GENERAL ENGINEERING MANUAL...Performance curves are plotted from data obtained in our hydraulic test...
Transcript of GENERAL ENGINEERING MANUAL...Performance curves are plotted from data obtained in our hydraulic test...
TRAINING DOCUMENT
GENERAL
ENGINEERING
MANUAL
LAYNE BOWLER PUMP CO.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
08.02.2011 0
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
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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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
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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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
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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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
08.02.2011 0
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 %
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
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VERTICAL TURBINE PUMP TERMINOLOGY
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
08.02.2011 0
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)
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
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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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Section xxx-Sx
Date Rev.
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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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Section xxx-Sx
Date Rev.
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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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
08.02.2011 0
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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
08.02.2011 0
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
Reference: Hydraulic Institute Engineering Data Book, 2nd edition, 1990
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
Reference: Hydraulic Institute Engineering Data Book, 2nd edition, 1990
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
Reference: Hydraulic Institute Engineering Data Book, 2nd edition, 1990
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
Section xxx-Sx
Date Rev.
08.02.2011 0
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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.
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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
LAYNE BOWLER PUMP CO. GENERAL ENGINEERING MANUAL
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