Layne Bowler Pump Engineering Brochure

Transcription

TRAINING DOCUMENT
GENERAL
ENGINEERING
MANUAL
LAYNE BOWLER PUMP CO.
Section
xxx-Sx
GENERAL ENGINEERING MANUAL
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
Section
xxx-Sx
Date
Rev.
08.02.2011
0
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.
Section
xxx-Sx
Date
Rev.
08.02.2011
0
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
2. Well depth
3. Static water level
4. Drawdown (at 60 l/s)
5. Dynamic water level (pumping water level)
6. Geometric head (lift above well head)
7. Discharge Line Losses (after discharge head)
8. Velocity Head
9. Total pump head (TPH) (sum of items 5, 6, 7 and 8)
10. Pump capacity
11. Quality of water
12. Current available
13 ½ inches
100 m
30 m
20 m
50 m
50 m
2.5 m
0.5 m
103 m
60 l/s
Sand-free, non-corrosive, 20°C, Sp. Gr. 1.0
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
10RL
10RM
10RH
Head/Stage
32.5 m
35.0 m
38.5 m
Bowl. Eff.
79.7 %
80.0 %
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:
103
 2.9 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.
Section
xxx-Sx
Date
Rev.
08.02.2011
0
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:
HT  105  12.41  1300 kg hydraulic downthrust
Hence, 1 3/16” AISI 420 shaft is selected regarding these data and the shaft friction loss is calculated as:
kWL  2.8  2 
55
 3.1 kW
100
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:
hC  3.18 
55
 1.75 m
100
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:
TBH  TPH  hC  hDH  103  1.75  0.14  104.89  105 m
This head fall exactly on 10RM 3 stages bowl assembly curve so no impeller trim is required. Pump power is now calculated as:
kWP 
Q  l / s   TBH  m 
1.02   B
 kWL 
60  105
 3.1  80.2 kW
1.02  80.0
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.
Section
xxx-Sx
SUMMARY OF CALCULATIONS
1
2
3
4
5
6
7
8
Specified Conditions @ 2980 RPM
Capacity
Static Water Level
Drawdown
Dynamic Water Level (sum of 2 and 3)
Geometric Head
Discharge Line Losses
Velocity Head
Total Pump Head (sum of 4, 5, 6 and 7)
60
30
20
50
50
2.5
0.5
103
l/s
m
m
m
m
m
m
m
1.75
0.14
105
61.8
80.0
77.1
3.1
300
1300
1600
0
80.2
76.9
92.5
86.7
71.1
m
m
m
kW
%
kW
kW
kg
kg
kg
kW
kW
%
%
kW
%
Calculated Values
9
10
11
12
13
14
15
16
17
18
19
20
21
22
23
24
Column Friction Loss
Discharge Head Loss
Total Bowl Head (sum of 8, 9 and 10)
Water Power
Bowl Efficiency
Bowl Power
Lineshaft Friction Loss
Shaft and Impeller Weight
Hydraulic Thrust
Total Pump Thrust (sum of 15 and 16)
Thrust Bearing Loss (neglected)
Pump Power (sum of 13, 14 and 18)
Pump Efficiency
Motor Efficiency
Wire Power (input power)
Overall Efficiency (wire to water)
Date
Rev.
08.02.2011
0
VERTICAL TURBINE PUMP TERMINOLOGY
Section
xxx-Sx
Date
Rev.
08.02.2011
0
1.
Section
xxx-Sx
Date
Rev.
08.02.2011
0
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.
Section
xxx-Sx
Date
Rev.
08.02.2011
0
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.
USEFUL FORMULAE
  kg / m3   g  m / s 2   Q  m3 / s   H  m 
PW 
1000
Q l / s   H  m
PW 
PB 
102
PW
B
PP  PB  PLF  PTF
P 
PW
PP
PI 
PP
3  V  I  PF

M
746
PW
PI
O 
where
Q
:
Capacity
H
:
Total Bowl Head in m
N
:
Rotational Speed in rpm
PW :
Water Power in kW
PB
:
Bowl Power in kW
PL
:
Lineshaft friction losses in kW
PT
:
Thrust bearing loss in kW
PP
:
Pump Power in kW
PI
:
Wire (input) Power in kW
ηB
:
Bowl Efficiency (read from performance curves)
ηP
:
Pump Efficiency
ηM :
Motor Efficiency
ηO
:
Overall Efficiency
V
:
Voltage per leg applied to motor
I
:
Current per leg applied to motor
PF :
Power factor of the motor (CosØ)
Section
xxx-Sx
Date
Rev.
08.02.2011
0
Section
xxx-Sx
Date
Rev.
08.02.2011
0
UNIT CONVERSION TABLE
Pressure
atmosphere
bar
kilopascal
kilogram-force / centimeter square
meter water column
pound-force/inch square
atm
1
0.98692
0.00987
0.96784
0.09678
0.06805
bar
1.01325
1
0.01
0.98067
0.09806
0.06895
kPa
101.325
100
1
98.0665
9.80638
6.89476
kgf/cm²
1.03323
1.01972
0.01020
1
0.10000
0.07031
mWC
10.33256
10.19744
0.10197
10.00028
1
0.70309
psi
14.69594
14.50377
0.14504
14.22334
1.42229
1
Capacity
liter/second
cubic meter/second
cubic meter/hour
liter/minute
gallon/minute (US)
gallon/minute (GB)
l/s
1
1000
3.6
0.01667
0.06309
0.07577
m³/s
0.001
1
0.0036
1.67E-05
6.31E-05
7.58E-05
m³/h
0.27778
277.77778
1
0.00463
0.01753
0.02105
l/min
60
60000
216
1
3.78541
4.54609
gpm (US)
15.85032
15850
57.06116
0.26417
1
1.20095
gpm (GB)
13.19815
13198
47.51334
0.21997
0.83267
1
Length
millimeter
meter
inch
foot
yard
mm
1
1000
25.4
304.8
914.4
m
0.001
1
0.0254
0.3048
0.9144
in
0.03937
39.37008
1
12
36
ft
0.00328
3.28084
0.08333
1
3
yd
0.00109
1.09361
0.02778
0.33333
1
Area
millimeter square
meter square
inch square
foot square
yard square
mm²
1
1000000
645.16
92903.04
836127.36
m²
0.000001
1
0.00065
0.09290
0.83613
in²
0.00155
1550.0031
1
144
1296
ft²
1.08E-05
10.76391
0.00694
1
9
yd²
1.20E-06
1.19599
0.00077
0.11111
1
Volume
liter
cubic meter
inch cube
foot cube
yard cube
l
1
1000
0.01639
28.31685
764.55486
m³
0.001
1
1.64E-05
0.02832
0.76455
in³
61.02374
61023.74409
1
1728
46656
ft³
0.03531
35.31467
0.00058
1
27
yd³
0.00131
1.30795
2.14E-05
0.03704
1
Rotational Speed
radian/second
radian/minute
revolution/second
revolution/minute
rad/s
1
0.01667
6.28319
0.10472
rad/min
60
1
376.99112
6.28319
rps
0.15915
0.00265
1
0.01667
rpm
9.54930
0.15915
60
1
Power
watt
kilowatt
horsepower
W
1
1000
746
kW
0.001
1
0.746
hp
0.00134
1.34048
1
Mass
kilogram
pound
ounce
kg
1
0.45359
0.02835
lb
2.20462
1
0.0625
oz
35.27396
16
1
Force
kilogram-force
Newton
pound-force
kgf
1
0.10197
0.45359
N
9.80665
1
4.44822
lbf
2.20462
0.22481
1
Section
xxx-Sx
Date
Rev.
08.02.2011
0
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.
Pipe
Diameter
inch
3
4
5
6
8
10
12
250
300
350
400
450
500
4.6
8.1
12.7
18.3
32.6
50.9
73.3
5.5
9.8
15.3
22.0
39.1
61.1
88.0
6.4
11.4
17.8
25.7
45.6
71.3
102.7
7.3
13.0
20.4
29.3
52.1
81.5
117.3
8.2
14.7
22.9
33.0
58.7
91.7
132.0
9.2
16.3
25.5
36.7
65.2
101.8
146.7
D — mm
550
600
650
700
Approximate Capacity — l/s
10.1
11.0
11.9
12.8
17.9
19.6
21.2
22.8
28.0
30.6
33.1
35.6
40.3
44.0
47.7
51.3
71.7
78.2
84.7
91.3
112.0 122.2 132.4 142.6
161.3 176.0 190.7 205.3
750
800
850
900
950
1000
13.7
24.4
38.2
55.0
97.8
152.8
220.0
14.7
26.1
40.7
58.7
104.3
163.0
234.7
15.6
27.7
43.3
62.3
110.8
173.1
249.3
16.5
29.3
45.8
66.0
117.3
183.3
264.0
17.4
31.0
48.4
69.7
123.8
193.5
278.6
18.3
32.6
50.9
73.3
130.4
203.7
293.3
Section
xxx-Sx
Date
Rev.
08.02.2011
0
LINESHAFT SELECTION TABLE
AISI 420
Diameter Speed
inch
rpm
2980
1480
3/4
990
740
2980
1480
1
990
740
2980
1480
1 3/16
990
740
2980
1480
1 1/2
990
740
2980
1480
1 11/16
990
740
2980
1480
1 15/16
990
740
AISI 1045
Diameter Speed
inch
rpm
2980
1480
3/4
990
740
2980
1480
1
990
740
2980
1480
1 3/16
990
740
2980
1480
1 1/2
990
740
2980
1480
1 11/16
990
740
2980
1480
1 15/16
990
740
500
1000
1500
2000
30.0
14.9
10.0
7.5
71.5
35.5
23.8
17.8
119.9
59.5
39.8
29.8
241.8
120.1
80.3
60.0
382.6
190.0
127.1
95.0
579.2
287.6
192.4
143.8
29.3
14.6
9.7
7.3
71.0
35.3
23.6
17.6
119.5
59.3
39.7
29.7
241.5
119.9
80.2
60.0
382.4
189.9
127.0
95.0
579.0
287.5
192.3
143.8
28.2
14.0
9.4
7.0
70.2
34.9
23.3
17.4
118.8
59.0
39.5
29.5
240.9
119.7
80.0
59.8
381.9
189.7
126.9
94.8
578.6
287.3
192.2
143.7
26.5
13.2
8.8
6.6
69.0
34.3
22.9
17.1
117.8
58.5
39.1
29.2
240.2
119.3
79.8
59.6
381.3
189.4
126.7
94.7
578.0
287.1
192.0
143.5
500
1000
1500
2000
26.0
12.9
8.7
6.5
62.1
30.9
20.6
15.4
104.2
51.8
34.6
25.9
210.2
104.4
69.8
52.2
332.7
165.2
110.5
82.6
503.6
250.1
167.3
125.1
25.3
12.5
8.4
6.3
61.6
30.6
20.5
15.3
103.7
51.5
34.5
25.8
209.9
104.2
69.7
52.1
332.4
165.1
110.4
82.5
503.4
250.0
167.2
125.0
23.9
11.9
7.9
5.9
60.6
30.1
20.1
15.0
102.9
51.1
34.2
25.6
209.2
103.9
69.5
52.0
331.9
164.8
110.3
82.4
502.9
249.8
167.1
124.9
21.9
10.9
7.3
5.4
59.2
29.4
19.7
14.7
101.8
50.6
33.8
25.3
208.3
103.5
69.2
51.7
331.2
164.5
110.0
82.2
502.3
249.5
166.9
124.7
Thrust Load — kg
3000
4000
5000
6000
7500
9000
Maximum Transmissible Horsepower — kW
20.9
8.0
10.4
4.0
6.9
2.7
5.2
2.0
65.5
60.2
52.7
41.7
32.5
29.9
26.2
20.7
21.8
20.0
17.5
13.8
16.3
15.0
13.1
10.3
114.9 110.8 105.2
98.0
83.1
60.1
57.1
55.0
52.3
48.7
41.3
29.9
38.2
36.8
35.0
32.6
27.6
20.0
28.5
27.5
26.1
24.3
20.6
14.9
237.9 234.8 230.7 225.5 215.8 203.2
118.2 116.6 114.6 112.0 107.2 100.9
79.0
78.0
76.6
74.9
71.7
67.5
59.1
58.3
57.3
56.0
53.6
50.5
379.5 377.1 373.8 369.8 362.4 353.1
188.5 187.3 185.7 183.7 180.0 175.4
126.1 125.3 124.2 122.9 120.4 117.3
94.2
93.6
92.8
91.8
90.0
87.7
576.5 574.3 571.6 568.1 561.8 553.9
286.3 285.2 283.9 282.2 279.0 275.1
191.5 190.8 189.9 188.7 186.6 184.0
143.2 142.6 141.9 141.1 139.5 137.5
Thrust Load — kg
3000
4000
5000
6000
7500
9000
Maximum Transmissible Horsepower — kW
14.6
7.3
4.9
3.6
55.1
48.7
39.0
22.0
27.4
24.2
19.4
10.9
18.3
16.2
13.0
7.3
13.7
12.1
9.7
5.5
98.5
93.6
87.0
78.1
58.3
10.1
48.9
46.5
43.2
38.8
29.0
5.0
32.7
31.1
28.9
25.9
19.4
3.4
24.5
23.2
21.6
19.4
14.5
2.5
205.8 202.1 197.3 191.3 179.7 164.4
102.2 100.4
98.0
95.0
89.3
81.7
68.4
67.1
65.6
63.6
59.7
54.6
51.1
50.2
49.0
47.5
44.6
40.8
329.1 326.3 322.5 317.9 309.2 298.3
163.5 162.0 160.2 157.9 153.6 148.1
109.3 108.4 107.2 105.6 102.7
99.1
81.7
81.0
80.1
78.9
76.8
74.1
500.5 498.0 494.8 490.9 483.5 474.3
248.6 247.3 245.8 243.8 240.1 235.6
166.3 165.5 164.4 163.1 160.6 157.6
124.3 123.7 122.9 121.9 120.1 117.8
Reference: ANSI B58.1-1971, AWWA E101-71
Note: At a given thrust load, maximum transmissible power is directly proportional with speed.
10500
12000
15000
20000
187.3
93.0
62.2
46.5
341.8
169.7
113.5
84.9
544.5
270.4
180.9
135.2
167.1
83.0
55.5
41.5
328.2
163.0
109.0
81.5
533.4
264.9
177.2
132.4
103.4
51.4
34.4
25.7
293.2
145.6
97.4
72.8
505.7
251.2
168.0
125.6
197.1
97.9
65.5
48.9
440.1
218.6
146.2
109.3
10500
12000
15000
20000
144.3
71.7
47.9
35.8
284.8
141.4
94.6
70.7
463.3
230.1
153.9
115.0
116.8
58.0
38.8
29.0
268.4
133.3
89.2
66.6
450.2
223.6
149.6
111.8
224.1
111.3
74.4
55.6
417.0
207.1
138.5
103.6
56.0
27.8
18.6
13.9
334.4
166.1
111.1
83.1
Section
xxx-Sx
Date
Rev.
08.02.2011
0
MECHANICAL FRICTION IN LINESHAFT BEARINGS
Shaft
Diameter
Oil Pipe
Diameter
3500
2980
3/4 “
1“
1 3/16 “
1 1/2 “
1 11/16 “
1 15/16 “
55 mm
60 mm
65 mm
70 mm
75 mm
80 mm
85 mm
90 mm
95 mm
100 mm
105 mm
110 mm
1 1/4 “
1 1/2 “
2“
2 1/2 “
3“
3“
4”
4“
4“
5“
5“
5“
5“
5“
6“
6“
6“
6“
1.3
2.4
3.3
5.3
6.7
8.9
11.1
13.2
15.5
17.9
20.6
23.4
26.5
29.7
33.1
36.6
40.4
44.3
1.1
2.0
2.8
4.5
5.7
7.6
9.4
11.2
13.2
15.3
17.5
20.0
22.5
25.3
28.1
31.2
34.4
37.7
Rotational Speed — rpm
1770
1480
1170
Mechanical Friction — kW / 100 m
0.7
0.6
0.4
1.2
1.0
0.8
1.7
1.4
1.1
2.7
2.2
1.8
3.4
2.8
2.2
4.5
3.8
3.0
5.6
4.7
3.7
6.7
5.6
4.4
7.8
6.5
5.2
9.1
7.6
6.0
10.4
8.7
6.9
11.9
9.9
7.8
13.4
11.2
8.8
15.0
12.5
9.9
16.7
14.0
11.1
18.5
15.5
12.2
20.4
17.1
13.5
22.4
18.7
14.8
990
880
740
0.4
0.7
0.9
1.5
1.9
2.5
3.1
3.7
4.4
5.1
5.8
6.6
7.5
8.4
9.4
10.4
11.4
12.5
0.3
0.6
0.8
1.3
1.7
2.2
2.8
3.3
3.9
4.5
5.2
5.9
6.7
7.5
8.3
9.2
10.2
11.1
0.3
0.5
0.7
1.1
1.4
1.9
2.3
2.8
3.3
3.8
4.4
5.0
5.6
6.3
7.0
7.7
8.5
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.
Section
xxx-Sx
Date
Rev.
08.02.2011
0
COLUMN PIPE FRICTION LOSSES IN LINESHAFT PUMPS
3
4
Friction
Loss
m / 100 m
1 1/4
1 1/2
1 1/4
1 1/2
2
0.4
0.6
0.7
0.9
1.2
1.4
1.7
1.9
2.3
2.6
2.9
3.3
3.7
4.1
4.5
5.0
5.5
6.0
6.5
7.0
0.7
0.9
1.1
1.3
1.5
1.6
1.8
2.0
2.2
2.4
2.5
2.7
2.9
3.1
3.3
3.4
3.6
3.8
4.0
4.2
0.7
0.8
1.0
1.1
1.3
1.5
1.6
1.8
1.9
2.1
2.3
2.4
2.6
2.7
2.9
3.1
3.2
3.4
3.6
3.7
2.3
2.9
3.4
4.0
4.6
5.1
5.7
6.2
6.8
7.4
7.9
8.5
9.1
9.6
10.2
10.8
11.3
11.9
12.4
13.0
1.9
2.4
2.8
3.3
3.8
4.2
4.7
5.2
5.6
6.1
6.6
7.0
7.5
8.0
8.4
8.9
9.4
9.8
10.3
10.8
1.3
1.7
2.0
2.3
2.7
3.0
3.3
3.7
4.0
4.3
4.7
5.0
5.3
5.6
6.0
6.3
6.6
7.0
7.3
7.6
8
Friction
Loss
m / 100 m
1 1/2
2
2 1/2
3
2
0.4
0.6
0.7
0.9
1.2
1.4
1.7
1.9
2.3
2.6
2.9
3.3
3.7
4.1
4.5
5.0
5.5
6.0
6.5
7.0
23.3
29.0
34.6
40.3
46.0
51.7
57.4
63.1
68.8
74.5
80.2
85.9
91.6
97.3
103.0
108.7
114.4
120.1
125.8
131.5
17.2
21.4
25.6
29.8
34.0
38.2
42.4
46.7
50.9
55.1
59.3
63.5
67.7
71.9
76.1
80.3
84.5
88.8
93.0
97.2
16.2
20.1
24.1
28.0
32.0
35.9
39.9
43.8
47.8
51.8
55.7
59.7
63.6
67.6
71.5
75.5
79.4
83.4
87.4
91.3
13.2
16.4
19.7
22.9
26.1
29.4
32.6
35.8
39.1
42.3
45.6
48.8
52.0
55.3
58.5
61.7
65.0
68.2
71.4
74.7
35.7
44.4
53.2
61.9
70.6
79.4
88.1
96.9
105.6
114.3
123.1
131.8
140.6
149.3
158.0
166.8
175.5
184.3
193.0
201.7
Column Pipe Diameter — inch
5
Oil Pipe Diameter — inch
1 1/4 1 1/2
2
2 1/2
Capacity — l/s
4.9
4.3
3.5
3.1
6.1
5.4
4.4
3.8
7.3
6.4
5.3
4.6
8.5
7.5
6.1
5.3
9.7
8.5
7.0
6.1
10.9
9.6
7.9
6.8
12.1
10.7
8.7
7.6
13.3
11.7
9.6
8.3
14.5
12.8
10.5
9.1
15.7
13.8
11.3
9.8
16.9
14.9
12.2
10.6
18.1
15.9
13.1
11.3
19.3
17.0
13.9
12.1
20.5
18.1
14.8
12.8
21.7
19.1
15.6
13.6
22.9
20.2
16.5
14.3
24.1
21.2
17.4
15.1
25.3
22.3
18.2
15.8
26.5
23.3
19.1
16.6
27.7
24.4
20.0
17.3
6
1 1/2
2
2 1/2
3
8.0
9.9
11.8
13.8
15.7
17.7
19.6
21.6
23.5
25.5
27.4
29.4
31.3
33.3
35.2
37.2
39.1
41.1
43.0
44.9
7.6
9.5
11.3
13.2
15.1
16.9
18.8
20.7
22.5
24.4
26.3
28.1
30.0
31.9
33.7
35.6
37.5
39.3
41.2
43.1
5.9
7.3
8.8
10.2
11.7
13.1
14.5
16.0
17.4
18.9
20.3
21.8
23.2
24.6
26.1
27.5
29.0
30.4
31.9
33.3
4.3
5.4
6.4
7.5
8.5
9.6
10.7
11.7
12.8
13.8
14.9
15.9
17.0
18.1
19.1
20.2
21.2
22.3
23.3
24.4
Column Pipe Diameter — inch
10
Oil Pipe Diameter — inch
2 1/2
3
4
5
2
Capacity — l/s
32.9
30.4
23.3
17.2
58.9
41.0
37.9
29.0
21.4
73.3
49.0
45.3
34.6
25.6
87.8
57.1
52.7
40.3
29.8
102.2
65.2
60.2
46.0
34.0
116.6
73.2
67.6
51.7
38.2
131.0
81.3
75.1
57.4
42.4
145.5
89.3
82.5
63.1
46.7
159.9
97.4
90.0
68.8
50.9
174.3
105.5
97.4
74.5
55.1
188.8
113.5 104.9
80.2
59.3
203.2
121.6 112.3
85.9
63.5
217.6
129.6 119.8
91.6
67.7
232.0
137.7 127.2
97.3
71.9
246.5
145.8 134.7 103.0
76.1
260.9
153.8 142.1 108.7
80.3
275.3
161.9 149.6 114.4
84.5
289.7
169.9 157.0 120.1
88.8
304.2
178.0 164.4 125.8
93.0
318.6
186.1 171.9 131.5
97.2
333.0
12
2 1/2
3
4
5
6
55.4
69.0
82.5
96.1
109.7
123.2
136.8
150.4
163.9
177.5
191.1
204.6
218.2
231.8
245.3
258.9
272.5
286.0
299.6
313.2
51.1
63.6
76.1
88.6
101.1
113.7
126.2
138.7
151.2
163.7
176.2
188.7
201.3
213.8
226.3
238.8
251.3
263.8
276.3
288.9
43.7
54.5
65.2
75.9
86.6
97.3
108.0
118.7
129.4
140.2
150.9
161.6
172.3
183.0
193.7
204.4
215.2
225.9
236.6
247.3
35.7
44.4
53.2
61.9
70.6
79.4
88.1
96.9
105.6
114.3
123.1
131.8
140.6
149.3
158.0
166.8
175.5
184.3
193.0
201.7
30.4
37.9
45.3
52.7
60.2
67.6
75.1
82.5
90.0
97.4
104.9
112.3
119.8
127.2
134.7
142.1
149.6
157.0
164.4
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.
08.02.2011
0
FRICTION LOSSES IN STEEL PIPES
Friction
Loss
m / 100 m
0.4
0.6
0.7
0.9
1.2
1.4
1.7
1.9
2.3
2.6
2.9
3.3
3.7
4.1
4.5
5.0
5.5
6.0
6.5
7.0
3
4
5
6
8
2.4
2.9
3.4
3.8
4.3
4.8
5.2
5.7
6.1
6.6
7.1
7.5
8.0
8.5
8.9
9.4
9.8
10.3
10.8
11.2
5.1
6.0
6.9
7.9
8.8
9.8
10.7
11.7
12.6
13.6
14.5
15.5
16.4
17.3
18.3
19.2
20.2
21.1
22.1
23.0
8.9
10.6
12.2
13.9
15.6
17.2
18.9
20.5
22.2
23.8
25.5
27.1
28.8
30.4
32.1
33.8
35.4
37.1
38.7
40.4
15.1
17.8
20.6
23.4
26.1
28.9
31.7
34.4
37.2
40.0
42.7
45.5
48.3
51.0
53.8
56.6
59.3
62.1
64.9
67.6
32.1
38.0
43.8
49.6
55.5
61.3
67.2
73.0
78.9
84.7
90.6
96.4
102.2
108.1
113.9
119.8
125.6
131.5
137.3
143.1
Pipe Diameter — inch
10
12
Capacity — l/s
58.7
94.0
69.3
110.9
79.9
127.8
90.4
144.7
101.0
161.6
111.6
178.4
122.2
195.3
132.8
212.2
143.4
229.1
154.0
246.0
164.6
262.9
175.2
279.7
185.8
296.6
196.4
313.5
207.0
330.4
217.5
347.3
228.1
364.1
238.7
381.0
249.3
397.9
259.9
414.8
14
16
18
20
121.8
143.6
165.4
187.2
209.0
230.8
252.6
274.4
296.2
318.0
339.8
361.6
383.4
405.2
427.0
448.8
470.6
492.4
514.2
536.0
175.8
207.1
238.5
269.8
301.1
332.5
363.8
395.2
426.5
457.8
489.2
520.5
551.9
583.2
614.6
645.9
677.2
708.6
739.9
771.3
242.4
285.5
328.6
371.7
414.8
457.9
501.0
544.1
587.1
630.2
673.3
716.4
759.5
802.6
845.7
888.8
931.8
974.9
1018.0
1061.1
322.8
380.0
437.2
494.4
551.6
608.8
666.0
723.2
780.4
837.6
894.8
952.0
1009.2
1066.4
1123.6
1180.8
1238.0
1295.3
1352.5
1409.7
Section
xxx-Sx
Date
Rev.
08.02.2011
0
DISCHARGE HEAD LOSSES
Discharge Head Loss — m
1
10x4
10x5
10x6
10AC6
12AC8
17x8
17AC8
20AC12 25AC14
0.1
10
100
Capacity — l/s
1000
Section
xxx-Sx
Date
Rev.
08.02.2011
0
DISCHARGE ELBOW LOSSES
Discharge Elbow Loss — m
1
3''
4''
5''
6''
8''
0.1
10
100
Capacity — l/s
1000
Section
xxx-Sx
Date
Rev.
08.02.2011
0
DISCHARGE HEAD & COLUMN ASSEMBLY SECTIONAL VIEW (WATER LUBE)
Motor
Key
Setscrew
Motor Shaft Coupling
Key
Setscrew
Head Shaft Coupling
Pressure Gage
Deflector Ring
Head Shaft
Pre-Lubrication Pipe
Discharge Head
Upper Column Pipe
Snap Ring
Washer
Column Pipe Coupling
Column Flange
Bearing Retainer
Line Shaft Bearing
Column Pipe
Non-Reverse Plate
Non-Reverse Pin
Adjusting Nut
Key
Pin Safety Plate
Drive Coupling
Pipe Plug
Intermediate Part
Copper Pipe
Gland
Deflector Ring
Grease Cup
Oil Level Indicator
Sealing Pipe
Thrust Bearing
Thrust Bearing Cover
Thrust Assembly Body
Lantern Ring
Seal
Packing Box
Packing Box Bearing
Section
xxx-Sx
Date
Rev.
DISCHARGE HEAD & COLUMN ASSEMBLY SECTIONAL VIEW (OIL LUBE)
Motor
Setscrew
Key
Motor Shaft Coupling
Setscrew
Key
Head Shaft Coupling
Pressure Gage
Pipe Plug
Head Shaft
Discharge Head
Column Flange
Upper Column Pipe
Line Shaft Bearing
Column Pipe Coupling
Tube Stabilizer
Column Pipe
Non-Reverse Plate
Non-Reverse Pin
Adjusting Nut
Key
Pin Safety Plate
Drive Coupling
Pipe Plug
Pipe Bushing
Pipe Plug
Lock Nut
Intermediate Part
Oil Level Indicator
Sealing Pipe
Thrust Bearing
Thrust Bearing Cover
Thrust Assembly Body
Tension Nut
Tube Connector
Tube Connector Bearing
08.02.2011
0
Section
xxx-Sx
Date
Rev.
BOWL ASSEMBLY SECTIONAL VIEW
OIL LUBRICATED
Column Pipe
Pump Shaft Coupling
Oil Tube
Pump Shaft
Tube Adapter
Deflector Ring
Discharge Case
Discharge Case Bearing
Bowl
Bowl Rubber Bearing
WATER LUBRICATED
Column Pipe
Pump Shaft Coupling
Pump Shaft
Discharge Case Bearing Cap
Discharge Case
Discharge Case Bearing
Bowl
Bowl Rubber Bearing
Bowl Bearing
Impeller Lock Collet
Impeller
Bowl Bearing
Impeller
Wear Ring (Optional)
Wear Ring (Optional)
Sand Collar
Suction Case
Suction Case Bearing
Sand Collar
Suction Case
Suction Case Bearing
Pipe Plug
Suction Pipe
Conical Strainer
Pipe Plug
Suction Pipe
Conical Strainer
08.02.2011
0
Section
xxx-Sx
Date
Rev.
08.02.2011
0
STANDARD MATERIALS FOR SUBMERSIBLE PUMPS
Item
1
2
6
Nomenclature
1
Discharge Case
2
Check Valve
3
Rubber Seat
4
Pump Shaft
5
Bolts and Nuts
6
Intermediate Bowl
7
Impeller
8
9
Intermediate Bowl Bearing
10
Suction Case
11
Strainer
12
Intermediate Part
13
Coupling
3
4
5
9
7
8
11
10
13
12
Material
Cast Iron
ASTM A48 Class 30B
Stainless Steel Sheet
ASTM A582 Type 304
Rubber
Shore 70
Stainless Steel
ASTM A582 Type 420
Steel
ASTM A307-61 Gr. A
Cast Iron
ASTM A48 Class 30B
Leaded Red Bronze
C83600
Stainless Steel
ASTM A582 Type 420
Leaded Red Bronze
C83600
Cast Iron
ASTM A48 Class 30B
Stainless Steel Sheet
ASTM A582 Type 304
Cast Iron
ASTM A48 Class 30B
Stainless Steel
ASTM A582 Type 420
Section
xxx-Sx
Date
Rev.
08.02.2011
0
SHAFT DETAIL FOR LINESHAFT BOWLS
Bowl
6NT
6R
7NR
8R
8NF
10R
10JK
10FH
12R
12FH
Shaft
Extension
E – inch
248
248
356
356
356
356
356
356
356
356
st
Shaft
Diameter
inch
1
1
1 3/16
1 3/16
1 3/16
1 11/16
1 1/2
1 11/16
1 15/16
1 15/16
1 Impeller
Position
A – mm
110
133
130.5
143
177
217.5
209.5
228.5
217
203
Single Stage
Shaft Length
B – mm
602.5
654
740
848
896.5
975
930
990
1041
1048
Additional Stage
Shaft Length
C – mm
91.5
132
158
165
178
210
193.5
222.5
254
279.5
Note: Subject to change without any notice.
B
A
C
E
Section
xxx-Sx
Date
Rev.
08.02.2011
0
APPROXIMATE TORQUE REQUIREMENTS FOR METRIC BOLTS
Bolt
Designation
M6
M8
M10
M12
M16
M20
M22
M24
M27
M30
M33
M39
Note: Torques in N-m
Steel
Gr. 1
4
8
15
38
75
132
210
312
461
651
895
1166
AISI
304
4
8
15
38
75
132
210
312
461
651
895
1166
AISI
316
4
8
15
38
75
132
210
312
461
651
895
1166
Steel
Gr. 5
11
20
38
95
190
339
549
814
1044
1465
1994
2645
Steel
Gr. 8
15
31
54
134
269
475
768
1150
1689
2373
3221
4252
Section
xxx-Sx
Date
Rev.
08.02.2011
0
DIAMETRIC RUNNING CLEARANCES
Nominal
Shaft Diameter
in
1
1 3/16
1 1/2
1 11/16
1 15/16
mm
25.40
30.16
38.10
42.86
49.21
Bronze Bowl Bearings
Nominal
Clearance
mm
0.20
0.20
0.20
0.20
0.25
Range of
Clearance
mm
0.20 to 0.36
0.20 to 0.38
0.20 to 0.38
0.20 to 0.38
0.25 to 0.43
Max. Allowable Bearing
I.D. Before Replacement
mm
25.90
30.66
38.65
43.41
49.81
Impeller Skirt & Wear Ring
Nominal
Shaft Diameter
in
Less than 2
2.0 to 3.99
4.0 to 4.99
5.0 to 5.99
6.0 to 6.99
8.0 to 10.99
11.0 to 11.99
12.0 to 19.99
20.0 to 29.99
mm
Less than 50.80
50.80 to 101.35
101.60 to 126.75
127.00 to 152.15
152.40 to 177.55
203.20 to 279.15
279.40 to 304.55
304.80 to 507.75
508.00 to 761.75
Nominal
Clearance
Range of
Clearance
mm
0.40
0.50
0.60
0.70
0.80
0.80
0.90
0.90
0.90
mm
0.40 to 0.50
0.50 to 0.60
0.60 to 0.70
0.70 to 0.80
0.80 to 0.90
0.80 to 0.90
0.90 to 1.00
0.90 to 1.00
0.90 to 1.00
Max. Allowable Diametric
Clearance Before
Replacement
mm
0.80
0.90
1.00
1.10
1.20
1.20
1.30
1.30
1.30
Section
xxx-Sx
Date
Rev.
08.02.2011
0
IMPELLER IDENTIFICATION
Impeller
6NTM
6RL
6RM
6RH
7NRL
8NRL
8RM
8RH
8NFM
10RL
10RM
10RH
10JKL
10JKM
10JKH
10JKXH
10FHM
10FHH
12RXL
12RL
12RM
12RH
12FHL
12FHM
12FHH
Maximum
Diameter
A – mm
114.7
113.8
113.8
113.8
144.9
151.9
151.9
151.9
162.4
199.6
199.6
199.6
199.6
199.6
199.6
199.6
204.2
204.2
235.8
235.8
235.8
235.8
243.7
243.7
243.7
Note: Subject to change without any notice.
Machining
Angle
C – mm
22.0
26.0
31.0
31.0
31.0
26.0
25.0
25.0
31.0
25.0
25.0
25.0
22.0
22.0
22.0
22.0
40.0
40.0
30.0
25.0
25.0
25.0
27.5
27.0
27.0
Number
Of
Vanes
6
6
5
7
6
6
6
8
5
5
6
7
5
8
8
8
5
7
6
5
6
8
5
4
8
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.
 N  D 
Q2  Q1  2  2 
 N1  D1 
2
N  D 
H 2  H1  2   2 
 N1   D1 
3
N  D 
P2  P1  2   2 
 N1   D1 
2
3
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 nonabrasive 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 pumpmotor 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 prelubrication 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 prelubrication 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
3”
4”
6”
8”
10”
f)
175 l
60 m
45 m
30 m
350 l
105 m
90 m
60 m
45 m
35 m
700 l
1000 l
120 m
105 m
90 m
180 m
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.
<=
1.00
<=
1.00
<=
1.00
(REF.)
(~)
(~)
TS EN 10088–3
<=
BS 970 A 276–02
1.4404
0.030
316 S11
316L
X2CrNiMo17–12–2
(~)
(~)
<=
BS 970 A 276–02
0.07
304 S31
304
(~)
(REF.)
0.18
BS 970 A 108–99
–
055 M15 1020
0.23
(~)
(REF.)
0.43
BS 970 A 108–99
–
080 M46 1045
0.50
(REF.)
Chromium Nickel
TS EN 10088–3
Steel
1.4306
Low Carbon
X2CrNi19–11
(REF.)
Chromium Nickel TS EN 10088–3
Steel
1.4301
X5CrNi18–10
(~)
TS EN 10083–2
1.0402
C22
(~)
TS EN 10083–2
1.053
C45
Chromium Nickel
Molybdenum
Steel
Low Carbon
(REF.)
Chromium Nickel
(~)
(~)
TS EN 10088–3
<=
Molybdenum
BS 970 A 276–02
1.4401
0.07
Steel
316 S31
316
X5CrNiMo17–12–2
(~)
(~)
<=
BS 970 A 276–02
0.030
304 S11
304L
Chromium
Steel
Carbon Steel
Carbon Steel
S2
S3
S4
S5
S6
S7
S8
0.60
–
0.90
<=
<=
0.030 0.050
<=
<=
0.030 0.050
<=
<=
0.045 0.030
<=
<=
0.045 0.030
<=
<=
0.045 0.030
<=
<=
0.045 0.030
<=
0.040
0.15
–
0.35
–
–
<=
0.11
<=
0.11
<=
0.11
<=
0.11
–
–
N
–
–
17.00
–
19.50
18.00
–
20.00
16.50
–
18.50
16.50
–
18.50
12.00
–
14.00
12.00
–
14.00
Cr
–
–
–
–
2.00
–
2.50
2.00
–
2.50
<=
0.60
–
Mo
–
–
8.00
–
10.50
10.00
–
12.00
10.00
–
13.00
10.00
–
13.00
–
–
Nİ
SA
SA
SA
SA
Q&T 650
A
<= 215
HB
<= 215
HB
<= 215
HB
<= 215
HB
–
>= 190
MPa
>= 180
MPa
>= 200
MPa
>= 200
MPa
450
MPa
–
<= 220
HB
500 – 700
MPa
460 – 680
MPa
500 – 700
MPa
500 – 700
MPa
650 – 850
MPa
<= 730
MPa
800 – 950
MPa
Q&T 650
600
MPa
–
–
<= 760
MPa
700 – 850
MPa
–
500
MPa
<= 230
HB
Q&T 650
A
Heat
Yield
Tensile
Hardness
Treatment
Strength Strength
Date
Rev.
–
0.30
–
0.60
S
<=
<=
0.040 0.030
P
MECHANICAL PROPERTIES
Section
xxx-Sx
–
<=
2.00
<=
2.00
<=
2.00
<=
2.00
<=
1.50
<=
1.50
Mn
CHEMICAL COMPOSITION
<=
1.00
<=
1.00
(~)
(~)
0.06
BS 970 A 276–02
–
416 S21
416
0.15
(REF.)
TS EN 10088–3
1.4005
X12CrS13
<=
1.00
Si
(~)
(~)
0.16
BS 970 A 276–02
–
420 S29
420
0.25
C
S1
STANDARD
(REF.)
TS EN 10088–3
1.4021
X20Cr13
DESCRIPTION
Chromium
Steel
LAYNE
BOWLER
NO.
08.02.2011
0
WROUGHT STEEL GRADES
–
–
–
–
(REF.)
TS EN 10283
1.4468
GX2CrNiMoN25–6–3
(REF.)
TS EN 10283
1.4469
(REF.)
TS EN 10283
1.4470
(REF.)
TS EN 10283
1.4517
GX2CrNiMoCuN25–6–3–3
Duplex Stainless
Steel
Duplex Stainless
Steel
Duplex Stainless
Steel
Duplex Stainless
Steel
Carbon Steel
S55
S56
S57
S58
S59
S60
<=
0.03
<=
0.80
–
–
<=
<=
<=
0.60 0.050 0.60
<=
<=
<=
1.50 0.035 0.025
<=
<=
<=
2.00 0.035 0.025
<=
<=
<=
1.00 0.035 0.025
<=
<=
<=
2.00 0.035 0.025
18.00
–
20.00
18.00
–
20.00
18.00
–
20.00
18.00
–
20.00
12.00
–
13.50
Cr
–
–
–
–
–
–
Cu
–
–
–
–
0.120 24.50 2.75
–
–
–
0.220 26.50 3.50
0.120 21.00
–
–
0.200 23.00
0.120 25.00
<=
–
–
1.30
0.220 27.00
0.120 24.50
–
–
0.250 26.50
<=
<=
<=
<=
2.00 0.035 0.025 0.200
<=
<=
<=
1.50 0.040 0.030
<=
<=
<=
<=
2.00 0.035 0.025 0.200
<=
<=
<=
1.50 0.040 0.030
–
N
9.00
–
12.00
8.00
–
11.00
1.00
–
2.00
Nİ
–
2.50
–
3.50
2.50
–
3.50
3.00
–
5.00
2.50
–
3.50
–
5.00
–
7.00
4.50
–
6.50
6.00
–
8.00
5.50
–
7.00
2.00 9.00
–
–
2.50 12.00
2.00 9.00
–
–
2.50 12.00
–
–
0.20
–
0.50
Mo
>= 200
MPa
>= 380
MPa
Heat
Yield
Tensile
Hardness
Treatment
Strength Strength
Date
Rev.
(~)
(REF.)
<=
BS 3100 A 27–00
0.30
AM1 Gr 60–30
<=
1.00
<=
1.00
<=
1.00
<=
1.00
S
Section
xxx-Sx
(~)
<=
A 890–99
0.03
1B
(~)
<=
A 890–99
0.03
4A
(~)
<=
A 890–99
0.03
5A
–
<=
1.50
<=
1.50
P
<=
<=
<=
1.00 0.035 0.025
Mn
(~)
DIN 1681
GS–38
GE200
–
(REF.)
TS EN 10283
1.4409
GX2CrNiMo19–11–2
Chromium Nickel
Molybdenum
Steel
Low Carbon
S54
<=
0.03
(~)
(~)
<=
BS 3100 A 351–00
0.07
316 C16 CF–8M
(REF.)
Chromium Nickel
TS EN 10283
Molybdenum
1.4408
Steel
GX5CrNiMo19–11–2
S53
–
(~)
(~)
<=
<=
BS 3100 A 351–00
0.030 1.50
304 C12 CF–3
(REF.)
Chromium Nickel
TS EN 10283
Steel
1.4309
Low Carbon
GX2CrNi19–11
<=
1.50
(~)
(~)
<=
BS 3100 A 351–00
0.07
304 C15 CF–8
<=
1.00
Si
S52
(~)
(~)
<=
BS 3100 A 351–00
0.10
410 C21 CA–15
C
(REF.)
Chromium Nickel TS EN 10283
Steel
1.4308
GX5CrNi19–10
(REF.)
TS EN 10283
1.4008
GX7CrNiMo12–1
STANDARD
S51
DESCRIPTION
Chromium
Steel
LAYNE
BOWLER
NO.
08.02.2011
0
CAST STEEL GRADES
Grey Cast Iron
Grey Cast Iron
Grey Cast Iron
Grey Cast Iron
Grey Cast Iron
Ductile Iron
Ductile Iron
Ductile Iron
Ductile Iron
Ni–Resist
Ni–Resist
C1
C2
C3
C4
C5
C6
C7
C8
C9
C51
C52
LAYNE
BOWLER DESCRIPTION
NO.
(REF.)
TS EN 1561
0.6015
GG–15
(REF.)
TS EN 1561
0.6020
GG–20
(REF.)
TS EN 1561
0.6025
GG–25
(REF.)
TS EN 1561
0.6030
GG–30
(REF.)
TS EN 1561
0.6035
GG–35
(REF.)
TS EN 1563
0.7040
GGG–40
(REF.)
TS EN 1563
0.7050
GGG–50
(REF.)
TS EN 1563
0.7060
GGG–60
(REF.)
TS EN 1563
0.7070
GGG–70
(REF.)
TS EN 13835
0.7660
GGG-NiCr 20 2
(REF.)
TS EN 13835
0.7676
GGG-NiCr 30 3
2.20
–
2.90
2.20
–
2.90
0.50
–
1.50
(~)
(~)
3.40
BS 2789 A 536–84
–
Gr 600/3 80–55–06 3.80
(~)
(~)
3.40
BS 2789 A 536–84
–
Gr 700/2 100–70–03 3.80
<=
3.00
<=
2.60
(~)
(~)
BS 3468 A 439–83
S-NiCr20–2 Type D–2
(~)
(~)
BS 3468 A 439–83
S-NiCr30–3 Type D–3
<=
0.080
–
–
<=
0.04
<=
0.04
<=
0.04
<=
0.04
<=
0.10
<=
0.10
<=
0.12
<=
0.12
<=
0.12
S
2.50
–
3.50
1.00
–
3.50
–
–
–
–
–
–
–
–
–
Cr
<=
0.50
<=
0.50
0.60
–
0.80
0.60
–
0.80
–
–
–
–
–
–
–
Cu
28.00
–
32.00
18.00
–
22.00
–
–
–
–
–
–
–
–
–
Nİ
130 – 170 >= 207
HB
MPa
140 – 200 >= 207
HB
MPa
230 – 320
HB
210 – 300
HB
170 – 240
HB
150 – 200
HB
210 – 250
HB
200 – 240
HB
180 – 250
HB
170 – 210
HB
160 – 190
HB
>= 379
MPa
>= 400
MPa
>= 687
MPa
>= 589
MPa
>= 491
MPa
>= 412
MPa
>= 350
MPa
>= 300
MPa
>= 250
MPa
>= 200
MPa
>= 150
MPa
Heat
Yield
Tensile
Hardness
Treatment
Strength Strength
Date
Rev.
0.50
–
1.50
<=
0.080
<=
0.08
<=
0.08
<=
0.08
<=
0.08
<=
0.20
<=
0.20
<=
0.25
<=
0.40
<=
0.50
P
Section
xxx-Sx
0.50
–
1.50
0.30
–
0.50
0.30
–
0.40
0.30
–
0.50
0.05
–
0.20
0.60
–
0.80
0.40
–
0.70
0.40
–
0.70
0.50
–
0.80
0.50
–
0.80
Mn
0.50
–
1.50
2.20
–
2.90
1.70
–
2.00
(~)
(~)
3.40
BS 2789 A 536–84
–
Gr 500/7 60–45–12 3.80
(~)
A 48–00
Gr 50B
(~)
BS 1452
Gr 350
2.95
–
3.10
1.85
–
2.10
2.20
–
2.90
(~)
A 48–00
Gr 45B
(~)
BS 1452
Gr 300
3.00
–
3.25
2.10
–
2.30
(~)
(~)
3.40
BS 2789 A 536–84
–
Gr 420/12 60–40–18 3.80
(~)
A 48–00
Gr 40B
(~)
BS 1452
Gr 260
3.20
–
3.40
2.30
–
2.50
Si
1.70
–
2.00
(~)
A 48–00
Gr 30B
(~)
BS 1452
Gr 220
3.40
–
3.60
C
3.00
–
3.26
(~)
A 48–00
Gr 25B
(~)
BS 1452
Gr 150
STANDARD
08.02.2011
0
CAST IRON GRADES
–
–
Bz–Al–Ni
Aluminum nickel
Bronze
Impeller material for DSI.
Bearing material for DSI.
B5
B50
B51
–
4.0
–
11.0
4.0
–
10.0
80.0
–
90.0
73.0
–
87.0
–
>=
79.0
>=
83.0
<=
3.0
–
3.5
–
4.5
<=
1.0
–
–
–
3.0
–
5.0
<=
1.0
<=
0.20
<=
0.25
<=
0.25
Sb
<=
0.25
<=
0.20
<=
0.30
Fe
<=
2.0
<=
2.0
4.0
–
5.0
<=
1.5
<=
0.8
<=
1.0
<=
1.0
Ni
–
–
–
–
<=
0.05
<=
0.05
<=
0.08
S
Al
Si
–
–
–
–
–
–
8.5
–
9.5
10.0
–
11.5
–
–
<=
0.1
–
<=
<=
<=
0.05 0.005 0.005
<=
<=
<=
0.25 0.005 0.005
<=
<=
<=
0.05 0.005 0.005
P
–
–
0.8
–
1.5
<=
0.5
–
–
–
<=
1.0
<=
1.0
–
–
–
–
–
Mn Other
Heat
Yield
Tensile
Hardness
Treatment
Strength Strength
Date
Rev.
9.0
–
15.0
<=
6.0
–
–
<=
0.50
<=
0.7
4.0
–
6.0
Zn
Section
xxx-Sx
<=
6.0
<=
0.09
–
<=
0.30
1.0
–
2.5
4.0
–
6.0
Pb
ASTM
C95800
ASTM
C95400
Bz–Al
Aluminum
Bronze
B4
9.2
–
11.0
89.0
–
91.0
ASTM
C90250
Bz 90–10
Tin Bronze
B3
9.0
–
11.0
86.0
–
89.0
ASTM
C92700
Bz 88–10–2
Leaded Tin
Bronze
B2
4.0
–
6.0
84.0
–
86.0
ASTM
C83600
Bz 85–5–5–5
Sn
Cu
STANDARD
Leaded Red
Bronze
DESCRIPTION
B1
LAYNE
BOWLER
NO.
08.02.2011
0
COPPER ALLOYS

Layne Bowler Pump Engineering Brochure

Transcription

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