives .5. R emove source of abras ives .4. R epack with correct grade for service.4. R epack with correct grade for service.3. R emachine or replace scored parts .3. R emachine or replace scored parts .2. R epack correctly.2. R epack correctly.1. R epack correctly.1. R epack correctly.

5. Abras ives in liquid.5. Abras ives in liquid.4. Incorrect type of packing.4. Incorrect type of packing.3. S haft or s leeve scored.3. S haft or s leeve scored.2. Insufficient lubrication.2. Insufficient lubrication.1. Improper packing procedure.1. Improper packing procedure.

4. R epack with correct grade for service.4. R epack with correct grade for service.3. R epack correctly.3. R epack correctly.2. R elease gland pressure.2. R elease gland pressure.1. R epack correctly.1. R epack correctly.

4. Incorrect type of packing.4. Incorrect type of packing.3. Insufficient lubrication.3. Insufficient lubrication.2. Packing too tight.2. Packing too tight.1. Improper packing procedure.1. Improper packing procedure.

BOWLS

Packing wears prematurelyPacking wears prematurely

Packing Housing overheatingPacking Housing overheatingPAC K ING HOUS INGPAC K ING HOUS ING

life.

3. Worn shaft or s leeve.3. Worn shaft or s leeve.

Wear on bowl vanesWear on bowl vanes Abras ive actionAbras ive action C oat bowls , upgrade materials , or rubber line.C oat bowls , upgrade materials , or rubber line.

Page 50Page 50



BUTT C OLUMNBUTT C OLUMN

TAPE R C OLUMNTAPE R C OLUMN

S HAFT PR OJE C T IONS HAFT PR OJE C T ION

S HAFT PR OJE C T IONS HAFT PR OJE C T IONC OLUMN MAKE -UPC OLUMN MAKE -UP

IN.IN.

IN.

(B )(C )

(B1)

DIA.S HAFT:

THR E AD LE NGTH.THR E AD LE NGTH.THR E ADS /IN.

MAKE -UP POINTMAKE -UP POINT

B1

C

B

FLANGE D C OLUMNFLANGE D C OLUMN

S HAFT PR OJE C T IONS HAFT PR OJE C T IONIN.(B )

DIA.S HAFT:


B

PUR C HAS E R

MODE L

L.H.

TAPE R OUTE R C OLUMNTAPE R OUTE R C OLUMN

3/16THR E ADS /IN.C OLUMN S IZEC OLUMN S IZE

TAPE R : 3/8 3/4

I.D. O.D. C OLUMN S IZEC OLUMN S IZETHR E ADS /IN.

BUTT JOINT THR E ADSBUTT JOINT THR E ADSI.D. O.D.

P.O. NUMBE RP.O. NUMBE R

Page 51Page 51

WATER LUBE BOWLREPLACEMENT

WATER LUBE BOWLREPLACEMENT

BUTT C OLUMNBUTT C OLUMN

TAPE R C OLUMN

TUBE PR OJE C T IONTUBE PR OJE C T IONS HAFT PR OJE C T IONS HAFT PR OJE C T ION

TUBE PR OJE C T IONTUBE PR OJE C T ION

C OLUMN MAKE -UPC OLUMN MAKE -UPS HAFT PR OJE C T IONS HAFT PR OJE C T ION

C OUPLING O.D.C OUPLING O.D.

A

O.D.I.D.BUTT JOINT THR E ADSBUTT JOINT THR E ADS

THR E ADS /IN.C OLUMN S IZEC OLUMN S IZEO.D.I.D.

3/43/8TAPE R :

C OLUMN S IZEC OLUMN S IZETHR E ADS /IN.

3/16

TAPE R OUTE R C OLUMNTAPE R OUTE R C OLUMN

LHR H

O.D.LINE S HAFT BE AR ING :LINE S HAFT BE AR ING :


IN.IN.

(B1)(A1)

MAKE -UP POINTMAKE -UP POINT

IN.

IN.IN.

(C )(B )(A)

THR E AD LE NGTH.THR E AD LE NGTH.THR E ADS /IN.DIA.

S HAFT:

B1

A1

B

C

FLANGE D C OLUMNFLANGE D C OLUMN

C OUPLING O.D.C OUPLING O.D.

A

LHR H

O.D.LINE S HAFT BE AR ING :LINE S HAFT BE AR ING :


THR E AD LE NGTH.THR E AD LE NGTH.THR E ADS /IN.DIA.

S HAFT:

B

PUR C HAS E R

MODE L

L.H.

P.O. NUMBE R

(A)(B )

IN.IN.S HAFT PR OJE C T IONS HAFT PR OJE C T ION

TUBE PR OJE C T IONTUBE PR OJE C T IONPR OJE C T ION

Page 52Page 52

OIL LUBE BOWLREPLACEMENTOIL LUBE BOWLREPLACEMENT

A gallon of water (U.S . S tandard) contains 231 cubic inches and weights approximatelyA gallon of water (U.S . S tandard) contains 231 cubic inches and weights approximately8 1/3 lbs .8 1/3 lbs .To find the pressure in pounds per square inch of a column of water, multiply theTo find the pressure in pounds per square inch of a column of water, multiply theheight of the column in feet by 0.434.height of the column in feet by 0.434.Doubling the diameter of a pipe increases its capacity four times .Doubling the diameter of a pipe increases its capacity four times .The weight of water (in pounds) in any length of pipe is obtained by multiplying theThe weight of water (in pounds) in any length of pipe is obtained by multiplying thelength in feet by the square of the diameter and by 0.34.length in feet by the square of the diameter and by 0.34.The capacity of a pipe in gallons is equal to the square of the diameter in inchesThe capacity of a pipe in gallons is equal to the square of the diameter in inchestimes the length times 0.0034.times the length times 0.0034.

DIAME TE R OF P IPEDIAME TE R OF P IPE(INC HE S ) GALLONS

NUMBE R OFNUMBE R OF WE IGHT(POUNDS )

2"4"6"8"

10"12"14"16"18"20"22"24"26"28"30"36"

0.16

52.9036.7032.0027.6023.5019.8016.3013.2010.508.005.904.102.601.500.65

1.3355.421

12.51021.68434.19449.20666.7287.57110.08135.94165.13195.99230.18266.88306.07441.18

NOTE S :

Page 53Page 53

CAPACITY OF PIPE FORWATER PER FOOT

CAPACITY OF PIPE FORWATER PER FOOT

Motor R atingMotor R atingVolts HP

1/2

14

130 210

12

340

10

540

8

840

6

1300

4

1610

3

1960

2

2390

1

2910

0

3540

00

4210

000 0000

50603/4 37703140263021601780146011909606203902501601001 6520536044103610296023801540990630400250

1 1/21 1/2 52404280350028502320187012007704803101902 4480362029302360191015309706203902501503 361028902320185014901190750470300190120*5 26802170174013901110890710450280180*00

7 1/27 1/2 172014101140930750610490310200*00010 176014301160930750600490390250*000015 12601020820660530430340270*170*0000

S ingle Phase C able, 60 HZ (S ervice E ntrance to Motor - Maximum Length in Feet)S ingle Phase C able, 60 HZ (S ervice E ntrance to Motor - Maximum Length in Feet)Maximum Feet of AWG C opper Wire S izeMaximum Feet of AWG C opper Wire S ize

Two or Three Wire C able, 60 HZTwo or Three Wire C able, 60 HZ

230VS ingle PhaseS ingle Phase

Lengths without the asterisk* meet the U. S . NationalLengths without the asterisk* meet the U. S . NationalE lectrical C ode ampacity for either individual conductors orE lectrical C ode ampacity for either individual conductors orjacketed 60° C cable.jacketed 60° C cable.

Lengths marked* meet the NE C ampacity only for individualLengths marked* meet the NE C ampacity only for individualconductor 60° C cable in free air or water, not in conduit. Ifconductor 60° C cable in free air or water, not in conduit. Ifcable rated other than 60° cable is used, lengths remaincable rated other than 60° cable is used, lengths remainunchanged, but the minimum size acceptable for each ratingunchanged, but the minimum size acceptable for each ratingmust be based on the NE C table column for that temperaturemust be based on the NE C table column for that temperaturecable.

F lat molded cable is cons idered jacketed cable.F lat molded cable is cons idered jacketed cable.Maximum lengths shown maintain motor voltage at 95% ofMaximum lengths shown maintain motor voltage at 95% of

service entrance voltage, running at maximum nameplateservice entrance voltage, running at maximum nameplateamperes . If service entrance voltage will be at least motoramperes . If service entrance voltage will be at least motor

nameplate voltage under normal load conditions , 50% additionalnameplate voltage under normal load conditions , 50% additionallength is permiss ible for all s izes .length is permiss ible for all s izes .

This table is based on copper wire. If aluminum wire is toThis table is based on copper wire. If aluminum wire is tobe used; it must be two sizes larger. E xample: If the tablebe used; it must be two sizes larger. E xample: If the tablecalls for #12 copper wire, #10 aluminum wire would be required.calls for #12 copper wire, #10 aluminum wire would be required.

The portion of the total cable length which is between theThe portion of the total cable length which is between thesupply and single phase control box with line contractor shouldsupply and single phase control box with line contractor shouldnot exceed 25% of the maximum allowable, to ensure reliablenot exceed 25% of the maximum allowable, to ensure reliablecontactor operation. S ingle-phase control boxes without linecontactor operation. S ingle-phase control boxes without linecontactors may be connected at any point in the total cablecontactors may be connected at any point in the total cablelength.

Lengths represent a 5% voltage drop. If 3% is required,Lengths represent a 5% voltage drop. If 3% is required,multiply by 0.6 for maximum feet.multiply by 0.6 for maximum feet.

AWG C opper Wire S izeAWG C opper Wire S izeThree Phase C able, 60 HZ (S ervice E ntrance to Motor - Maximum Length in Feet)Three Phase C able, 60 HZ (S ervice E ntrance to Motor - Maximum Length in Feet)

0 0 0 0 0 260* 330* 410* 510 620 760 930 1130300 0 0 0 0 320* 400 500 610 750 920 1120 1360250 0 0 0 250* 400 500 610 760 930 1140 1380200 0 0 210* 330 520 650 800 980 1200 1470 1780150 0 190* 310 490 760 950 1170 1440 1760 2160100 160* 260 420 650 1020 1270 1560 1920 2340 28707 1/27 1/2

140 230 370 590 920 1430 1790 2190 2690 3290 40305240 390 620 990 1540 2400 2980 3660 4480 5470 66903320 510 810 1280 2010 3130 3890 4770 5860 7170 8780 0 02

00000000

0000

09170

17530

26160

35030

44050

62610

81670

101060

12670420

141 1/21 1/2HPVolts

Motor R atingMotor R ating

9680802058704850416034403160261021501680

230V60 HZ60 HZ

Three PhaseThree PhaseThree WireThree Wire

32904500

4470 543055307110

35

1000590 950

160015002520

23603970

37006200

57507 1/27 1/2 768062605100410026401690107068042010 705057504680380030501960125079050031015 5900481039303200260020901340850540340*020 4580373030402470200016101030650410*25 370030102450199016201300830530*30 3700306024902030164013301070680430*40 27102250183014901210980790500*50 26502190181014801210980800640*60 2240185015012501020830*670*540*

0 680* 840* 1030 1260 1520 185075620* 760* 940* 1130 1380100

740* 890* 1000*125760 920*150

0 810*1750 0200

460 V460 V60 HZ60 HZ

Three PhaseThree PhaseThree WireThree Wire

67304270271017001 1/21 1/22 1300 2070 3270 5150 8050

000000000000 0

00000000000

00000000000 0

00000000

00000000 0

00000

00000 0

0000

0000 0

000

000

Page 54Page 54

CABLE SELECTION FOR SINGLEAND THREE PHASE MOTORS

CABLE SELECTION FOR SINGLEAND THREE PHASE MOTORS

To calculate the flow required to keep a submers ible motor cool, use the following formula:To calculate the flow required to keep a submers ible motor cool, use the following formula:

V =FGPM x 0.408

(W ) - (M )(W ) - (M )ID2

OD2

WHE R E : FV = VE LOC ITY FLOWV = VE LOC ITY FLOW

GPM = GALLONS PE R MINUTEGPM = GALLONS PE R MINUTE

W = WE LL C AS ING INS IDE DIAME TE RW = WE LL C AS ING INS IDE DIAME TE RIDM = MOTOR OUTS IDE DIAME TE RM = MOTOR OUTS IDE DIAME TE ROD

At a maximum temperature of 86°F (30°C ) the minimum Velocity F low past motor would be:At a maximum temperature of 86°F (30°C ) the minimum Velocity F low past motor would be:

0.25 ft/sec (7.62 C M/sec) - 4" diameter motor0.25 ft/sec (7.62 C M/sec) - 4" diameter motor

0.50 ft/sec (15.24 C M/sec) - 6" diameter and larger motor)0.50 ft/sec (15.24 C M/sec) - 6" diameter and larger motor)

If the flow past the motor is less than the minimum velocity, the motor needs to be installedIf the flow past the motor is less than the minimum velocity, the motor needs to be installedin a flow sleeve.in a flow sleeve.When the water temperature is greater than 86°F (30°C ) the flow rate past the motor should notWhen the water temperature is greater than 86°F (30°C ) the flow rate past the motor should notbe less than 3.0 ft/sec.be less than 3.0 ft/sec.

To calculate Horsepower required at temperature greater than 86°F (30°C ):To calculate Horsepower required at temperature greater than 86°F (30°C ):

H = P x HFH = P x HFPR HP

HF = HE AT FAC TOR MULTIPLIE R AT 3 ft/sec FLOWHF = HE AT FAC TOR MULTIPLIE R AT 3 ft/sec FLOW

P = PUMP HOR S E POWE R AT DE S IGNP = PUMP HOR S E POWE R AT DE S IGN

H = HOR S E POWE R R E QUIR E DH = HOR S E POWE R R E QUIR E DWHE R E : PR

HP

Heat Factor Multiplier at 3 ft/sec flowHeat Factor Multiplier at 3 ft/sec flow

(The above chart is for can type submers ible motor, for water proof wire type consult factory.)(The above chart is for can type submers ible motor, for water proof wire type consult factory.)NOTE :

MAXIMUM WATE R TE MPE R ATUR EMAXIMUM WATE R TE MPE R ATUR E

140°F (60°C )

131°F (55°C )

122°F (50°C )

113°F (45°C )

104°F (40°C )

95°F (35°C )

up to 5 H.P.

1.25

1.11

1.00

1.00

1.00

1.00 1.00

1.00

1.00

1.14

1.32

1.62

up to 30 H.P. over 30 H.P.over 30 H.P.

2.00

1.62

1.32

1.14

1.00

1.00

Page 55

SUBMERSIBLE MOTORFLOW RATE

SUBMERSIBLE MOTORFLOW RATE

S elect firs t correct cable copper cross-section based on motor rating and length required.S elect firs t correct cable copper cross-section based on motor rating and length required.

600V TAPE S PLIC ING600V TAPE S PLIC INGA) S trip individual conductor of insulation only as for as necessary to provide room for a stake type connector.A) S trip individual conductor of insulation only as for as necessary to provide room for a stake type connector.

Tubular connectors of the staked type are preferred. If the connector O.D. is not as large as the cableTubular connectors of the staked type are preferred. If the connector O.D. is not as large as the cableinsulation,

build-up with rubber electrical tape.build-up with rubber electrical tape.B ) Tape the individual joints with rubber electrical tape, us ing two layers : the firs t extending two inches beyondB ) Tape the individual joints with rubber electrical tape, us ing two layers : the firs t extending two inches beyondeach

end of the conductor insulation end, the second layer two inches beyond the ends of the firs t layer. Wrapend of the conductor insulation end, the second layer two inches beyond the ends of the firs t layer. Wraptightly, eliminating air spaces as much as poss ible.tightly, eliminating air spaces as much as poss ible.

C ) Tape over the rubber electrical tape with #33 S cotch electrical tape, (Minnesota Mining C o.) or equivalent,C ) Tape over the rubber electrical tape with #33 S cotch electrical tape, (Minnesota Mining C o.) or equivalent,us ing

two layers as in step "B " and making each layer overlap the end of the preceding layer by at least two inches .two layers as in step "B " and making each layer overlap the end of the preceding layer by at least two inches .

In the case of a cable with three conductors encased in a s ingle outer sheath, tape the individual conductors asIn the case of a cable with three conductors encased in a s ingle outer sheath, tape the individual conductors asdescribed,staggering joints .s taggering joints .Total thickness of tape should be no less than the thickness of the conductor insulation.Total thickness of tape should be no less than the thickness of the conductor insulation.

S TAC KE D C ONNE C TORS TAC KE D C ONNE C TOR

R UBBE R TAPE (step B )R UBBE R TAPE (step B )

2" 2"

2"2"

PVC E LE C TR IC AL TAPEPVC E LE C TR IC AL TAPE(step C )(step C )

NOTE S :

Page 56Page 56

CABLE SPLICING

AATTE NTION

ATTE NTIONIn case of splicing cables of a s ix-lead motor for Y start, be sure that the extens ion cables continue with theIn case of splicing cables of a s ix-lead motor for Y start, be sure that the extens ion cables continue with thesamelead colors and phase des ignation as the original motor cables . This will ease up above ground connections to the Ylead colors and phase des ignation as the original motor cables . This will ease up above ground connections to the Ypanel or an external connection for DOL start.panel or an external connection for DOL start.

ATTE NTIONLoose wire connections can cause the burn out of the splice and short circuit, leading to poss ible motor failure.Loose wire connections can cause the burn out of the splice and short circuit, leading to poss ible motor failure.

INS ULATION R E S IS TANC E R E ADINGSINS ULATION R E S IS TANC E R E ADINGSNOR MAL OHM AND ME GOHM VALUE S BE TWE E N ALL LE ADS AND GR OUNDNOR MAL OHM AND ME GOHM VALUE S BE TWE E N ALL LE ADS AND GR OUNDInsulation res istance varies little with rating. Motors of all H.P., voltage, and phase rating have s imilar valuesInsulation res istance varies little with rating. Motors of all H.P., voltage, and phase rating have s imilar valuesofinsulation.

C ONDIT ION OF MOTOR AND LE ADSC ONDIT ION OF MOTOR AND LE ADS OHM VALUEOHM VALUE ME GOHM VALUEME GOHM VALUE20,000,000 (or more)20,000,000 (or more) >20.0A new motor (without drop cable)A new motor (without drop cable)

A used motor which can be reinstalled in the wellA used motor which can be reinstalled in the well 10,000,000 (or more)10,000,000 (or more) >10.0

A new motor in the well.A new motor in the well. 2,000,000 (or more)2,000,000 (or more) >2.0A motor in the well in reasonably good conditionA motor in the well in reasonably good condition 500,000-2,000,000 0.5-2.0A motor which may have been damaged by lightning or which mayA motor which may have been damaged by lightning or which may 20,000-500,000 0.02-0.5have damaged leads . Do not pull the pump for this reason.have damaged leads . Do not pull the pump for this reason.A motor which definitely has been damaged or with damaged cable.A motor which definitely has been damaged or with damaged cable.The pump should be pulled and repairs made to the cable or theThe pump should be pulled and repairs made to the cable or the

10,000-20,000 0.01-0.02

motor replaced. The motor will not fail for this reason alone, but itmotor replaced. The motor will not fail for this reason alone, but itwill probably not operate for long.will probably not operate for long.A motor which has failed or with completely destroyed cable insulation.A motor which has failed or with completely destroyed cable insulation.The pump must be pulled and the cable repaired or the motorThe pump must be pulled and the cable repaired or the motor

less than 10,000less than 10,000 0-0.01

replaced.

The key factor of success is to follow exactly the manufacturer's application instructions for the splicing kits . TheThe key factor of success is to follow exactly the manufacturer's application instructions for the splicing kits . Thebas is for a good splice is the connection of the copper wires for which we recommend the use of crimping connectorsbas is for a good splice is the connection of the copper wires for which we recommend the use of crimping connectorsavailable for almost any common wire s ize.available for almost any common wire s ize.

S pecial attention should be given that the crimp connectors match the wire s izes used in order to get an electricallyS pecial attention should be given that the crimp connectors match the wire s izes used in order to get an electricallylow res istance joint.low res istance joint.

ME GOHM VALUEME GOHM VALUEOHM VALUEOHM VALUEMOTOR IN WE LL. Ohm readings are for drop cable plus motor.MOTOR IN WE LL. Ohm readings are for drop cable plus motor.

Page 57Page 57

CABLE SPLICING

C urrent unbalance, particularly in rural areas with heavy s ingle-C urrent unbalance, particularly in rural areas with heavy s ingle-phase loads , can cause premature motor failure - a result ofphase loads , can cause premature motor failure - a result ofreduced starting and breakdown torque, excess ive and unevenreduced starting and breakdown torque, excess ive and unevenheating, and excess ive vibration.heating, and excess ive vibration.It is important that the electrical load to the submers ible motor beIt is important that the electrical load to the submers ible motor bereasonable balanced. It is also important that the installation bereasonable balanced. It is also important that the installation bemade properly. Here's how to make a proper electrical installationmade properly. Here's how to make a proper electrical installationand what to do if you can't.and what to do if you can't.

P rior to installation, the power company should be notified ofP rior to installation, the power company should be notified ofthe motor data, plus other loads that are on the transformer bank.the motor data, plus other loads that are on the transformer bank.

You should know if the service provided is a true three-phase,You should know if the service provided is a true three-phase,three transformer system or a two transformer system. This canthree transformer system or a two transformer system. This canbe determined by counting the transformers if the service is in, orbe determined by counting the transformers if the service is in, orby questioning the power company if service is not yet in. Here isby questioning the power company if service is not yet in. Here isan open-delta or wye system (on the left), with a true three-phase,an open-delta or wye system (on the left), with a true three-phase,three transformer system (on the right).three transformer system (on the right).

Make sure that the transformer rating, in KVA, is adequate forMake sure that the transformer rating, in KVA, is adequate forthe motor load by referring to this chart which references the KVAthe motor load by referring to this chart which references the KVArequirement by horsepower. Note that the minimum KVA rating,requirement by horsepower. Note that the minimum KVA rating,at the right on the chart, refers to "each" transformer used. Thisat the right on the chart, refers to "each" transformer used. Thischart, incidentally, covers only the motor KVA requirements andchart, incidentally, covers only the motor KVA requirements anddoes not make allowances for other loads .does not make allowances for other loads .

S UBME R S IBLE3" DIA MOTORH.P. R AT INGH.P. R AT ING

TOTAL E FFE C T IVETOTAL E FFE C T IVEKVA R E QUIR E DKVA R E QUIR E D

S MALLE S T KVA R ATINGS MALLE S T KVA R ATING"E AC H TR ANS FOR ME R ""E AC H TR ANS FOR ME R "

OPE N WYE OROPE N WYE ORDE LTA

2 TR ANS FOR ME R SWYE OR DE LTAWYE OR DE LTA

3 TR ANS FOR ME R S3 TR ANS FOR ME R S

S TE P 1

1 1/21 1/2

2

3

5

7 1/27 1/2

10

15

20

25

30

40

50 65

53

40

32

27

20

15

12

7 1/27 1/2

5

4

3 2

2

3

5

7 1/27 1/2

10

15

15

20

25

30

37 1/237 1/2 25

20

15

10

10

7 1/27 1/2

5

5

3

2

1 1/21 1/2

1

S elect the proper s ize magnetic starter or pump panelS elect the proper s ize magnetic starter or pump panelfor the H.P. rating of the motor.for the H.P. rating of the motor.Use ambient compensated extra quick trip heaters on allUse ambient compensated extra quick trip heaters on allthree legs . The recommended heater s ize for the make ofthree legs . The recommended heater s ize for the make ofpanel is provided with the motor.panel is provided with the motor.

Manufacturer's recommended cable s ize must be followedManufacturer's recommended cable s ize must be followedfrom the transformer to the pump panel and from the panelfrom the transformer to the pump panel and from the panelto the motor, based on H.P. and voltage rating. Make sureto the motor, based on H.P. and voltage rating. Make surethat the length of cable in each case is no longer than thethat the length of cable in each case is no longer than themanufacturer's recommendation for that s ize of cable.manufacturer's recommendation for that s ize of cable.

If the pump is to operate properly on a system with twoIf the pump is to operate properly on a system with twotransformers , it is good practice to use both the next highertransformers , it is good practice to use both the next higherH.P. motor rating and the nest larger cable s ize. TakingH.P. motor rating and the nest larger cable s ize. Takingthese steps gives a greater margin of safety and providesthese steps gives a greater margin of safety and providesmore tolerance to current unbalance.more tolerance to current unbalance.

S TE P 2S TE P 2

S TE P 3S TE P 3

While the pump is still above ground check the insulationWhile the pump is still above ground check the insulationres istance of the motor to make sure that it is at least twores istance of the motor to make sure that it is at least twomillion or more ohms (two megohms).million or more ohms (two megohms).

After the drop cable has been spliced to the motor leadsAfter the drop cable has been spliced to the motor leadsand the pump is installed in the well, check the insulationand the pump is installed in the well, check the insulationres istance again to determine if your splice and cable areres is tance again to determine if your splice and cable aregood.

If insulation res istance is still one million ohms or more,If insulation res istance is still one million ohms or more,voltage can be applied to the motor.voltage can be applied to the motor.

Whatever you do, remember "S AFE TY F IR S T !" BeforeWhatever you do, remember "S AFE TY F IR S T !" Beforeworking ins ide the pump panel or magnetic starter, alwaysworking ins ide the pump panel or magnetic starter, alwaysdisconnect the line to the panel or starter. Be sure it is off.disconnect the line to the panel or starter. Be sure it is off.Double-check this with a voltmeter.Double-check this with a voltmeter.

C heck for correct rotation of the motor by running itC heck for correct rotation of the motor by running itfirs t in one direction and then the other. Use a dischargefirs t in one direction and then the other. Use a dischargevalve and pressure gage. The rotation that gives thevalve and pressure gage. The rotation that gives thehighest pressure is always the correct one.highest pressure is always the correct one.

R otation can be changed by switching any two of theR otation can be changed by switching any two of thethree motor leads at the pump panel.three motor leads at the pump panel.

Now that correct rotation is established, the amount ofNow that correct rotation is established, the amount ofcurrent unbalance between legs should be calculated.current unbalance between legs should be calculated.C UR R E NT UNBALANC E BE TWE E N LE GS S HOULD NOTE XC E E DC UR R E NT UNBALANC E BE TWE E N LE GS S HOULD NOTE XC E E D 5% OF THE AVE R AGE .5% OF THE AVE R AGE .

The percent of current unbalance is defined and calculatedThe percent of current unbalance is defined and calculatedas follows:

Percent current unbalance =Percent current unbalance =maximum current difference from average currentmaximum current difference from average current

average currentaverage current x 100x 100

C urrent readings in amps should be checked on each legC urrent readings in amps should be checked on each legusing the three poss ible hookups shown in the illustration.us ing the three poss ible hookups shown in the illustration.The best hookup is the one that has the lowest percentageThe best hookup is the one that has the lowest percentageof unbalance.

To prevent changing motor rotation when taking theseTo prevent changing motor rotation when taking thesereadings , the motor leads should be rolled across the starterreadings , the motor leads should be rolled across the starterterminals by always moving them in the same direction asterminals by always moving them in the same direction asshown in the illustration. (0n next page).shown in the illustration. (0n next page).

PR E -INS TALLATION

OPE N DE LTA OR WYEOPE N DE LTA OR WYE TR UE THR E E PHAS ETR UE THR E E PHAS E

S YS TE M R E QUIR E ME NTSS YS TE M R E QUIR E ME NTS

S TAR T UPS TAR T UP

Page 58Page 58

DEALING WITH THREEPHASE UNBALANCE


1st Hookup1st HookupL1 2L L3

T2

1T T3 2TT3

1T

3LL21L2nd Hookup2nd Hookup 3rd Hookup

L1 2L L3

T3

2T T1

S UPPLY

S TAR TE R

MOTOR

Use s imple arithmetic to calculate the percentage of current unbalance for all three hookups .Use s imple arithmetic to calculate the percentage of current unbalance for all three hookups .Here is an example of current readings at maximum pump loads on each leg of a three-wire hookup.Here is an example of current readings at maximum pump loads on each leg of a three-wire hookup.To start with, add up all three readings for hookup number 1.To start with, add up all three readings for hookup number 1.

Hookup 1Hookup 1

T = 51 AmpsT = 51 AmpsT = 46 AmpsT = 46 AmpsT = 53 AmpsT = 53 Amps

123 2

13


Hookup 2Hookup 2 Hookup 3Hookup 3


231

T = 53 AmpsT = 53 Amps

T = 46 Amps

T = 51 AmpsT = 51 AmpsTotal for each of the three hookups are as follows:Total for each of the three hookups are as follows:

1

2

3TOTAL 150 AmpsTOTAL 150 Amps

150 Amps - 3 = 50 Amps150 Amps - 3 = 50 AmpsDivide the total by three to obtain the average.Divide the total by three to obtain the average.

C alculate the greatest amp difference from the average.C alculate the greatest amp difference from the average.50 Amps50 Amps

-46 Amps4 Amps4 Amps

Divide this difference by the average to obtain theDivide this difference by the average to obtain thepercentage of unbalance.percentage of unbalance.

4.00 Amps - 50 = 0.08 or 8%4.00 Amps - 50 = 0.08 or 8%

In this case, the current unbalance for hookup numberIn this case, the current unbalance for hookup number1 is 8%.1 is 8%.If you use the same method of calculation, the maximumIf you use the same method of calculation, the maximumcurrent unbalance for hookup number 2 is 4% and forcurrent unbalance for hookup number 2 is 4% and forhookup number 3 is 2%.hookup number 3 is 2%.Next, compare the percentage of unbalance for all threeNext, compare the percentage of unbalance for all threehookups . The firs t hookup exceeds 5% current unbalancehookups . The firs t hookup exceeds 5% current unbalanceand should not be used. The second and third hookupsand should not be used. The second and third hookupsdid not exceed 5%, so either would be satis factory.did not exceed 5%, so either would be satis factory.However, the third hokup had the lowest percentage ofHowever, the third hokup had the lowest percentage ofcurrent unmbalance and it should be used, s ince thecurrent unmbalance and it should be used, s ince themotor will then be operating at maximum efficiency andmotor will then be operating at maximum efficiency andreliability.

By observing where the highest current reading is for each legBy observing where the highest current reading is for each legon the various hookups , you can now determine if the unbalanceon the various hookups , you can now determine if the unbalanceis caused by the power source or the electric motor. For example,is caused by the power source or the electric motor. For example,note in the example that the highest leg was always on the samenote in the example that the highest leg was always on the sameleg, L ; this indicates that most of the unbalance was from theleg, L ; this indicates that most of the unbalance was from thepower source.

If the high current were on a different leg each time the motorIf the high current were on a different leg each time the motorleads were changed, you would know that the motor or a poorleads were changed, you would know that the motor or a poorconnection caused most of the unbalance.connection caused most of the unbalance.

S ince loads on a transformer bank may vary during the day,S ince loads on a transformer bank may vary during the day,readings should be taken at least twice - once during the day inreadings should be taken at least twice - once during the day inwhat would be considered the normal load period and once in thewhat would be considered the normal load period and once in theevening during the usual peak load period. The installation shouldevening during the usual peak load period. The installation shouldthen be connected for the lowest percentage of current unbalancethen be connected for the lowest percentage of current unbalance(again, not to exceed 5%.)(again, not to exceed 5%.)

S hould you continue to have problems with balance or if youS hould you continue to have problems with balance or if youencounter heater trip problems. contact your power company forencounter heater trip problems. contact your power company forhelp.

S o you can fully explain the s ituation to the power use engineer,S o you can fully explain the s ituation to the power use engineer,or to your pump supplier, keep a complete log of your pumpor to your pump supplier, keep a complete log of your pumpinstallation.

You should keep a record of:You should keep a record of:Well location and ownerWell location and ownerDepth to waterDepth to waterHorsepowerMotor makeMotor makeS ize of control panelS ize of control panelHeaters usedHeaters usedC able s izes and lengthsC able s izes and lengthsC urrent and voltage readings , by legC urrent and voltage readings , by legWith this type of log, you will be on solid ground when youWith this type of log, you will be on solid ground when you

discuss the current unbalance problem with your power company.discuss the current unbalance problem with your power company.You can show what you did and why. This will help pinpoint theYou can show what you did and why. This will help pinpoint theproblem.

3

Pa ge 59Pa ge 59



PR OBLE M: MOTOR DOE S NOT S TAR TPR OBLE M: MOTOR DOE S NOT S TAR TC AUS E OF TR OUBLEC AUS E OF TR OUBLE C HE C K ING PR OC E DUR EC HE C K ING PR OC E DUR E R E ME DY

No power or incorrect voltage.No power or incorrect voltage. Us ing voltmeter check the line terminals .Us ing voltmeter check the line terminals .Voltage must be 10% of rated voltage.Voltage must be 10% of rated voltage.+-

C ontact power company if voltage isC ontact power company if voltage isincorrect.

Fuses blown or circuit breakersFuses blown or circuit breakerstripped.

C heck fuses for recommended size andC heck fuses for recommended size andcheck for loose, dirty or corrodedcheck for loose, dirty or corroded breaker.

R eplace with proper fuse or reset circuitR eplace with proper fuse or reset circuit

connections in fuse receptacle. C heckconnections in fuse receptacle. C heckfor tripped circuit breaker. Look forfor tripped circuit breaker. Look for

Defective pressure switch.Defective pressure switch. C heck voltage at contact points .C heck voltage at contact points .Improper contact of switch points canImproper contact of switch points cancause voltage less than line voltage.cause voltage less than line voltage.

R eplace pressure switch or clean points .R eplace pressure switch or clean points .

C ontrol panel malfunction.C ontrol panel malfunction.manufacturers instructions .manufacturers instructions .For detailed procedure, see panelFor detailed procedure, see panel

Defective wiring.Defective wiring.

voltmeter for power.voltmeter for power.C heck the motor lead terminals with aC heck the motor lead terminals with aC heck for loose or corroded connections .C heck for loose or corroded connections . C orrect faulty wiring or connections .C orrect faulty wiring or connections .

Bound pump.Bound pump. Locked rotor conditions can result fromLocked rotor conditions can result frommisalignment between pump and motormisalignment between pump and motoror sand bound pump. Amp readings 3or sand bound pump. Amp readings 3to 6 times higher than normal will beto 6 times higher than normal will be

S and bound pumps can sometimes beS and bound pumps can sometimes becorrected by temporarily revers ing anycorrected by temporarily revers ing any

indicated. Well may be crooked.indicated. Well may be crooked.

two leads in the control panel. If pumptwo leads in the control panel. If pumpdoes not rotate freely, it must be pulled.does not rotate freely, it must be pulled.

Defective cable or motor.Defective cable or motor. C heck insulation res istance.C heck insulation res istance. R epair or replace.R epair or replace.

C heck system for leaks .C heck system for leaks .Leak in system.Leak in system.

C lean or replace. Drain and rechargeC lean or replace. Drain and rechargefor proper operation.for proper operation.C heck air volume control or snifter valveC heck air volume control or snifter valveWaterlogged tank (air supply)Waterlogged tank (air supply)

R eplace if defective.R eplace if defective.not hold pressure.not hold pressure.Damaged or defective check valve willDamaged or defective check valve willC heck valve, stuck open.C heck valve, stuck open.

R eset limit or replace switch.R eset limit or replace switch.examine for defects .examine for defects .C heck setting on pressure switch andC heck setting on pressure switch andP ressure switch.P ressure switch.

R E ME DYC HE C K ING PR OC E DUR EC HE C K ING PR OC E DUR EC AUS E OF TR OUBLEC AUS E OF TR OUBLE

PR OBLE M: MOTOR S TAR TS TOO OFTE NPR OBLE M: MOTOR S TAR TS TOO OFTE N

tank.R eplace damaged pipes or repair leaks .R eplace damaged pipes or repair leaks .

manufacturers instructions .manufacturers instructions .

-+

R epair or replace pump and/or motor.R epair or replace pump and/or motor.C heck running current.C heck running current.Worn pump or motor.Worn pump or motor.C heck insulation res istance.C heck insulation res istance.Defective cable or motor.Defective cable or motor.

For detailed procedure, see panelFor detailed procedure, see panelC ontrol panel malfunction.C ontrol panel malfunction.to touch.to touch.to trip. The box must not be too hotto trip. The box must not be too hot

S hade box, provide ventilation or moveS hade box, provide ventilation or movebox away from heat source.box away from heat source.make control box hot caus ing protectorsmake control box hot caus ing protectors

Direct sunlight or other heat source canDirect sunlight or other heat source canOverheated protectors .Overheated protectors .incorrect.C ontact power company if voltage isC ontact power company if voltage is

Voltage must be 10% of rated voltage.Voltage must be 10% of rated voltage.Us ing voltmeter check the line terminals .Us ing voltmeter check the line terminals .Incorrect voltage.Incorrect voltage.


PR OBLE M: MOTOR R UNS BUT OVE R LOAD PR OTE C TOR TR IPSPR OBLE M: MOTOR R UNS BUT OVE R LOAD PR OTE C TOR TR IPS

R epair or replace.R epair or replace.

damage from heat, lightning or surge.damage from heat, lightning or surge.

C heck for waterlogged tank or defectiveC heck for waterlogged tank or defectivepressure switch.pressure switch.

Water system malfunction.Water system malfunction.

Pump load too great.Pump load too great. Incorrect pump for motor.Incorrect pump for motor.Operating too far out on curve.Operating too far out on curve.R otation backwards .R otation backwards .

R epair or replace.R epair or replace.

Page 60Page 60

COMPONENT PROBLEM SOLVINGSUBMERSIBLE PUMP AND MOTORCOMPONENT PROBLEM SOLVINGSUBMERSIBLE PUMP AND MOTOR

R eplace if defective.R eplace if defective.No water will be delivered if check valveNo water will be delivered if check valveC heck valve stuck closed.C heck valve stuck closed.

It may be necessary to clean well.It may be necessary to clean well.C lean screen and reset at less depth.C lean screen and reset at less depth.

installed in mud or sand.installed in mud or sand.intake screen on pump. Pump may beintake screen on pump. Pump may beR estricted flow may indicate a cloggedR estricted flow may indicate a cloggedPump screen blocked.Pump screen blocked.

C heck for damaged shafts if couplingC heck for damaged shafts if couplingNo or little water will be delivered ifNo or little water will be delivered ifcoupling between motor and pump shaftcoupling between motor and pump shaftis loose or if a jammed pump hasis loose or if a jammed pump has

Loose or broken motorLoose or broken motor

S ymptoms of worn pump are s imilar toS ymptoms of worn pump are s imilar tothose of drop pipe leak or low waterthose of drop pipe leak or low water

Worn Pump.Worn Pump.R eplace damaged pipes or repair leaks .R eplace damaged pipes or repair leaks .C heck system for leaks .C heck system for leaks .Leak in system.Leak in system.

from well head.from well head.C heck static and draw-down levelsC heck static and draw-down levels

Throttle back pump output or resetThrottle back pump output or resetpump at a lower level. Do not lower ifpump at a lower level. Do not lower ifoff pump, wait for well to recover.off pump, wait for well to recover.

Pump may exceed well capacity. S hutPump may exceed well capacity. S hutLow level well.Low level well.

readjust setting.readjust setting.C lean points or replace switch, orC lean points or replace switch, or

pos ition. P ressure switch may be setpos ition. P ressure switch may be setS witch points may be "welded" in closedS witch points may be "welded" in closedP ressure switch.P ressure switch.


PR OBLE M: MOTOR R UNS C ONTINUOUS LYPR OBLE M: MOTOR R UNS C ONTINUOUS LY

too high.too high.

sand may clog pump.sand may clog pump.

level in well. R educe pressure switchlevel in well. R educe pressure switchsetting, if pump shuts off, worn partssetting, if pump shuts off, worn partsmay be at fault. S and is usuallymay be at fault. S and is usuallypresent in tank.present in tank.

Pull pump and replace worn impellers ,Pull pump and replace worn impellers ,

shaft.

caused the motor shaft to shear off.caused the motor shaft to shear off.

is loose and replace worn or defectiveis loose and replace worn or defectiveunits .

is in closed position.is in closed position.C ontrol panel malfunction.C ontrol panel malfunction. S ee panel manufacturers instructions .S ee panel manufacturers instructions .

cas ing or other close fitting parts .cas ing or other close fitting parts .

PR OBLE M: NO WATE R DE LIVE R E DPR OBLE M: NO WATE R DE LIVE R E DC AUS E OF TR OUBLEC AUS E OF TR OUBLE C HE C K ING PR OC E DUR EC HE C K ING PR OC E DUR E R E ME DY

Pump not turning.Pump not turning. C heck for broken pump/motor shaft orC heck for broken pump/motor shaft orcoupling. Motor is not running.coupling. Motor is not running.

Discharge line restricted.Discharge line restricted. C heck valve could be installed backwardsC heck valve could be installed backwardsor could be stuck closed.or could be stuck closed.

Inlet restricted.Inlet restricted. S creen could be plugged, well may beS creen could be plugged, well may be

Wrong rotation.Wrong rotation. R otation of three phase motor.R otation of three phase motor.R ecalculate requirements .R ecalculate requirements .Wrong pump selection.Wrong pump selection.

collapsed or the water level may be toocollapsed or the water level may be toolow.

in well. P lugged impeller.in well. P lugged impeller.partially collapsed. Water level too lowpartially collapsed. Water level too low

Pump worn or loose impeller.Pump worn or loose impeller.Mechanical problem.Mechanical problem.

Partially clogged inlet screen. WellPartially clogged inlet screen. WellR estricted inlet.R estricted inlet.C heck valve stuck partially closed.C heck valve stuck partially closed.Line clogged, corroded or ruptured.Line clogged, corroded or ruptured.R estricted discharge.R estricted discharge.

low voltage or low phase. Wrong speed,low voltage or low phase. Wrong speed,R otation could be backwards . C heck forR otation could be backwards . C heck forPump speed or selection.Pump speed or selection.


PR OBLE M: LOW WATE R DE LIVE R YPR OBLE M: LOW WATE R DE LIVE R Y

pump vs . motor.pump vs . motor.

R ecalculate requirements .R ecalculate requirements .

Pump selection incorrect for system.Pump selection incorrect for system.Pump performancePump performance R ecalculate R equirements .R ecalculate R equirements .

R epair or R eplace.R epair or R eplace.

R eplace if defective.R eplace if defective.

R epair or change well locations .R epair or change well locations .

R epair or R eplace.R epair or R eplace.R eplace.


R epair or change well locations .R epair or change well locations .


Page 61Page 61


PR OBLE M: E LE C TR IC S HOC KPR OBLE M: E LE C TR IC S HOC KC AUS E OF TR OUBLEC AUS E OF TR OUBLE C HE C K ING PR OC E DUR EC HE C K ING PR OC E DUR E R E ME DY

Grounding Improper (or absence of) ground onImproper (or absence of) ground onelectrical system, controls or motor.electrical system, controls or motor.

Wiring C heck for improper wiring, groundedC heck for improper wiring, groundedmotor or cable.motor or cable.

C ontrols Defective or burned out component.Defective or burned out component.Moisture Wet controls or wiring.Wet controls or wiring.

C AUTION!E lectric shock from contact with any pumping system part is never safe to ignore! F ind and correct the cause!E lectric shock from contact with any pumping system part is never safe to ignore! F ind and correct the cause!

AMME TE R ANALYS IS OF MOTOR PR OBLE MSAMME TE R ANALYS IS OF MOTOR PR OBLE MSOPE R ATION ANDOPE R ATION AND

AMME TE R R E ADINGSAMME TE R R E ADINGS C ONDIT ION INDIC ATE DC ONDIT ION INDIC ATE D WHAT TO LOOK FOR :WHAT TO LOOK FOR :1 PHAS E MOTOR1 PHAS E MOTOR 3 PHAS E MOTOR3 PHAS E MOTOR

Motor won't start. AmmeterMotor won't start. Ammeterreads zero on all lines .reads zero on all lines .

Power is not connected to motor.Power is not connected to motor. Dead power line.Dead power line.B lown fuses .B lown fuses .Tripped overload.Tripped overload.Defective pressureDefective pressureswitch.Defective control box.Defective control box.S eparated motor leads .S eparated motor leads . S ame

S ame

S ameS ameS ameS ame

splice.Damaged cables orDamaged cables or

Very low voltage.Very low voltage.mounted vertically.mounted vertically.C ontrol box notC ontrol box notDefective control box.Defective control box. S ame

One blown fuseOne blown fuse

One lead in powerOne lead in power

S ame

Power is connected to only partPower is connected to only partMotor won't start. AmmeterMotor won't start. Ammeterreads high on two lines , zeroreads high on two lines , zeroon other line.on other line.

of motor windings .of motor windings .

supply

S ame

something prevents starting.something prevents starting.all leads .reads several times normal onreads several times normal onMotor won't start. AmmeterMotor won't start. Ammeter Power is connected to motor butPower is connected to motor but

S ameS ameTight motor bearings .Tight motor bearings .

Tight pump bearings .Tight pump bearings .Damaged cables orDamaged cables orsplice.Very low voltage.Very low voltage.

S ame

Motor connected toMotor connected toVery low voltage.Very low voltage.Defective relay.Defective relay.mounted vertically.mounted vertically.C ontrol box notC ontrol box not Not applicableC ontrols are not switching outC ontrols are not switching outS ingle phase motor runs butS ingle phase motor runs but

ammeter reads high, especiallyammeter reads high, especiallyon red lead. Overload mayon red lead. Overload may

start capacitor.s tart capacitor.

trip.

wrong phase or voltage.wrong phase or voltage.

S ame

S ameS ame

motor.Incorrect pump forIncorrect pump forLow or high voltage.Low or high voltage.Faulty pump.Faulty pump.Faulty motor.Faulty motor.Motor is overloaded or voltage isMotor is overloaded or voltage is

incorrect.Motor runs but ammeter readsMotor runs but ammeter readshigh on some or all leads .high on some or all leads .Overload may trip.Overload may trip.

S ame



R epair or R eplace.R epair or R eplace.R epair or R eplace.R epair or R eplace.

Page 62Page 62


CLOSED IMPELLER BOWLSCLOSED IMPELLER BOWLSIMPELLER SEAL - BOTT OM FACE AND SKIR T TO MATCHING BOWL SECTIONIMPELLER SEAL - BOTT OM FACE AND SKIR T TO MATCHING BOWL SECTION

SEMI-OPENIMPELLER SEAL - BOTT OM OF VANES TO MATCHING BOWLIMPELLER SEAL - BOTT OM OF VANES TO MATCHING BOWL

SECTION

BOWL MODELBOWL MODELEND PLA YEND PLA YST ANDARD

(inches)

END PLA YEND PLA Y*SPECIAL(inches)

THRUST CONST ANTTHRUST CONST ANTK (Lbs./Ft. Head)K (Lbs./Ft. Head) BOWL MODELBOWL MODEL END PLA Y SPECIALEND PLA Y SPECIAL

(inches) K (Lbs./Ft. Head)K (Lbs./Ft. Head)THRUST CONST ANTTHRUST CONST ANT

6JC M4 3/81/4H46LC

3.528JS

6MC

3.348LS

6HC

4.428KS

2.835/86XC

4.288MS

4.133/86WC

5.403/88EHS

4.101/46YC

8.003/88YS

8JC8LC8KC8MC

5.408EHC

8.008YC3.9810JC4.2010KC

10LS10LC10MS10MC

9.2010HS110HC11.207/810WS1 1/47/810WC11.403/410YS1 1/81 1/83/410YC13.501/210ZS13.607/81/210ZC

8.205/812IS6.757/85/812IC6.607/85/812JC

7/812LS1 3/81 3/812LC12MS12MC

19.0012HS16.5012HC

17.4012WS16.201 3/1612WC16.507/812YS14.201 1/212YC

20.807/812XS18.201 1/412XC

19.7014LS17.2014LC23.4014MS14MC25.2014HS14HC23.4014XS14XC26.2014WS24.8014WC

30.0011/1615KS28.001 1/81 1/811/1615KC

3/8

1/2N/A

1.56

2.24

1.50

7/1623/32 2.98

3.9311/16

1/2

7/85/8

6.60

3/4

8.10

10.30

5/87.50

3/4 1 1/410.60 12.50

3/4

7/8 1 3/8 21.80 7/8

8WC

12KC

13M

14YC14ZC

3/8 5/8

5/83/8

7/83/47/8

3/4

3/4

5/8

15/16

1/2 5/8 6.20

7/8 6.50

1 3/161 3/16 8.00

1/2 5/8 24.701/2 5/8 24.00

12KS 1/2 7.75

7/16

*Special End Play may reduce performance.*Special End Play may reduce performance.NOTE: CONSUL T FACT OR Y if additional end play is required.NOTE: CONSUL T FACT OR Y if additional end play is required.

Page 63Page 63

18LC 1/2 3/4 21.7518MC 1/2 3/4 21.7518HC 1/2 3/4 23.5020MC20HC 5/8

3/411

58.0029.40

END PLAY (LATERAL)-THRUST CONSTANTEND PLAY (LATERAL)-THRUST CONSTANT


Dimensional Information

TURBINE BOWL DIMENSIONS

OPEN LINESHAFT

Bowl Shaft

D

G

F

A

C

E

B

BowlSize

BowlModel

Std.A Alt. A B C D E F G

Available PipeDiameterAll Dimensions Are In Inches

Bowl Max.Dia.

BowlTurbine

Dia.

ShaftDia.

AddStageLength

SuctionBellDia.

ShaftProjection

First StageWithout

Suction Bell

First StageWith

Suction BellSuction Column

6

8

10

12

13

14

15

18

20

Note: Dimensions subject to change without notice

No discharge cases on models 18" and up

6JL6MHXWY

8JL

8KM

8EH

T8RW

10JK

10LMH

10WYZ

12J

12IK

12LMHX

12W

12Y

13M

14LMHX

14W

14YZ

15K

18LMH20M20H

17-1/219-1/419-3/4

N/AN/AN/A

2-3/162-7/16

1419

19-1/2

1820-7/8

23-5/16

7-1/27-1/27-1/2

28.12533.50036.375

N/AN/AN/A

121416

N/A2-7/16

3-3/44-3/4

5-5/8

5-5/8

6-1/4

7-1/2

7-1/4

7

8-1/2

9

10

10-1/2

11-1/4

11-3/4

N/A

7-7/8

7-13/16

7-11/16

7-3/4

5-9/16

7-1/2

7-5/8

3/41

1

1-3/16

N/A

7-1/49-1/47-1/49-1/47-1/49-1/47-1/49-1/4

7-1/2

7-1/2

9-1/411-1/4

9-1/411-1/4

9-1/411-1/4

11-1/413-1/4

11-1/413-1/4

11-1/413-1/411-1/413-1/411-1/413-1/411-1/413-1/413-1/415-1/413-1/415-1/413-1/415-1/413-1/415-1/4

7-1/2

7-1/2

7-1/2

7-1/2

7-1/2

1-1/2

1-11/16

9-1/2

11-1/4

11-1/2

11-1/4 1-11/16

11-3/4

12-1/8 1-11/16 10-3/4

13-1/4 12-1/2

1-15/16 13-1/413-3/4

N/A 1-15/16

12-5/16

15-1/414-3/4

14

13-1/2

12-1/2

12-1/4

11-9/16

12-3/16

12

11-9/16

9-7/8

12.75013.750

13.875

14.500

16.688

N/AN/A

16.93817.43816.93817.43817.56318.06320.250

19.750

19.500

21.000

20.37521.375

23.31324.18823.06323.93824.56325.43824.81326.12525.813

22.25021.87522.75022.62523.50023.125

27.12526.31327.62527.06328.37527.563

24.00022.12523.00025.56326.31326.313

28.87526.56327.87530.43832.81331.188

27.06325.37526.12528.31329.063

33.56330.25032.62533.18835.563

4565656566868688

108

108

108

108

108

101012101210121012

4565656566868688

108

108

108

108

108

101012101210121012

6

8

10

12

13

14

15

6JL6MHXWY

8JL

8KM

8EH

T8RW

10JK

10LMH

10WYZ

12J

12IK

12LMHX

12W

12Y

13M

14LMHX

14W

14YZ

15K

3-3/44-3/4

5-5/8

5-5/8

6-1/4

7-1/2

7-1/4

7

8-1/2

9

10

10-1/2

11-1/4

11-3/4

N/A

7-7/8

7-13/16

7-11/16

7-3/4

5-9/16

7-1/2

7-5/8

3/41

1

1-3/16

N/A

7-1/49-1/47-1/49-1/47-1/49-1/47-1/49-1/4

9-1/411-1/4

9-1/411-1/4

9-1/411-1/4

11-1/413-1/4

11-1/413-1/4

11-1/413-1/411-1/413-1/411-1/413-1/411-1/413-1/413-1/415-1/413-1/415-1/413-1/415-1/413-1/415-1/4

1-1/2

1-11/16

9-1/2

11-1/4

11-1/2

11-1/4

1-11/1611-3/4

12-1/8 10-3/4

13-1/4 12-1/2

1-15/16 13-1/413-3/4

N/A 1-15/16

12-5/16

15-1/414-3/4

14

13-1/2

12-1/2

12-1/4

11-9/16

12-3/16

12

11-9/16

9-7/8

BowlSize

BowlModel

Std.A Alt. A B C D EAll Dimensions Are In Inches

Bowl Max.Dia.

BowlTurbine

Dia.ShaftDia.

AddStageLength

SuctionBellDia.

ShaftProjection

4565656566868688

108

108

108

108

108

101012101210121012

4565656566868688

108

108

108

108

108

101012101210121012

22

22

22

22

22

9-1/2

9-1/2

9-1/2

9-1/2

9-1/2

TubeProj.

Available PipeDiameter

First StageWithout

Suction Bell

First StageWith

Suction BellSuction Column

F G H

TURBINE BOWL DIMENSIONS

ENCLOSED LINESHAFT

Inner Column Adapter(R.H.Thread)

Bowl Shaft

D

H

G

A

C

F

E

B

Note: Dimensions subject to change without notice

14.25015.250

15.000

15.625

17.063

N/AN/A

18.06318.56318.06318.56318.68819.188

20.625

21.750

21.500

23.000

21.87522.875

25.31326.18825.06325.93826.56327.43826.31325.43827.313

23.75023.37524.25024.12525.00024.625

28.62527.81329.12528.56329.87529.063

25.00023.62524.50027.43828.18828.188

30.37528.06329.37532.31334.68833.063

28.93827.25028.00030.18830.938

35.43832.12534.50035.06337.438

N/A N/A

NPT Thread

CG H D E

A

SUBMERSIBLE TURBINES

B F

Nom.BowlSize

BowlModel

BowlDia.Max.O.D.

BowlDia.

TurnedO.D.

Shaft A B C D E F G HAvailableDischarge

Conn.N.P.T.

MotorSize

All Dimensions Are In Inches

6"6"6"6"6"6"8"8"8"8"8"8"8"8"

3.7505.3753.7505.3753.7505.3755.3757.3755.3757.3755.3757.3755.3757.375

5.8755.8755.8135.8135.8755.8757.8757.8757.6887.6887.8757.8757.7507.750

5.5635.5635.5635.5635.5635.5637.5007.5007.5007.5007.5007.5007.6257.625

17.62518.62518.62519.62518.62519.62522.56323.87523.18824.50024.43825.75024.68826.000

5.8755.8755.8755.8755.8755.8757.8137.8137.8137.8137.8137.8137.8137.813

5.3755.3755.3755.3755.3755.3755.2505.2505.2505.2505.2505.2505.6255.625

3.7503.7504.7504.7504.7504.7505.6255.6256.2506.2507.5007.5007.5007.500

8.5009.5008.5009.5008.5009.500

11.68813.00011.68813.00011.68813.00011.56312.875

1.6251.6251.6251.6251.6251.6251.7501.7501.7501.7501.7501.7501.7501.750

3.7503.7503.7503.7503.7503.7503.5003.5003.5003.5003.5003.5003.8753.875

4"4"4"4"4"4"6"6"6"6"6"6"6"6"

4"6"4"6"4"6"6"8"6"8"6"8"6"8"

3/4"3/4"1"1"1"1"1"1"1"1"

1-3/16"1-3/16"1-3/16"1-3/16"

NS6JLNJ6JL

NS6MHXNS6MHXNS6WYNS6WY

NS8JLKMNS8JLKMNS8EHNS8EHNS8YNS8Y

NS8RWNS8RW

Note: Drawing depicts flanged bowl assembly. Dimensions are representative of both flanged or threaded conditions.

Standard Duty - High ProfileWith Threaded Inlet

L2

G

C

E

9' 11-1/4" TopColumn Pipe

10' ColumnPipe And

Spider Assembly

Heavy Duty - Low ProfileWith Head Column Flange

B

10' Bottom ColumnPipe And Spider

Assembly

Discharge Case

7-1/2" ShaftProjection

10' StandardLineshaft


Notes:"CD" dimension is to be obtained from the appropriate geardrive or motor vendor catalog."E" HIGH PROFILE = From top outer column (butt joint) tobottom of discharge head.

HIGH PROFILEHead Shaft Couples Above The Packing Housing Kit

(Inches)

TR4A TR6B/BC TR8C TR10C TR10HD TR12HD

G

C

E

L2

B

Note:Top and Bottom Standard is 9' 11-1/4" (or 4' 11-1/4" at customers request.)

Z

G

E

L1

C

L1 G

EC

Z

8' 9-7/8"Top Shaft

15-7/8

2-7/8

1-5/8

123-1/2

16-7/8

3-3/8

1-3/4

123-1/2

20-7/16

4-3/16

2

126

21-7/16

4-11/16

2-1/2

126

22-3/8

4-1/8

2-1/2

127-1/2

23

4

2-1/2

128-1/4

"C" + "CD" + 2" = Head Shaft Length

F4A F6C F8C F10C F12C

LOW PROFILEHead Shaft Couples Below Head

(Inches)

17-3/16

13-1/4

2-1/2

3-15/16

18-15/16

15-1/4

2-1/2

3-11/16

18-11/16

15-1/2

3

3-3/16

20-9/16

18-3/8

4

2-3/16

22-15/16

20-3/4

4

2-3/16

"Z" + "CD" + 2" = Head Shaft Length

OPEN LINESHAFTTURBINE PUMP COLUMN DIMENSIONS

Heavy Duty - Low ProfileWith Head Column Flange

HIGH PROFILEHead Shaft Couples Above The Packing Housing Kit

(Inches)

TR4A TR6B/BC TR8C TR10C TR10HD TR12HD

G

C

E

L2

B

Z

G

E

L1

B

15-7/8

2-7/8

1-1/2

110

16-7/8

3-1/8

1-3/4

110

20-7/16

5

2

111-7/16

21-7/16

4-11/16

2-1/2

112-1/4

22-3/8

4-1/8

2-1/2

112-1/4

23

4

2-1/2

114-1/2

"C" + "CD" + 2" = Head Shaft Length

F4A F6C F8C F10C F12C

LOW PROFILEHead Shaft Couples Below Head

(Inches)

13-1/16

13-1/4

2-3/16

120"

15-1/16

15-1/4

2-3/16

120"

14-13/16

15-1/2

2-11/16

120"

16-11/16

18-3/16

3-11/16

120"

19-1/16

20-3/4

3-11/16

120"

"Z" + "CD" + 2" = Head Shaft Length

L1 G

B Topshaft

EZ

28"**(See notes)

5" InnerColumnExtension

ENCLOSED LINESHAFT TURBINE PUMP COLUMN DIMENSIONS

Notes:"CD" dimension is to be obtained from the appropriate gearor motor vendor catalog."E" HIGH PROFILE = From top outer column (butt joint) tobottom of discharge head.**28" is provided by the factory. Customer is to cut tolength at installation.

Standard Duty - High ProfileWith Threaded Inlet

CL2

G

E28"**

(See notes)

B Top Shaft

5' InnerColumnExtension

2' TopColumnPipe


10' ColumnPipe

5' InnerColumn

10' BottomColumn

Pipe

5' InnerColumn

22" ShaftProjection

Discharge Case

9-1/2"Projection

DischargeHeadModel

STANDARD DUTY - HIGH PROFILE DISCHARGE HEADSAND FOUNDATION PLATES

Discharge InnerColumn

OuterColumn

TR4ATR6BTR6CTR8CTR10C

TR10HDTR12HD

4668

101012

222

2-1/22-1/23-1/23-1/2

4668

101012

1012

16-1/216-1/216-1/2

2020

8-1/48-1/4

13-1/213-1/213-1/213-1/213-1/2

7/167/16

11/1611/1611/1611/1611/16

9-1/89-1/814-3/414-3/414-3/414-3/414-3/4

1-5/81-3/41-3/4

22-1/22-1/22-1/2

15-7/816-7/816-7/820-7/1621-7/1622-3/8

23

44-1/84-1/8

3-13/164-5/165-1/165-3/16

6-3/48-3/88-3/8

10-11/1610-11/1611-5/1611-15/16

99-1/89-1/812-1/410-7/811-1/16

11

A B C D E F G H J

Standard Duty - High Profile Discharge HeadsDimensions (In Inches)

(4) Dia.Holes

Square

(4) "F" Dia.Holes Thru(4) "G" Dia Holes ThruTap "H" Thru

C

AB

D E

ED

J

AB

P

T

(4) Dia.HolesD

J

G

X

HE S

R N.P.TThread

Z

N

M

S

F

A

B

C

Dia.

B.C.Dia.

Dia.

NOTE: Dimensions are subject to change without notice.

125 # A.S.ADisch. FlangeK L

QOn B.C.

Foundation Steel Plates(Standard Threaded Discharge Heads)

Foundation Steel Plates(Standard Threaded Discharge Heads)

Plate Dimensions

Plate DimensionsDisch.HeadModel

Disch.HeadModel

Approx.Weight

TR4ATR6BCTR8CTR10C

TR10HDTR12HD

130130130130165180

24.00024.00024.00024.00026.00028.000

12.00012.00012.00012.00013.00014.000

12.50013.00016.50016.75017.50018.500

10.50010.50010.50010.50011.50012.500

5.0316.0166.6256.6257.5168.047

TR4ATR6BCTR8CTR10C

TR10HDTR12HD

A B C D E

F G H J1-1/81-1/81-1/81-1/81-1/81-1/4

49/6449/64

7/87/87/8

63/64

7/8-9UNC-2B7/8-9UNC-2B

1-8UNC-2B1-8UNC-2B1-8UNC-2B

1-1/8-7UNC-2B

1.0001.0001.0001.0001.0001.250

"All Dimensions in inches"

TR4ATR6BTR6CTR8CTR10C

TR10HDTR12HD

8888121212

5/8 Tap3/4 Tap3/4 Tap3/4 Tap7/8 Tap7/8 Tap7/8 Tap

Standard Duty - High Profile Discharge HeadsDimensions (In Inches)

3/43/43/43/43/43/43/4

1-1/81111

1-11/162-3/16

111

1-1/81-1/81-1/81-1/4

6-7/87-3/47-3/48-3/16

10-9/1611-5/16

12

8-3/47-7/87-7/810101014

1619192121

23-1/225

10-1/1612-1/3212-1/3213-1/413-1/4

15-1/3216-3/32

7-1/29-1/29-1/2

11-3/414-1/414-1/4

17

3-1/83-1/83-3/43-3/43-3/4

55

DischargeHeadModel K L M N P Q R S T X Z

HEAVY DUTY - LOW PROFILE DISCHARGE HEADSAND FOUNDATION PLATES

F4AF6BF6CF8CF12C

4668

12

222

2-1/22-1/2

566

1012

1012

16-1/216-1/216-1/2

9-1/89-1/89-1/8

14-3/414-3/4

8-1/48-1/413-1/213-1/213-1/2

3/83/83/85/85/8

2-1/22-1/22-1/2

34

6-1/28-5/168-5/167-7/8

10-7/8

13-1/415-1/415-1/415-1/220-3/4

55-7/165-7/166-1/47-3/4

A B C D E F G H

DischargeHeadModel Discharge Inner

ColumnOuter

Column

Heavy Duty - Low Profile Discharge HeadsDimensions (In Inches)

Heavy Duty - Low Profile Discharge HeadsDimensions (In Inches)Discharge

HeadModel

F4AF6BF6CF8CF12C

5-1/26-1/46-1/46-1/28-1/4

10111115

17-1/2

12-3/414-3/414-3/417-1/420-1/4

7-1/88-3/168-3/169-3/4

11-3/4

14-1/416-3/816-3/819-1/2

23

11-1/213-1/813-1/815-1/2

18

1-1/21-1/21-1/22-1/22-1/2

1-1/81-3/81-3/81-1/2

2

3/47/87/8

1-1/81-1/4

3-1/83-1/83-1/83-3/4

5

J K L M N P R S T Z

NOTE: Dimensions are subject to change without notice.

ABC

Dia.

Dia.B.C. "D" - NC Thrd.

JZ Bore Dia.

Through Head

125 # A.S.A.Disch. Flange

G

F

E

KL

M

Dia.Square

0.06

3

"R" - N.P.T.

(4) "T" Dia.Holes

H

S

AB

D E

A

DE

B

C

J

(4) "F" Dia.Holes Thru

(4) "G" Dia.Holes ThruTap "H" Thru

P SquareN Square

"All dimensions in inches"

Foundation Steel Plates (Heavy Duty - Low Profile Discharge Heads)Disch.Head

ModelApprox.Weight

Plate Dimensions

F4AF6A/F6C

F8CF12C

5586

108173

18.00020.00024.00026.000

9.00010.00012.00013.000

12.50012.50016.00016.000

7.7508.750

10.50011.500

5.7506.5637.7509.000

1.0001.0001.0001.250

3/47/8

1-1/81-1/4

17/3221/327/8

63/64

5/8-11UNC-2B3/4-10UNC-2B

1-8UNC-2B1-1/8-7UNC-2B

A B C D E F G H J

Documents

AMP EPG Engineering Catalog 2010 aadicps-fire.com/CPS catalog locked/without curve/CPS VT Catalog.pdf · ANSI/AWWA Specification E101, Section 5.1 “Standard Specifications ... 69