TECHNICAL Layne Engineering Manual

TRAINING DOCUMENT

GENERAL

ENGINEERING

MANUAL

LAYNE BOWLER PUMP CO.

LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL

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VERTICAL TURBINE PUMP TYPES

Open Lineshaft

Deep well

Enclosed Lineshaft

Open Lineshaft

Above floor discharge

Enclosed Lineshaft

Lineshaft

Short setting

Open Lineshaft

Below floor discharge

Enclosed Lineshaft

In-line nozzles

Vertical Turbine Pumps

Barrel or can

Suction nozzle in barrel

Well

Open pit mounting

Submersible

Short setting

Barrel mounting

Horizontal in-line mounting


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DEEPWELL LINESHAFT VERTICAL TURBINE PUMP SELECTION

VERTI-LINE vertical turbine pumps are engineered in three basic assemblies. Each has to be combined to perform its particular function and to operate with together. To do this properly, each must be understood by the engineer and selected in the sequence below.

A – BOWL ASSEMBLY

This is the pumping element and consists of a vertical rotating shaft on which is mounted one or more impellers called rotor part. The impellers are rotated in enclosed housings or bowls called stator part and water flows into the bottom of the bowl, it is engaged by the rotating vanes of the impeller and forced into guide vanes in the bowl, changing the flow direction to direct the other impellers. It is a special series pump application for deep and narrow wells. Head is increased by the number of stages (including impeller and bowl) linearly. Quantity and pressure developed are dependent on the diameter and rotational speed of the impeller. In general increased diameter, capacity increases. For the same diameter, while the rotational speed increases, the head and capacity also increases for the same pump. The total pressure of a multi-stage pump is the sum of the pressures developed by individual stages.

B – COLUMN ASSEMBLY

This assembly consists of the column pipe which suspends the bowl assembly from the discharge head assembly and directs the water from the bowl assembly to the discharge elbow. Contained within the column is the lineshaft which transmits power from the driver to the pump shaft. The lineshaft is supported throughout its length by means of bearings which are placed according to the speed of the pump. Shafts may be in an enclosed in a tube. This type is generally lubricated with oil. Also, the shaft may be open and lubricated with the fluid being pumped. The length of this assembly must be sufficient to provide submergence of the pump bowl assembly when pumping at the designated capacity.

The pump column should be of sufficient diameter to conduct the desired quantity of water through its entire length without excessive friction loss. The line shaft diameter is determined by the power to be transmitted to the pump shaft and also by the rotational speed, length of the column and shaft assembly, and total pump head (TPH).

C – DISCHARGE HEAD ASSEMBLY

The discharge head assembly consists of the base on which the driver is mounted and the discharge elbow which directs the flow into the piping system. The column shaft assembly, and bowl assembly are suspended from the discharge head assembly.

In the case of underground discharge, the discharge elbow is separated from the head assembly and installed in the column pipe at the desired distance below the head assembly.

The driver is the mechanism mounted on the discharge head which gives power to the head shaft. It contains means for impeller adjustment and provides a bearing to carry the thrust load. It may or may not be a prime mover.

The driver may be a vertical solid shaft electric motor, vertical hollow shaft electric motor, vertical hollow shaft right angle gear drive, vertical hollow shaft belted head with either flat belt or V-belt pulley, or vertical steam turbine.

The thrust assembly is a mechanism having a thrust bearing capable of carrying the pump thrust, and a means of impeller adjustment. Some drivers have thrust capacity in itself. In many applications, thrust assembly is an extra part. The pump line shaft is connected to the driver shaft by a flexible coupling. The top of this drive is designed to mount solid shaft prime movers including electric motors, steam turbines, radial engines or any other type of prime mover having a solid shaft that is suitable for mounting in a vertical position.

Selection of the driver is governed by power requirements; availability of electric power and current characteristics; economic and other considerations.


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WELL PUMP SELECTION EXAMPLE

Proper selection of a deep well turbine pump requires complete and accurate information about the conditions of service for which the pump is intended. This is important for to select the right pump to meet the desired working conditions and also for the life cycle cost. Data to be furnished should include pump capacity, internal diameter of the well casing, depth of well, static water level, dynamic water level at designated capacity (determined by well test), static head, friction losses through discharge line, velocity head and total pumping head. If water analysis or other observations indicate corrosive water, then all available information on this subject should be noted to aid in determining whether special materials are to be considered. An example of well pump selection is given below, and for this purpose we will use the following conditions, which constitute a typical application with no complex problems. Whether oil or water lubrication is furnished is a matter of customer preference, type of service and other considerations.

A – WELL DESCRIPTION & OPERATING CONDITIONS

1. I.D. of well casing 13 ½ inches 2. Well depth 100 m 3. Static water level 30 m 4. Drawdown (at 60 l/s) 20 m 5. Dynamic water level (pumping water level) 50 m 6. Geometric head (lift above well head) 50 m 7. Discharge Line Losses (after discharge head) 2.5 m 8. Velocity Head 0.5 m 9. Total pump head (TPH) (sum of items 5, 6, 7 and 8) 103 m 10. Pump capacity 60 l/s 11. Quality of water Sand-free, non-corrosive, 20°C, Sp. Gr. 1.0 12. Current available 380 Volt, 3 phase, 50 Hz

B – BOWL ASSEMBLY SELECTION

According to well conditions and desired performance values with the power supply types and limitations, different selections can be done. This selection is based on low investment cost (high speed low stage small pump), low life cycle cost (high efficiency, low speed pump), low NPSHR, standard motor speed or different speeds with gear heads etc.

Refer to pump performance curves which show laboratory performance at various induction motor speeds. Unless otherwise stated on curve sheets the values are per-stage performance. Keep in mind that the O.D. of the bowls must be less than the I.D. of well casing into which the bowls must fit.

Performance curves are plotted from data obtained in our hydraulic test laboratory. Head-Capacity curves are the bowl performance curves showing the relationship of amount of water pumped to corresponding bowl head. The curves are marked A, C and the box above shows the corresponding impeller diameters. Select one or more curves at 2980 rpm showing the desired capacity at the maximum efficiency, or slightly less, and then determine which shows the greatest head at this capacity. We find three bowl units to consider:

Bowl Unit Head/Stage Bowl. Eff. 10RL 32.5 m 79.7 % 10RM 35.0 m 80.0 % 10RH 38.5 m 77.8 %

The 10RM impeller is obviously the best selection because of high efficiency and high head per stage. The total pumping head required is 103 m, and the head per stage is 35.0 m, thus:

1032.9 stages

35.0

Obviously it should be a 3 stage bowl assembly. The 10RM 3 stages bowl assembly will deliver 60 l/s at 105 m which is slightly in excess of the head required. This is acceptable since we did not consider any head losses in the system. From the power curve, approximate bowl power required by 10RM 3 stages bowl assembly is 78 kW.


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C – COLUMN SELECTION

The pump bowls must be submerged at all times; therefore, the column length must be minimum equal to the dynamic water level. To provide protection against decrease water level and for applications where pump will sometimes operate at lower head and higher capacity than design point (resulting in lower dynamic water level) pump setting should be from 3 to 6 m lower than normal dynamic water level. The column length is commonly referred to as setting. In this case the required setting is taken as 55 m.

Following factors are established: Size and number of stages of bowl assembly; approximate bowl power required; depth of setting and TPH.

Shaft selection table gives the maximum power that can be transmitted by a shaft at a given thrust load. Downthrust is the total thrust load expressed in kilograms carried by the thrust bearing in the motor, gear drive or thrust assembly. It is the sum of the weight of the rotating elements and the hydraulic downthrust of the impeller. Hydraulic thrust factors of the impellers are read from performance curves. In this example, we calculate the hydraulic downthrust as:

105 12.41 1300 kg hydraulic downthrustHT

Hence, 1 3/16” AISI 420 shaft is selected regarding these data and the shaft friction loss is calculated as:

552.8 2 3.1 kW

100L

kW

From the same table, oil tube size for 1 3/16” shaft is found to be 2”. From the column friction loss table, we select 8” column pipes and calculate the column friction loss as:

553.18 1.75 m

100Ch

Discharge head loss (hDH) is read from discharge head loss graph as 0.14 m for 8” nominal elbow size. Total Bowl Head (TBH) is calculated as:

103 1.75 0.14 104.89 105 mC DH

TBH TPH h h

This head fall exactly on 10RM 3 stages bowl assembly curve so no impeller trim is required. Pump power is now calculated as:

/ 60 1053.1 80.2 kW

1.02 1.02 80.0P L

B

Q l s TBH mkW kW

D – MOTOR & DISCHARGE HEAD SELECTION

NEMA designs A, B, C and F poly-phase squirrel cage induction type integral power motors, 3 HP, 3 phase 50 Hz and larger, have a service factor of 1.15. It is permissible to operate these motors at rated voltage and frequency in an ambient temperature not exceeding 40°C, at continuous load of 115% of rated load, with possible slight differences in efficiencies and power factor than those rated at full load. We do not generally recommend exceeding the rated motor power by more than 10%.

In this example, we select a 90 kW, 3000 rpm (full load speed of 2980 rpm), 220/440 volt, 3 phase, 50 Hz vertical hollow shaft motor (VHS) with 2000 kg thrust capability which is sufficient for this application.

Proper discharge head for this pump and motor is 17AC8 with 1 ½” head shaft.


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SUMMARY OF CALCULATIONS

Specified Conditions @ 2980 RPM

1 Capacity 60 l/s 2 Static Water Level 30 m 3 Drawdown 20 m 4 Dynamic Water Level (sum of 2 and 3) 50 m 5 Geometric Head 50 m 6 Discharge Line Losses 2.5 m 7 Velocity Head 0.5 m 8 Total Pump Head (sum of 4, 5, 6 and 7) 103 m

Calculated Values 9 Column Friction Loss 1.75 m 10 Discharge Head Loss 0.14 m 11 Total Bowl Head (sum of 8, 9 and 10) 105 m 12 Water Power 61.8 kW 13 Bowl Efficiency 80.0 % 14 Bowl Power 77.1 kW 15 Lineshaft Friction Loss 3.1 kW 16 Shaft and Impeller Weight 300 kg 17 Hydraulic Thrust 1300 kg 18 Total Pump Thrust (sum of 15 and 16) 1600 kg 19 Thrust Bearing Loss (neglected) 0 kW 20 Pump Power (sum of 13, 14 and 18) 80.2 kW 21 Pump Efficiency 76.9 % 22 Motor Efficiency 92.5 % 23 Wire Power (input power) 86.7 kW 24 Overall Efficiency (wire to water) 71.1 %


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VERTICAL TURBINE PUMP TERMINOLOGY


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1. Datum

It is the reference line where altitude is taken as zero. Generally discharge pipe centerline is taken as datum.

2. Ground

It is the place where discharge head assembly sits.

3. Discharge Axis

It is the vertical distance between ground and datum.

4. Static Water Level

It is the vertical distance from ground to the water level in the well while pump is not operating.

5. Dynamic Water Level

It is the vertical distance from ground to the water level in the well while pump is operating at specified capacity.

6. Drawdown

It is the vertical distance between static water level and pumping water level.

7. Geometric Head

It is the vertical distance from the ground to the desired location in the discharge line. It can also be expressed by a discharge pressure.

8. Velocity Head

It is the head due to the velocity of the fluid at a given pipe section.

9. Discharge Line Losses

It is the head loss occurring in the whole discharge line after the discharge head.

10. Total Pump Head (TPH)

It is the head specified by the customer and equal to pumping water level plus geometric head plus discharge line losses plus velocity head.

11. Total Bowl Head (TBH)

It is the head that should be delivered by the bowl assembly and equal to TPH plus column friction loss plus discharge head loss.

12. Water Power

It is the power imparted to the fluid.

13. Bowl Efficiency

It is the ratio of the bowl output based on TBH to bowl power. Generally it is the efficiency read from performance curves.


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14. Bowl Power

It is the power required by the bowl assembly giving the TBH at the designated capacity.

15. Lineshaft Friction Loss

It is the power loss due to the friction in lineshaft bearings in the column assembly.

16. Thrust Bearing Loss

It is the power loss in the thrust bearing due to the total pump thrust load.

17. Hydraulic Thrust

It is load expressed in kg due to fluid flow across the impeller and found by multiplying the maximum operating head by the thrust coefficient given in the performance tables.

18. Total Pump Thrust

It is the total load expressed in kg acting on the thrust bearing and found by adding the weight of the rotating members to the hydraulic thrust.

19. Pump Power

It is the total power required by the pump assembly and found by adding the lineshaft friction loss and thrust bearing loss to the bowl power.

20. Pump Efficiency

It is ratio of the water power to the pump power in percentage.

21. Motor Efficiency

It is the efficiency of the driver.

22. Wire Power

It is the power input to the motor.

23. Overall Efficiency

It is the ratio of the water power to the wire power in percentage.


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USEFUL FORMULAE

3 2 3

W

/ / /1000

/102

3746

where

Q : CapacityH : Total Bowl Head in mN : Rotational Speed in rpmP : Wat

W

W

WB

B

P B LF TF

WP

P

PI

M

WO

I

kg m g m s Q m s H mP

Q l s H mP

PP

P P P PPP

P V I PFP

PP

B

L

T

P

I

B

er Power in kWP : Bowl Power in kWP : Lineshaft friction losses in kWP : Thrust bearing loss in kWP : Pump Power in kWP : Wire (input) Power in kWη : B

P

M

O

owl Efficiency (read from performance curves)η : Pump Efficiencyη : Motor Efficiencyη : Overall EfficiencyV : Voltage per leg applied to motorI : Current per leg applied to motorPF : Power factor of the motor (CosØ)


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UNIT CONVERSION TABLE

Pressure atm bar kPa kgf/cm² mWC psi

atmosphere 1 1.01325 101.325 1.03323 10.33256 14.69594 bar 0.98692 1 100 1.01972 10.19744 14.50377

kilopascal 0.00987 0.01 1 0.01020 0.10197 0.14504 kilogram-force / centimeter square 0.96784 0.98067 98.0665 1 10.00028 14.22334

meter water column 0.09678 0.09806 9.80638 0.10000 1 1.42229 pound-force/inch square 0.06805 0.06895 6.89476 0.07031 0.70309 1

Capacity l/s m³/s m³/h l/min gpm (US) gpm (GB)

liter/second 1 0.001 0.27778 60 15.85032 13.19815 cubic meter/second 1000 1 277.77778 60000 15850 13198

cubic meter/hour 3.6 0.0036 1 216 57.06116 47.51334 liter/minute 0.01667 1.67E-05 0.00463 1 0.26417 0.21997

gallon/minute (US) 0.06309 6.31E-05 0.01753 3.78541 1 0.83267 gallon/minute (GB) 0.07577 7.58E-05 0.02105 4.54609 1.20095 1

Length mm m in ft yd

millimeter 1 0.001 0.03937 0.00328 0.00109 meter 1000 1 39.37008 3.28084 1.09361 inch 25.4 0.0254 1 0.08333 0.02778 foot 304.8 0.3048 12 1 0.33333 yard 914.4 0.9144 36 3 1

Area mm² m² in² ft² yd²

millimeter square 1 0.000001 0.00155 1.08E-05 1.20E-06 meter square 1000000 1 1550.0031 10.76391 1.19599 inch square 645.16 0.00065 1 0.00694 0.00077 foot square 92903.04 0.09290 144 1 0.11111 yard square 836127.36 0.83613 1296 9 1

Volume l m³ in³ ft³ yd³

liter 1 0.001 61.02374 0.03531 0.00131 cubic meter 1000 1 61023.74409 35.31467 1.30795 inch cube 0.01639 1.64E-05 1 0.00058 2.14E-05 foot cube 28.31685 0.02832 1728 1 0.03704 yard cube 764.55486 0.76455 46656 27 1

Rotational Speed rad/s rad/min rps rpm

radian/second 1 60 0.15915 9.54930 radian/minute 0.01667 1 0.00265 0.15915

revolution/second 6.28319 376.99112 1 60 revolution/minute 0.10472 6.28319 0.01667 1

Power W kW hp watt 1 0.001 0.00134

kilowatt 1000 1 1.34048 horsepower 746 0.746 1

Mass kg lb oz

kilogram 1 2.20462 35.27396 pound 0.45359 1 16 ounce 0.02835 0.0625 1

Force kgf N lbf

kilogram-force 1 9.80665 2.20462 Newton 0.10197 1 0.22481

pound-force 0.45359 4.44822 1


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APPROXIMATE FLOW MEASUREMENT FROM OPEN PIPES

When there are no instruments available to accurately measure the flow of water from a pump, following method will serve as an approximation.

D — mm

250 300 350 400 450 500 550 600 650 700 750 800 850 900 950 1000 Pipe Diameter inch Approximate Capacity — l/s

3 4.6 5.5 6.4 7.3 8.2 9.2 10.1 11.0 11.9 12.8 13.7 14.7 15.6 16.5 17.4 18.3 4 8.1 9.8 11.4 13.0 14.7 16.3 17.9 19.6 21.2 22.8 24.4 26.1 27.7 29.3 31.0 32.6 5 12.7 15.3 17.8 20.4 22.9 25.5 28.0 30.6 33.1 35.6 38.2 40.7 43.3 45.8 48.4 50.9 6 18.3 22.0 25.7 29.3 33.0 36.7 40.3 44.0 47.7 51.3 55.0 58.7 62.3 66.0 69.7 73.3 8 32.6 39.1 45.6 52.1 58.7 65.2 71.7 78.2 84.7 91.3 97.8 104.3 110.8 117.3 123.8 130.4

10 50.9 61.1 71.3 81.5 91.7 101.8 112.0 122.2 132.4 142.6 152.8 163.0 173.1 183.3 193.5 203.7 12 73.3 88.0 102.7 117.3 132.0 146.7 161.3 176.0 190.7 205.3 220.0 234.7 249.3 264.0 278.6 293.3


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LINESHAFT SELECTION TABLE

AISI 420 Thrust Load — kg 500 1000 1500 2000 3000 4000 5000 6000 7500 9000 10500 12000 15000 20000 Diameter

inch Speed rpm Maximum Transmissible Horsepower — kW 2980 30.0 29.3 28.2 26.5 20.9 8.0 1480 14.9 14.6 14.0 13.2 10.4 4.0 990 10.0 9.7 9.4 8.8 6.9 2.7

3/4

740 7.5 7.3 7.0 6.6 5.2 2.0 2980 71.5 71.0 70.2 69.0 65.5 60.2 52.7 41.7 1480 35.5 35.3 34.9 34.3 32.5 29.9 26.2 20.7 990 23.8 23.6 23.3 22.9 21.8 20.0 17.5 13.8

1

740 17.8 17.6 17.4 17.1 16.3 15.0 13.1 10.3 2980 119.9 119.5 118.8 117.8 114.9 110.8 105.2 98.0 83.1 60.1 1480 59.5 59.3 59.0 58.5 57.1 55.0 52.3 48.7 41.3 29.9 990 39.8 39.7 39.5 39.1 38.2 36.8 35.0 32.6 27.6 20.0

1 3/16

740 29.8 29.7 29.5 29.2 28.5 27.5 26.1 24.3 20.6 14.9 2980 241.8 241.5 240.9 240.2 237.9 234.8 230.7 225.5 215.8 203.2 187.3 167.1 103.4 1480 120.1 119.9 119.7 119.3 118.2 116.6 114.6 112.0 107.2 100.9 93.0 83.0 51.4 990 80.3 80.2 80.0 79.8 79.0 78.0 76.6 74.9 71.7 67.5 62.2 55.5 34.4

1 1/2

740 60.0 60.0 59.8 59.6 59.1 58.3 57.3 56.0 53.6 50.5 46.5 41.5 25.7 2980 382.6 382.4 381.9 381.3 379.5 377.1 373.8 369.8 362.4 353.1 341.8 328.2 293.2 197.1 1480 190.0 189.9 189.7 189.4 188.5 187.3 185.7 183.7 180.0 175.4 169.7 163.0 145.6 97.9 990 127.1 127.0 126.9 126.7 126.1 125.3 124.2 122.9 120.4 117.3 113.5 109.0 97.4 65.5

1 11/16

740 95.0 95.0 94.8 94.7 94.2 93.6 92.8 91.8 90.0 87.7 84.9 81.5 72.8 48.9 2980 579.2 579.0 578.6 578.0 576.5 574.3 571.6 568.1 561.8 553.9 544.5 533.4 505.7 440.1 1480 287.6 287.5 287.3 287.1 286.3 285.2 283.9 282.2 279.0 275.1 270.4 264.9 251.2 218.6 990 192.4 192.3 192.2 192.0 191.5 190.8 189.9 188.7 186.6 184.0 180.9 177.2 168.0 146.2

1 15/16

740 143.8 143.8 143.7 143.5 143.2 142.6 141.9 141.1 139.5 137.5 135.2 132.4 125.6 109.3

AISI 1045 Thrust Load — kg 500 1000 1500 2000 3000 4000 5000 6000 7500 9000 10500 12000 15000 20000 Diameter

inch Speed rpm Maximum Transmissible Horsepower — kW 2980 26.0 25.3 23.9 21.9 14.6 1480 12.9 12.5 11.9 10.9 7.3 990 8.7 8.4 7.9 7.3 4.9

3/4

740 6.5 6.3 5.9 5.4 3.6 2980 62.1 61.6 60.6 59.2 55.1 48.7 39.0 22.0 1480 30.9 30.6 30.1 29.4 27.4 24.2 19.4 10.9 990 20.6 20.5 20.1 19.7 18.3 16.2 13.0 7.3

1

740 15.4 15.3 15.0 14.7 13.7 12.1 9.7 5.5 2980 104.2 103.7 102.9 101.8 98.5 93.6 87.0 78.1 58.3 10.1 1480 51.8 51.5 51.1 50.6 48.9 46.5 43.2 38.8 29.0 5.0 990 34.6 34.5 34.2 33.8 32.7 31.1 28.9 25.9 19.4 3.4

1 3/16

740 25.9 25.8 25.6 25.3 24.5 23.2 21.6 19.4 14.5 2.5 2980 210.2 209.9 209.2 208.3 205.8 202.1 197.3 191.3 179.7 164.4 144.3 116.8 1480 104.4 104.2 103.9 103.5 102.2 100.4 98.0 95.0 89.3 81.7 71.7 58.0 990 69.8 69.7 69.5 69.2 68.4 67.1 65.6 63.6 59.7 54.6 47.9 38.8

1 1/2

740 52.2 52.1 52.0 51.7 51.1 50.2 49.0 47.5 44.6 40.8 35.8 29.0 2980 332.7 332.4 331.9 331.2 329.1 326.3 322.5 317.9 309.2 298.3 284.8 268.4 224.1 56.0 1480 165.2 165.1 164.8 164.5 163.5 162.0 160.2 157.9 153.6 148.1 141.4 133.3 111.3 27.8 990 110.5 110.4 110.3 110.0 109.3 108.4 107.2 105.6 102.7 99.1 94.6 89.2 74.4 18.6

1 11/16

740 82.6 82.5 82.4 82.2 81.7 81.0 80.1 78.9 76.8 74.1 70.7 66.6 55.6 13.9 2980 503.6 503.4 502.9 502.3 500.5 498.0 494.8 490.9 483.5 474.3 463.3 450.2 417.0 334.4 1480 250.1 250.0 249.8 249.5 248.6 247.3 245.8 243.8 240.1 235.6 230.1 223.6 207.1 166.1 990 167.3 167.2 167.1 166.9 166.3 165.5 164.4 163.1 160.6 157.6 153.9 149.6 138.5 111.1

1 15/16

740 125.1 125.0 124.9 124.7 124.3 123.7 122.9 121.9 120.1 117.8 115.0 111.8 103.6 83.1

Reference: ANSI B58.1-1971, AWWA E101-71

Note: At a given thrust load, maximum transmissible power is directly proportional with speed.


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MECHANICAL FRICTION IN LINESHAFT BEARINGS

Rotational Speed — rpm 3500 2980 1770 1480 1170 990 880 740

Shaft Diameter

Oil Pipe Diameter

Mechanical Friction — kW / 100 m 3/4 “ 1 1/4 “ 1.3 1.1 0.7 0.6 0.4 0.4 0.3 0.3

1 “ 1 1/2 “ 2.4 2.0 1.2 1.0 0.8 0.7 0.6 0.5 1 3/16 “ 2 “ 3.3 2.8 1.7 1.4 1.1 0.9 0.8 0.7 1 1/2 “ 2 1/2 “ 5.3 4.5 2.7 2.2 1.8 1.5 1.3 1.1

1 11/16 “ 3 “ 6.7 5.7 3.4 2.8 2.2 1.9 1.7 1.4 1 15/16 “ 3 “ 8.9 7.6 4.5 3.8 3.0 2.5 2.2 1.9

55 mm 4 ” 11.1 9.4 5.6 4.7 3.7 3.1 2.8 2.3 60 mm 4 “ 13.2 11.2 6.7 5.6 4.4 3.7 3.3 2.8 65 mm 4 “ 15.5 13.2 7.8 6.5 5.2 4.4 3.9 3.3 70 mm 5 “ 17.9 15.3 9.1 7.6 6.0 5.1 4.5 3.8 75 mm 5 “ 20.6 17.5 10.4 8.7 6.9 5.8 5.2 4.4 80 mm 5 “ 23.4 20.0 11.9 9.9 7.8 6.6 5.9 5.0 85 mm 5 “ 26.5 22.5 13.4 11.2 8.8 7.5 6.7 5.6 90 mm 5 “ 29.7 25.3 15.0 12.5 9.9 8.4 7.5 6.3 95 mm 6 “ 33.1 28.1 16.7 14.0 11.1 9.4 8.3 7.0

100 mm 6 “ 36.6 31.2 18.5 15.5 12.2 10.4 9.2 7.7 105 mm 6 “ 40.4 34.4 20.4 17.1 13.5 11.4 10.2 8.5 110 mm 6 “ 44.3 37.7 22.4 18.7 14.8 12.5 11.1 9.4

Reference: ANSI B58.1-1971, AWWA E101-71

It is assumed that the lineshafts are enclosed and lubricated with a drip-feed oiling system or water-flushed with bronze bearings spaced every 1.5 m. The table is also used for open, water-lubricated lineshafts where the standard bearings are synthetic rubber and spaced every 3 m.

If the shaft is protected with journals, resulting in larger bearing diameters, these diameters should be used when reading the chart.

For a system where the shaft is enclosed and the enclosing tube is flooded with oil, instead of drip-feed, twice the values given in the table are used.

All the mechanical friction values are interpolated from the original data point at which a loss of 1.5 hp / 100 ft is read for the shaft of diameter 2 1/2" running at 870 rpm by using following assumptions:

1) At a given shaft diameter, frictional loss is directly proportional with rotational speed.

2) At a given rotational speed, frictional loss is directly proportional with square of shaft diameter.

The first assumption is true and the errors associated with the second assumption are negligible.

These values represent approximate values valid for standard bearing lengths. If bearings with non-standard lengths are used, this table does not give correct results.


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COLUMN PIPE FRICTION LOSSES IN LINESHAFT PUMPS

Column Pipe Diameter — inch

3 4 5 6 Oil Pipe Diameter — inch

1 1/4 1 1/2 1 1/4 1 1/2 2 1 1/4 1 1/2 2 2 1/2 1 1/2 2 2 1/2 3

Friction Loss

m / 100 m Capacity — l/s

0.4 0.7 0.7 2.3 1.9 1.3 4.9 4.3 3.5 3.1 8.0 7.6 5.9 4.3 0.6 0.9 0.8 2.9 2.4 1.7 6.1 5.4 4.4 3.8 9.9 9.5 7.3 5.4 0.7 1.1 1.0 3.4 2.8 2.0 7.3 6.4 5.3 4.6 11.8 11.3 8.8 6.4 0.9 1.3 1.1 4.0 3.3 2.3 8.5 7.5 6.1 5.3 13.8 13.2 10.2 7.5 1.2 1.5 1.3 4.6 3.8 2.7 9.7 8.5 7.0 6.1 15.7 15.1 11.7 8.5 1.4 1.6 1.5 5.1 4.2 3.0 10.9 9.6 7.9 6.8 17.7 16.9 13.1 9.6 1.7 1.8 1.6 5.7 4.7 3.3 12.1 10.7 8.7 7.6 19.6 18.8 14.5 10.7 1.9 2.0 1.8 6.2 5.2 3.7 13.3 11.7 9.6 8.3 21.6 20.7 16.0 11.7 2.3 2.2 1.9 6.8 5.6 4.0 14.5 12.8 10.5 9.1 23.5 22.5 17.4 12.8 2.6 2.4 2.1 7.4 6.1 4.3 15.7 13.8 11.3 9.8 25.5 24.4 18.9 13.8 2.9 2.5 2.3 7.9 6.6 4.7 16.9 14.9 12.2 10.6 27.4 26.3 20.3 14.9 3.3 2.7 2.4 8.5 7.0 5.0 18.1 15.9 13.1 11.3 29.4 28.1 21.8 15.9 3.7 2.9 2.6 9.1 7.5 5.3 19.3 17.0 13.9 12.1 31.3 30.0 23.2 17.0 4.1 3.1 2.7 9.6 8.0 5.6 20.5 18.1 14.8 12.8 33.3 31.9 24.6 18.1 4.5 3.3 2.9 10.2 8.4 6.0 21.7 19.1 15.6 13.6 35.2 33.7 26.1 19.1 5.0 3.4 3.1 10.8 8.9 6.3 22.9 20.2 16.5 14.3 37.2 35.6 27.5 20.2 5.5 3.6 3.2 11.3 9.4 6.6 24.1 21.2 17.4 15.1 39.1 37.5 29.0 21.2 6.0 3.8 3.4 11.9 9.8 7.0 25.3 22.3 18.2 15.8 41.1 39.3 30.4 22.3 6.5 4.0 3.6 12.4 10.3 7.3 26.5 23.3 19.1 16.6 43.0 41.2 31.9 23.3 7.0 4.2 3.7 13.0 10.8 7.6 27.7 24.4 20.0 17.3 44.9 43.1 33.3 24.4

Column Pipe Diameter — inch

8 10 12 Oil Pipe Diameter — inch

1 1/2 2 2 1/2 3 2 2 1/2 3 4 5 2 2 1/2 3 4 5 6

Friction Loss

m / 100 m Capacity — l/s

0.4 23.3 17.2 16.2 13.2 35.7 32.9 30.4 23.3 17.2 58.9 55.4 51.1 43.7 35.7 30.4 0.6 29.0 21.4 20.1 16.4 44.4 41.0 37.9 29.0 21.4 73.3 69.0 63.6 54.5 44.4 37.9 0.7 34.6 25.6 24.1 19.7 53.2 49.0 45.3 34.6 25.6 87.8 82.5 76.1 65.2 53.2 45.3 0.9 40.3 29.8 28.0 22.9 61.9 57.1 52.7 40.3 29.8 102.2 96.1 88.6 75.9 61.9 52.7 1.2 46.0 34.0 32.0 26.1 70.6 65.2 60.2 46.0 34.0 116.6 109.7 101.1 86.6 70.6 60.2 1.4 51.7 38.2 35.9 29.4 79.4 73.2 67.6 51.7 38.2 131.0 123.2 113.7 97.3 79.4 67.6 1.7 57.4 42.4 39.9 32.6 88.1 81.3 75.1 57.4 42.4 145.5 136.8 126.2 108.0 88.1 75.1 1.9 63.1 46.7 43.8 35.8 96.9 89.3 82.5 63.1 46.7 159.9 150.4 138.7 118.7 96.9 82.5 2.3 68.8 50.9 47.8 39.1 105.6 97.4 90.0 68.8 50.9 174.3 163.9 151.2 129.4 105.6 90.0 2.6 74.5 55.1 51.8 42.3 114.3 105.5 97.4 74.5 55.1 188.8 177.5 163.7 140.2 114.3 97.4 2.9 80.2 59.3 55.7 45.6 123.1 113.5 104.9 80.2 59.3 203.2 191.1 176.2 150.9 123.1 104.9 3.3 85.9 63.5 59.7 48.8 131.8 121.6 112.3 85.9 63.5 217.6 204.6 188.7 161.6 131.8 112.3 3.7 91.6 67.7 63.6 52.0 140.6 129.6 119.8 91.6 67.7 232.0 218.2 201.3 172.3 140.6 119.8 4.1 97.3 71.9 67.6 55.3 149.3 137.7 127.2 97.3 71.9 246.5 231.8 213.8 183.0 149.3 127.2 4.5 103.0 76.1 71.5 58.5 158.0 145.8 134.7 103.0 76.1 260.9 245.3 226.3 193.7 158.0 134.7 5.0 108.7 80.3 75.5 61.7 166.8 153.8 142.1 108.7 80.3 275.3 258.9 238.8 204.4 166.8 142.1 5.5 114.4 84.5 79.4 65.0 175.5 161.9 149.6 114.4 84.5 289.7 272.5 251.3 215.2 175.5 149.6 6.0 120.1 88.8 83.4 68.2 184.3 169.9 157.0 120.1 88.8 304.2 286.0 263.8 225.9 184.3 157.0 6.5 125.8 93.0 87.4 71.4 193.0 178.0 164.4 125.8 93.0 318.6 299.6 276.3 236.6 193.0 164.4 7.0 131.5 97.2 91.3 74.7 201.7 186.1 171.9 131.5 97.2 333.0 313.2 288.9 247.3 201.7 171.9

Reference: Hydraulic Institute Engineering Data Book, 2nd edition, 1990

The table is directly used for oil lubricated columns. For water lubricated columns, the loss is assumed to be equal to an oil lubricated column with the proper oil tube that would normally enclose the lineshaft. Pipe material is steel.


Section xxx-Sx

Date Rev.

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FRICTION LOSSES IN STEEL PIPES

Pipe Diameter — inch 3 4 5 6 8 10 12 14 16 18 20

Friction Loss

m / 100 m Capacity — l/s 0.4 2.4 5.1 8.9 15.1 32.1 58.7 94.0 121.8 175.8 242.4 322.8 0.6 2.9 6.0 10.6 17.8 38.0 69.3 110.9 143.6 207.1 285.5 380.0 0.7 3.4 6.9 12.2 20.6 43.8 79.9 127.8 165.4 238.5 328.6 437.2 0.9 3.8 7.9 13.9 23.4 49.6 90.4 144.7 187.2 269.8 371.7 494.4 1.2 4.3 8.8 15.6 26.1 55.5 101.0 161.6 209.0 301.1 414.8 551.6 1.4 4.8 9.8 17.2 28.9 61.3 111.6 178.4 230.8 332.5 457.9 608.8 1.7 5.2 10.7 18.9 31.7 67.2 122.2 195.3 252.6 363.8 501.0 666.0 1.9 5.7 11.7 20.5 34.4 73.0 132.8 212.2 274.4 395.2 544.1 723.2 2.3 6.1 12.6 22.2 37.2 78.9 143.4 229.1 296.2 426.5 587.1 780.4 2.6 6.6 13.6 23.8 40.0 84.7 154.0 246.0 318.0 457.8 630.2 837.6 2.9 7.1 14.5 25.5 42.7 90.6 164.6 262.9 339.8 489.2 673.3 894.8 3.3 7.5 15.5 27.1 45.5 96.4 175.2 279.7 361.6 520.5 716.4 952.0 3.7 8.0 16.4 28.8 48.3 102.2 185.8 296.6 383.4 551.9 759.5 1009.2 4.1 8.5 17.3 30.4 51.0 108.1 196.4 313.5 405.2 583.2 802.6 1066.4 4.5 8.9 18.3 32.1 53.8 113.9 207.0 330.4 427.0 614.6 845.7 1123.6 5.0 9.4 19.2 33.8 56.6 119.8 217.5 347.3 448.8 645.9 888.8 1180.8 5.5 9.8 20.2 35.4 59.3 125.6 228.1 364.1 470.6 677.2 931.8 1238.0 6.0 10.3 21.1 37.1 62.1 131.5 238.7 381.0 492.4 708.6 974.9 1295.3 6.5 10.8 22.1 38.7 64.9 137.3 249.3 397.9 514.2 739.9 1018.0 1352.5 7.0 11.2 23.0 40.4 67.6 143.1 259.9 414.8 536.0 771.3 1061.1 1409.7



Section xxx-Sx

Date Rev.

08.02.2011 0

DISCHARGE HEAD LOSSES

Dis

char

ge H

ead

Loss

— m

10x4 10x5 10x610AC6

12AC817x8

17AC8

20AC12 25AC14

0.1

1

10 100 1000

Capacity — l/s



Section xxx-Sx

Date Rev.

08.02.2011 0

DISCHARGE ELBOW LOSSES

Dis

char

ge E

lbow

Los

s —

m

3'' 4'' 5'' 6'' 8''

0.1

1

10 100 1000

Capacity — l/s



Section xxx-Sx

Date Rev.

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DISCHARGE HEAD & COLUMN ASSEMBLY SECTIONAL VIEW (WATER LUBE)

Bearing RetainerLine Shaft Bearing

Snap RingWasherColumn Pipe Coupling

Upper Column Pipe

Column Flange

Discharge Head

Head ShaftPre-Lubrication Pipe

Head Shaft CouplingSetscrew

Key Motor Shaft CouplingSetscrew

Key

Motor

Deflector Ring

Column Pipe

Pressure Gage

Packing BoxPacking Box Bearing

SealLantern Ring

Grease CupDeflector Ring

GlandCopper Pipe

Non-Reverse Pin

Key

Sealing PipeThrust Bearing

Thrust Bearing CoverThrust Assembly Body

Oil Level Indicator

Drive CouplingPin Safety Plate

Adjusting Nut

Non-Reverse Plate

Intermediate Part

Pipe Plug


Section xxx-Sx

Date Rev.

08.02.2011 0

DISCHARGE HEAD & COLUMN ASSEMBLY SECTIONAL VIEW (OIL LUBE)

Head Shaft CouplingKeySetscrew

Motor Shaft Coupling KeySetscrew

Motor

Column Pipe Coupling

Line Shaft Bearing

Upper Column PipeColumn Flange

Discharge Head

Pipe Plug Head Shaft

Column PipeTube Stabilizer

Pressure Gage

Tube Connector BearingTube Connector

Tension Nut

Lock Nut

Pipe Bushing

Pipe Plug

Non-Reverse Pin

Key

Sealing PipeThrust Bearing

Thrust Bearing CoverThrust Assembly Body

Oil Level Indicator

Drive CouplingPin Safety Plate

Adjusting Nut

Non-Reverse Plate

Intermediate Part

Pipe Plug


Section xxx-Sx

Date Rev.

08.02.2011 0

BOWL ASSEMBLY SECTIONAL VIEW

Suction Pipe

Suction CaseSuction Case Bearing

Pipe Plug

Sand Collar

ImpellerImpeller Lock Collet

Bowl

Bowl Bearing

Bowl Rubber Bearing

Discharge Case

Discharge Case Bearing

Discharge Case Bearing CapPump Shaft

Pump Shaft Coupling

Wear Ring (Optional)

Conical Strainer

Column Pipe

Tube Adapter

Oil Tube

Deflector Ring

OIL LUBRICATED WATER LUBRICATED

Column Pipe

Pump Shaft Coupling

Pump Shaft

Suction Pipe

Suction CaseSuction Case Bearing

Pipe Plug

Sand Collar

ImpellerImpeller Lock Collet

Bowl

Bowl Bearing

Bowl Rubber Bearing

Discharge Case

Discharge Case Bearing

Wear Ring (Optional)

Conical Strainer


Section xxx-Sx

Date Rev.

08.02.2011 0

STANDARD MATERIALS FOR SUBMERSIBLE PUMPS

Item Nomenclature Material

1 Discharge Case Cast Iron ASTM A48 Class 30B

2 Check Valve Stainless Steel Sheet ASTM A582 Type 304

3 Rubber Seat Rubber Shore 70

4 Pump Shaft Stainless Steel ASTM A582 Type 420

5 Bolts and Nuts Steel ASTM A307-61 Gr. A

6 Intermediate Bowl Cast Iron ASTM A48 Class 30B

7 Impeller Leaded Red Bronze C83600

8 Impeller Lock Collet Stainless Steel ASTM A582 Type 420

9 Intermediate Bowl Bearing Leaded Red Bronze C83600

10 Suction Case Cast Iron ASTM A48 Class 30B

11 Strainer Stainless Steel Sheet ASTM A582 Type 304

12 Intermediate Part Cast Iron ASTM A48 Class 30B

13 Coupling Stainless Steel ASTM A582 Type 420

1

2 3

4 6

5

9

7

8

10 11

13 12


Section xxx-Sx

Date Rev.

08.02.2011 0

SHAFT DETAIL FOR LINESHAFT BOWLS

Bowl Shaft

Extension E – inch

Shaft Diameter

inch

1st Impeller Position A – mm

Single Stage Shaft Length

B – mm

Additional Stage Shaft Length

C – mm 6NT 248 1 110 602.5 91.5 6R 248 1 133 654 132

7NR 356 1 3/16 130.5 740 158 8R 356 1 3/16 143 848 165

8NF 356 1 3/16 177 896.5 178 10R 356 1 11/16 217.5 975 210 10JK 356 1 1/2 209.5 930 193.5 10FH 356 1 11/16 228.5 990 222.5 12R 356 1 15/16 217 1041 254

12FH 356 1 15/16 203 1048 279.5

Note: Subject to change without any notice.

A E

B

C


Section xxx-Sx

Date Rev.

08.02.2011 0

APPROXIMATE TORQUE REQUIREMENTS FOR METRIC BOLTS

Bolt

Designation Steel Gr. 1

AISI 304

AISI 316

Steel Gr. 5

Steel Gr. 8

M6 4 4 4 11 15 M8 8 8 8 20 31

M10 15 15 15 38 54 M12 38 38 38 95 134 M16 75 75 75 190 269 M20 132 132 132 339 475 M22 210 210 210 549 768 M24 312 312 312 814 1150 M27 461 461 461 1044 1689 M30 651 651 651 1465 2373 M33 895 895 895 1994 3221 M39 1166 1166 1166 2645 4252

Note: Torques in N-m


Section xxx-Sx

Date Rev.

08.02.2011 0

DIAMETRIC RUNNING CLEARANCES

Bronze Bowl Bearings

Nominal Shaft Diameter

Nominal Clearance

Range of Clearance

Max. Allowable Bearing I.D. Before Replacement

in mm mm mm mm 1 25.40 0.20 0.20 to 0.36 25.90

1 3/16 30.16 0.20 0.20 to 0.38 30.66 1 1/2 38.10 0.20 0.20 to 0.38 38.65

1 11/16 42.86 0.20 0.20 to 0.38 43.41 1 15/16 49.21 0.25 0.25 to 0.43 49.81

Impeller Skirt & Wear Ring

Nominal Shaft Diameter

Nominal Clearance

Range of Clearance

Max. Allowable Diametric Clearance Before

Replacement in mm mm mm mm

Less than 2 Less than 50.80 0.40 0.40 to 0.50 0.80 2.0 to 3.99 50.80 to 101.35 0.50 0.50 to 0.60 0.90 4.0 to 4.99 101.60 to 126.75 0.60 0.60 to 0.70 1.00 5.0 to 5.99 127.00 to 152.15 0.70 0.70 to 0.80 1.10 6.0 to 6.99 152.40 to 177.55 0.80 0.80 to 0.90 1.20

8.0 to 10.99 203.20 to 279.15 0.80 0.80 to 0.90 1.20 11.0 to 11.99 279.40 to 304.55 0.90 0.90 to 1.00 1.30 12.0 to 19.99 304.80 to 507.75 0.90 0.90 to 1.00 1.30 20.0 to 29.99 508.00 to 761.75 0.90 0.90 to 1.00 1.30


Section xxx-Sx

Date Rev.

08.02.2011 0

IMPELLER IDENTIFICATION

Impeller Maximum Diameter A – mm

Machining Angle

C – mm

Number Of

Vanes 6NTM 114.7 22.0 6

6RL 113.8 26.0 6 6RM 113.8 31.0 5 6RH 113.8 31.0 7 7NRL 144.9 31.0 6 8NRL 151.9 26.0 6 8RM 151.9 25.0 6 8RH 151.9 25.0 8

8NFM 162.4 31.0 5 10RL 199.6 25.0 5

10RM 199.6 25.0 6 10RH 199.6 25.0 7 10JKL 199.6 22.0 5 10JKM 199.6 22.0 8 10JKH 199.6 22.0 8

10JKXH 199.6 22.0 8 10FHM 204.2 40.0 5 10FHH 204.2 40.0 7 12RXL 235.8 30.0 6 12RL 235.8 25.0 5

12RM 235.8 25.0 6 12RH 235.8 25.0 8 12FHL 243.7 27.5 5

12FHM 243.7 27.0 4 12FHH 243.7 27.0 8

Note: Subject to change without any notice.


Section xxx-Sx

Date Rev.

08.02.2011 0

IMPELLER TRIM

The effect on hydraulic performance of a centrifugal pump due to speed change or impeller trim can be determined by the application of the formulae below. Different producers may use different formulae. These equations are theoretical and do not always give the same results as an actual test. However, for small changes in speed and small impeller trims, they serve as an excellent guide for calculating unknown performance characteristics from known values when test data are not available.

2 22 1

1 1

2 2

2 22 1

1 1

3 3

2 22 1

1 1

N DQ QN D

N DH HN D

N DP PN D

Subscript 1 represents known values and subscript 2 represents unknown values. Efficiency is assumed to remain the same for calculation purposes. Some variation may occur according to the amount of change or the design of the impellers and bowls.

It can be seen from above equations that when we make a diameter trim (which is at constant speed), power approximately changes with the cube of the diameter ratio, head approximately changes with the square of the diameter ratio and capacity approximately changes directly with the diameter ratio.

There are two things to consider when making an impeller trim:

1 – The impeller diameter is measured at the bottom shroud of the waterway as indicated on the drawing.

2 – Machining angle “C” is the same for trimmed impeller as the maximum diameter impeller.


Section xxx-Sx

Date Rev.

08.02.2011 0

BOWL AND LINESHAFT BEARING TEMPERATURE LIMITATIONS AND RECOMMENDATIONS

Material Temperature Range — °C Remarks

Synthetic Rubber ~ 0 to 40 Standard water lube lineshaft bearing. Do not use where H2S is present. Bearing must be wet prior to start-up for settings over 15 m.

Bronze ~ -2 to 50 Standard bowl bearing. General purpose bearing successfully applied on non-abrasive fresh water and hydro-carbons.

Teflon (Carbonized or Pure)

~ 0 to 150 Good for extreme temperature and non-abrasive fluids. Also excellent where fluid has poor lubricating properties.

Different materials with special machining tolerances can be used for other duties.


Section xxx-Sx

Date Rev.

08.02.2011 0

USE OF CHECK VALVES

It is recommended that one or more check valves are always be used in submersible pump installations. If the pump does not have a built-in check valve, a line check valve should be installed in the discharge line within 25 feet (7.6 m) of the pump and below the drawdown level of the water supply. For deeper settings, it is recommended that a line check valve be installed every 200 feet (61 m).

Swing type check valves should never be used with submersible pumps. When the pump stops, there is a sudden reversal of flow before the swing check valve closes, causing a sudden change in the velocity of the water. Spring loaded check valves should be used as they are designed to close quickly as the water flow stops and before it begins to move in the reverse direction. There is little or no velocity of flow when the spring loaded valve closes and no hydraulic shock or water hammer is produced by the closing of the valve.

Check valves are used to hold pressure in the system when the pump stops. They are also used to prevent backspin, water hammer and upthrust. Any of these three or a combination of them can lead to immediate pump or motor failure, a shortened service life or operating problems in the system.

a) Backspin – with no check valve or the check valve fails, the water in the drop pipe and the water in the system can flow back down the discharge pipe when the motor stops. This can cause the pump to rotate in a reverse direction as the water flows back down the pipe. If the motor is started while this is happening, a heavy strain may be placed across the pump-motor assembly. It can also cause excessive thrust bearing wear because the motor is not turning fast enough to ensure an adequate film of water in the thrust bearing.

b) Upthrust – with no check valve, or with a leaking check valve, the unit starts each time under zero head conditions. With most pumps, this causes an uplifting or upthrust on the impellers. This upward movement carries across the pump-motor coupling and creates an upthrust condition in the motor. Repeated upthrust at each start can cause premature wear and failure of either or both the pump and the motor.

c) Water Hammer – if the lowest check valve is more than 30 feet (9.1 m) above the standing water level or the lower check valve leaks and the check valve above holds, a partial vacuum is created in the discharge piping. On the next pump start, water moving at very high velocity fills the void and strikes the closed check valve and the stationary water in the pipe above it, causing a hydraulic shock. This shock can split pipes, break joints and damage the pump and/or motor. Water hammer is an easily detected noise. When discovered, the system be shut down and the pump installer contacted to correct the problem.


Section xxx-Sx

Date Rev.

08.02.2011 0

PRE-LUBRICATION RECOMMENDATIONS FOR OPEN LINESHAFT PUMPS

During operation, pumped water fills the column and lubricates the lineshaft bearings. However, at startup or shutdown special care must be taken to make sure that bearings are wetted never operates dry. Pre-lubrication of lineshaft bearings depend on pump type and column length.

d) Small pumps may have bottom check valve. In this case, pre-lubrication is necessary in the first startup. Generally pre-lubrication is not necessary in the later startups because the bottom check valve ensures that the column is filled with water.

e) A pre-lubrication tank with a 1 ¼” pipe and valve is installed after the check valve of the discharge line at the pump exit. Before the startup, valve of the pre-lubrication tank is opened and water flows to the column. After the pre-lubrication tank fills the column, pump can be operated. Valve of the pre-lubrication tank should be kept open until the pre-lubrication tank is filled again by the pump.

For different column pipe diameters and column lengths, below table is used to determine the size of the pre-lubrication tank.

Column 175 l 350 l 700 l 1000 l 3” 60 m 105 m 4” 45 m 90 m 6” 30 m 60 m 120 m 8” 45 m 105 m

10” 35 m 90 m 180 m

f) Non-reverse mechanisms should be used to prevent the back flow of the water through the pump when the pump is shut down. If there is no non-reverse mechanism, pre-lubrication should be done as explained before. Also make sure that when the pump is started there is no reverse rotation of the pump due to back flow of water. This may induce a very critical load to the driver. For low settings, non-reverse mechanisms may not be used.


Section xxx-Sx

Date Rev.

08.02.2011 0

WROUGHT STEEL GRADES

Tens

ile

Stre

ngth

<= 7

60

MPa

700

– 85

0 M

Pa

800

– 95

0 M

Pa

<= 7

30

MPa

650

– 85

0 M

Pa

500

– 70

0 M

Pa

500

– 70

0 M

Pa

460

– 68

0 M

Pa

500

– 70

0 M

Pa

Yiel

d St

reng

th

– 500

MPa

600

MPa

– 450

MPa

>= 2

00

MPa

>= 2

00

MPa

>= 1

80

MPa

>= 1

90

MPa

Har

dnes

s

<= 2

30

HB – –

<= 2

20

HB –

<= 2

15

HB

<= 2

15

HB

<= 2

15

HB

<= 2

15

HB

MEC

HA

NIC

AL

PRO

PERT

IES

Hea

t Tr

eatm

ent

A

Q&

T 65

0

Q&

T 65

0

A

Q&

T 65

0

SA

SA

SA

SA

Nİ – –

10.0

0 –

13.0

0

10.0

0 –

13.0

0

10.0

0 –

12.0

0

8.00

–

10.5

0

– –

Mo – <=

0.60

2.00

–

2.50

2.00

–

2.50

– – – –

Cr

12.0

0 –

14.0

0

12.0

0 –

14.0

0

16.5

0 –

18.5

0

16.5

0 –

18.5

0

18.0

0 –

20.0

0

17.0

0 –

19.5

0

– –

N

– – <=

0.11

<=

0.11

<=

0.11

<=

0.11

– –

S <=

0.03

0

0.15

–

0.35

<=

0.03

0

<=

0.03

0

<=

0.03

0

<=

0.03

0

<=

0.05

0

<=

0.05

0

P <=

0.04

0

<=

0.04

0

<=

0.04

5

<=

0.04

5

<=

0.04

5

<=

0.04

5

<=

0.03

0

<=

0.03

0

Mn

<=

1.50

<=

1.50

<=

2.00

<=

2.00

<=

2.00

<=

2.00

0.30

–

0.60

0.60

–

0.90

Si

<=

1.00

<=

1.00

<=

1.00

<=

1.00

<=

1.00

<=

1.00

– –

CHEM

ICA

L CO

MPO

SITI

ON

C

0.16

–

0.25

0.06

–

0.15

<=

0.03

0

<=

0.07

<=

0.03

0

<=

0.07

0.18

–

0.23

0.43

–

0.50

(~)

A 2

76–0

2 42

0

(~)

A 2

76–0

2 41

6

(~)

A 2

76–0

2 31

6L

(~)

A 2

76–0

2 31

6

(~)

A 2

76–0

2 30

4L

(~)

A 2

76–0

2 30

4

(REF

.) A

108

–99

1020

(REF

.) A

108

–99

1045

(~)

BS 9

70

420

S29

(~)

BS 9

70

416

S21

(~)

BS 9

70

316

S11

(~)

BS 9

70

316

S31

(~)

BS 9

70

304

S11

(~)

BS 9

70

304

S31

(~)

BS 9

70

055

M15

(~)

BS 9

70

080

M46

STA

ND

ARD

(REF

.) TS

EN

100

88–3

1.

4021

X2

0Cr1

3

(REF

.) TS

EN

100

88–3

1.

4005

X1

2CrS

13

(REF

.) TS

EN

100

88–3

1.

4404

X2

CrN

iMo1

7–12

–2

(REF

.) TS

EN

100

88–3

1.

4401

X5

CrN

iMo1

7–12

–2

(REF

.) TS

EN

100

88–3

1.

4306

X2

CrN

i19–

11

(REF

.) TS

EN

100

88–3

1.

4301

X5

CrN

i18–

10

(~)

TS E

N 1

0083

–2

1.04

02

C22

(~)

TS E

N 1

0083

–2

1.05

3 C4

5

DES

CRIP

TIO

N

Chro

miu

m

Stee

l

Chro

miu

m

Stee

l

Chro

miu

m N

icke

l M

olyb

denu

m

Stee

l Lo

w C

arbo

n

Chro

miu

m N

icke

l M

olyb

denu

m

Stee

l

Chro

miu

m N

icke

l St

eel

Low

Car

bon

Chro

miu

m N

icke

l St

eel

Carb

on S

teel

Carb

on S

teel

LAYN

E BO

WLE

R N

O.

S1

S2

S3

S4

S5

S6

S7

S8


Section xxx-Sx

Date Rev.

08.02.2011 0

CAST STEEL GRADES

Tens

ile

Stre

ngth

>= 3

80

MPa

Yiel

d St

reng

th

>= 2

00

MPa

Har

dnes

s

MEC

HA

NIC

AL

PRO

PERT

IES

Hea

t Tr

eatm

ent

Nİ

1.00

–

2.00

8.00

–

11.0

0

9.00

–

12.0

0

9.00

–

12.0

0

9.00

–

12.0

0

5.50

–

7.00

6.00

–

8.00

4.50

–

6.50

5.00

–

7.00

–

Mo

0.20

–

0.50

– –

2.00

–

2.50

2.00

–

2.50

2.50

–

3.50

3.00

–

5.00

2.50

–

3.50

2.50

–

3.50

–

Cu

– – – – – – <=

1.30

–

2.75

–

3.50

–

Cr

12.0

0 –

13.5

0

18.0

0 –

20.0

0

18.0

0 –

20.0

0

18.0

0 –

20.0

0

18.0

0 –

20.0

0

24.5

0 –

26.5

0

25.0

0 –

27.0

0

21.0

0 –

23.0

0

24.5

0 –

26.5

0

–

N

– – <=

0.20

0

– <=

0.20

0

0.12

0 –

0.25

0

0.12

0 –

0.22

0

0.12

0 –

0.20

0

0.12

0 –

0.22

0

–

S <=

0.02

5

<=

0.03

0

<=

0.02

5

<=

0.03

0

<=

0.02

5

<=

0.02

5

<=

0.02

5

<=

0.02

5

<=

0.02

5

<=

0.60

P <=

0.03

5

<=

0.04

0

<=

0.03

5

<=

0.04

0

<=

0.03

5

<=

0.03

5

<=

0.03

5

<=

0.03

5

<=

0.03

5

<=

0.05

0

Mn

<=

1.00

<=

1.50

<=

2.00

<=

1.50

<=

2.00

<=

2.00

<=

1.00

<=

2.00

<=

1.50

<=

0.60

Si

<=

1.00

<=

1.50

<=

1.50

<=

1.50

<=

1.50

<=

1.00

<=

1.00

<=

1.00

<=

1.00

<=

0.80

CHEM

ICA

L CO

MPO

SITI

ON

C <=

0.10

<=

0.07

<=

0.03

0

<=

0.07

<=

0.03

<=

0.03

<=

0.03

<=

0.03

<=

0.03

<=

0.30

(~)

A 3

51–0

0 CA

–15

(~)

A 3

51–0

0 CF

–8

(~)

A 3

51–0

0 CF

–3

(~)

A 3

51–0

0 CF

–8M

– – (~)

A 8

90–9

9 5A

(~)

A 8

90–9

9 4A

(~)

A 8

90–9

9 1B

(REF

.) A

27–

00

Gr

60–3

0

(~)

BS 3

100

410

C21

(~)

BS 3

100

304

C15

(~)

BS 3

100

304

C12

(~)

BS 3

100

316

C16

– – – – – (~)

BS 3

100

AM

1

STA

ND

ARD

(REF

.) TS

EN

102

83

1.40

08

GX7

CrN

iMo1

2–1

(REF

.) TS

EN

102

83

1.43

08

GX5

CrN

i19–

10

(REF

.) TS

EN

102

83

1.43

09

GX2

CrN

i19–

11

(REF

.) TS

EN

102

83

1.44

08

GX5

CrN

iMo1

9–11

–2

(REF

.) TS

EN

102

83

1.44

09

GX2

CrN

iMo1

9–11

–2

(REF

.) TS

EN

102

83

1.44

68

GX2

CrN

iMoN

25–6

–3

(REF

.) TS

EN

102

83

1.44

69

GX2

CrN

iMoN

26–7

–4

(REF

.) TS

EN

102

83

1.44

70

GX2

CrN

iMoN

22–5

–3

(REF

.) TS

EN

102

83

1.45

17

GX2

CrN

iMoC

uN25

–6–3

–3

(~)

DIN

168

1 G

S–38

G

E200

DES

CRIP

TIO

N

Chro

miu

m

Stee

l

Chro

miu

m N

icke

l St

eel

Chro

miu

m N

icke

l St

eel

Low

Car

bon

Chro

miu

m N

icke

l M

olyb

denu

m

Stee

l

Chro

miu

m N

icke

l M

olyb

denu

m

Stee

l Lo

w C

arbo

n

Dup

lex

Stai

nles

s St

eel

Dup

lex

Stai

nles

s St

eel

Dup

lex

Stai

nles

s St

eel

Dup

lex

Stai

nles

s St

eel

Carb

on S

teel

LAYN

E BO

WLE

R N

O.

S51

S52

S53

S54

S55

S56

S57

S58

S59

S60


Section xxx-Sx

Date Rev.

08.02.2011 0

CAST IRON GRADES

Tens

ile

Stre

ngth

>= 1

50

MPa

>= 2

00

MPa

>= 2

50

MPa

>= 3

00

MPa

>= 3

50

MPa

>= 4

12

MPa

>= 4

91

MPa

>= 5

89

MPa

>= 6

87

MPa

>= 4

00

MPa

>= 3

79

MPa

Yiel

d St

reng

th

>= 2

07

MPa

>= 2

07

MPa

Har

dnes

s

160

– 19

0 H

B

170

– 21

0 H

B

180

– 25

0 H

B

200

– 24

0 H

B

210

– 25

0 H

B

150

– 20

0 H

B

170

– 24

0 H

B

210

– 30

0 H

B

230

– 32

0 H

B

140

– 20

0 H

B

130

– 17

0 H

B

MEC

HA

NIC

AL

PRO

PERT

IES

Hea

t Tr

eatm

ent

Nİ – – – – – – – – –

18.0

0 –

22.0

0

28.0

0 –

32.0

0

Cu

– – – – – – –

0.60

–

0.80

0.60

–

0.80

<=

0.50

<=

0.50

Cr

– – – – – – – – –

1.00

–

3.50

2.50

–

3.50

S <=

0.12

<=

0.12

<=

0.12

<=

0.10

<=

0.10

<=

0.04

<=

0.04

<=

0.04

<=

0.04

– –

P <=

0.50

<=

0.40

<=

0.25

<=

0.20

<=

0.20

<=

0.08

<=

0.08

<=

0.08

<=

0.08

<=

0.08

0

<=

0.08

0

Mn

0.50

–

0.80

0.50

–

0.80

0.40

–

0.70

0.40

–

0.70

0.60

–

0.80

0.05

–

0.20

0.30

–

0.50

0.30

–

0.40

0.30

–

0.50

0.50

–

1.50

0.50

–

1.50

Si

2.30

–

2.50

2.10

–

2.30

1.85

–

2.10

1.70

–

2.00

1.70

–

2.00

2.20

–

2.90

2.20

–

2.90

2.20

–

2.90

2.20

–

2.90

0.50

–

1.50

0.50

–

1.50

CHEM

ICA

L CO

MPO

SITI

ON

C

3.40

–

3.60

3.20

–

3.40

3.00

–

3.25

2.95

–

3.10

3.00

–

3.26

3.40

–

3.80

3.40

–

3.80

3.40

–

3.80

3.40

–

3.80

<=

3.00

<=

2.60

(~)

A 4

8–00

G

r 25

B

(~)

A 4

8–00

G

r 30

B

(~)

A 4

8–00

G

r 40

B

(~)

A 4

8–00

G

r 45

B

(~)

A 4

8–00

G

r 50

B

(~)

A 5

36–8

4 60

–40–

18

(~)

A 5

36–8

4 60

–45–

12

(~)

A 5

36–8

4 80

–55–

06

(~)

A 5

36–8

4 10

0–70

–03

(~)

A 4

39–8

3 Ty

pe D

–2

(~)

A 4

39–8

3 Ty

pe D

–3

(~)

BS 1

452

Gr

150

(~)

BS 1

452

Gr

220

(~)

BS 1

452

Gr

260

(~)

BS 1

452

Gr

300

(~)

BS 1

452

Gr

350

(~)

BS 2

789

Gr

420/

12

(~)

BS 2

789

Gr

500/

7

(~)

BS 2

789

Gr

600/

3

(~)

BS 2

789

Gr

700/

2

(~)

BS 3

468

S-N

iCr2

0–2

(~)

BS 3

468

S-N

iCr3

0–3

STA

ND

ARD

(REF

.) TS

EN

156

1 0.

6015

G

G–1

5 (R

EF.)

TS E

N 1

561

0.60

20

GG

–20

(REF

.) TS

EN

156

1 0.

6025

G

G–2

5 (R

EF.)

TS E

N 1

561

0.60

30

GG

–30

(REF

.) TS

EN

156

1 0.

6035

G

G–3

5 (R

EF.)

TS E

N 1

563

0.70

40

GG

G–4

0 (R

EF.)

TS E

N 1

563

0.70

50

GG

G–5

0 (R

EF.)

TS E

N 1

563

0.70

60

GG

G–6

0 (R

EF.)

TS E

N 1

563

0.70

70

GG

G–7

0 (R

EF.)

TS E

N 1

3835

0.

7660

G

GG

-NiC

r 20

2

(REF

.) TS

EN

138

35

0.76

76

GG

G-N

iCr

30 3

DES

CRIP

TIO

N

Gre

y Ca

st Ir

on

Gre

y Ca

st Ir

on

Gre

y Ca

st Ir

on

Gre

y Ca

st Ir

on

Gre

y Ca

st Ir

on

Duc

tile

Iron

Duc

tile

Iron

Duc

tile

Iron

Duc

tile

Iron

Ni–

Resi

st

Ni–

Resi

st

LAYN

E BO

WLE

R N

O.

C1

C2

C3

C4

C5

C6

C7

C8

C9

C51

C52


Section xxx-Sx

Date Rev.

08.02.2011 0

COPPER ALLOYS

Te

nsile

St

reng

th

Yiel

d St

reng

th

Har

dnes

s

MEC

HA

NIC

AL

PRO

PERT

IES

Hea

t Tr

eatm

ent

Oth

er

– – – – – <=

1.0

<=

1.0

Mn – – – <=

0.5

0.8 – 1.5 – –

Si

<=

0.00

5

<=

0.00

5

<=

0.00

5

– <=

0.1 – –

Al

<=

0.00

5

<=

0.00

5

<=

0.00

5

10.0

–

11.5

8.5 – 9.5 – –

P <=

0.05

<=

0.25

<=

0.05

– – – –

S <=

0.08

<=

0.05

<=

0.05

– – – –

Ni

<=

1.0

<=

1.0

<=

0.8

<=

1.5

4.0 – 5.0

<=

2.0

<=

2.0

Sb

<=

0.25

<=

0.25

<=

0.20

– – – –

Fe

<=

0.30

<=

0.20

<=

0.25

3.0 – 5.0

3.5 – 4.5

<=

1.0

<=

1.0

Zn

4.0 – 6.0

<=

0.7

<=

0.50

– – <=

6.0

<=

3.0

Pb

4.0 – 6.0

1.0 – 2.5

<=

0.30

– <=

0.09

<=

6.0

9.0 –

15.0

Sn

4.0 – 6.0

9.0 –

11.0

9.2 –

11.0

– – 4.0 –

11.0

4.0 –

10.0

CHEM

ICA

L CO

MPO

SITI

ON

Cu

84.0

–

86.0

86.0

–

89.0

89.0

–

91.0

>=

83.0

>=

79.0

80.0

–

90.0

73.0

–

87.0

STA

ND

ARD

AST

M

C836

00

AST

M

C927

00

AST

M

C902

50

AST

M

C954

00

AST

M

C958

00

– –

Bz 8

5–5–

5–5

Bz 8

8–10

–2

Bz 9

0–10

Bz–A

l

Bz–A

l–N

i

DES

CRIP

TIO

N

Lead

ed R

ed

Bron

ze

Lead

ed T

in

Bron

ze

Tin

Bron

ze

Alu

min

um

Bron

ze

Alu

min

um n

icke

l Br

onze

Impe

ller m

ater

ial f

or D

SI.

Bear

ing

mat

eria

l for

DSI

.

LAYN

E B

OW

LER

N

O.

B1

B2

B3

B4

B5

B50

B51

Documents

TECHNICAL Layne Engineering Manual