Technical Data
Water Products
© 2005 ITT Water Technology, Inc.
Effective March, 2005
TTECHWP
www.goulds.com
Technical Data
TECHNICAL DATA
Index
FRICTION LOSS
CONVERSION CHARTS
Plastic ........................................................................................ 1
Steel .......................................................................................... 2
Copper ...................................................................................... 3
Aluminum .................................................................................. 4
Rubber Hose .............................................................................. 4
Fittings ...................................................................................... 5
Offset Jet Pump Pipe Friction ...................................................... 5
Conversion Charts.................................................................... 25
JET AND SUBMERSIBLE PUMP SELECTION
Private Residences, Yard Fixtures, Public Buildings, Farm Use ..... 6
Boiler Feed Requirements .......................................................... 6
TANK SELECTION
Hydro-Pro® ............................................................................... 7
Galvanized................................................................................. 8
Capacities of Tanks of Various Dimensions ................................. 9
CENTRIFUGAL PUMP FUNDAMENTALS
NPSH and Cavitation................................................................ 10
Vapor Pressure of Water .......................................................... 12
ELECTRICAL DATA
TYPICAL INSTALLATIONS
Jet – Deep and Shallow Well ................................................... 29
Submersible – 4” Well ............................................................. 30
High Capacity Submersible ...................................................... 31
Centrifugal Booster .................................................................. 32
Jet Booster ............................................................................... 33
PIPE VOLUME AND VELOCITY
Storage of Water in Various Size Pipes ..................................... 34
Minimum Flow to Maintain 2 Ft./Sec........................................ 34
Storage of Water in Various Sizes of Wells ............................... 34
MOTOR DATA
Goulds Pumps and A.O. Smith Motor Data ............................... 35
Electrical Components ............................................................. 35
Terminal Board and Voltage Change Plug ................................ 36
Capacitor Start Induction Run – Motor Wiring .......................... 36
NOTE:
Submersible Motor Data moved to catalog “Motor Section”
Transformer Sizes ..................................................................... 13
Three Phase Unbalance............................................................ 14
NEMA Panel Enclosures ........................................................... 15
EMERSON MOTOR WIRING
DETERMINING WATER LEVEL
PRESSURE SWITCH WIRING AND ADJUSTMENTS
Determining Water Level ......................................................... 16
Square “D” Switches ................................................................ 38
Furnas Pro Control ................................................................... 38
USE OF TAIL PIPE WITH JET PUMPS
115/230 Voltage ...................................................................... 37
Use of Tail Pipe with Jet Pumps ................................................ 17
WIRING DIAGRAMS
DETERMINING FLOW RATES
AWA501, AWA502 .................................................................. 39
Power/Pump Connections: AWA501, AWA502......................... 40
Full Pipe Flow .......................................................................... 18
Pipe Not Running Full .............................................................. 18
Discharge Rate in Gallons per Minute ...................................... 18
Theoretical Discharge of Nozzles in U.S. Gal. per Min............... 19
TERMS AND USABLE FORMULAS
Calculating Suction Lift ............................................................ 21
Definitions ............................................................................... 22
Basic Formulas ......................................................................... 22
Affinity Laws............................................................................ 24
SPECIFICATIONS ARE SUBJECT TO CHANGE WITHOUT NOTICE.
LOW YIELD WELL COMPONENTS
Components for a Low Yield Well with a Booster System ......... 41
Friction Loss
TECHNICAL DATA
PLASTIC PIPE: FRICTION LOSS (IN FEET OF HEAD) PER 100 FT.
GPM
GPH
1
2
3
4
5
6
8
10
15
20
25
30
35
40
45
50
60
70
80
90
100
125
150
175
200
250
300
350
400
500
550
600
700
800
900
950
1000
60
120
180
240
300
360
480
600
900
1,200
1,500
1,800
2,100
2,400
2,700
3,000
3,600
4,200
4,800
5,400
6,000
7,500
9,000
10,500
12,000
15,000
18,000
21,000
24,000
30,000
33,000
36,000
42,000
48,000
54,000
57,000
60,000
⁄8"
ft.
4.25
15.13
31.97
54.97
84.41
3
½"
ft.
1.38
4.83
9.96
17.07
25.76
36.34
63.71
97.52
¾"
ft.
.356
1.21
2.51
4.21
6.33
8.83
15.18
25.98
49.68
86.94
1"
ft.
.11
.38
.77
1.30
1.92
2.69
4.58
6.88
14.63
25.07
38.41
1¼"
ft.
.10
.21
.35
.51
.71
1.19
1.78
3.75
6.39
9.71
13.62
18.17
23.55
29.44
1½"
ft.
.10
.16
.24
.33
.55
.83
1.74
2.94
4.44
6.26
8.37
10.70
13.46
16.45
23.48
1
2"
ft.
.10
.17
.25
.52
.86
1.29
1.81
2.42
3.11
3.84
4.67
6.60
8.83
11.43
14.26
2½"
ft.
.11
.22
.36
.54
.75
1.00
1.28
1.54
1.93
2.71
3.66
4.67
5.82
7.11
10.83
3"
ft.
.13
.19
.26
.35
.44
.55
.66
.93
1.24
1.58
1.98
2.42
3.80
5.15
6.90
8.90
4"
ft.
.09
.12
.15
.17
.25
.33
.41
.52
.63
.95
1.33
1.78
2.27
3.36
4.85
6.53
6"
ft.
.08
.13
.18
.23
.30
.45
.63
.84
1.08
1.66
1.98
2.35
8"
ft.
.12
.17
.22
.28
.42
.50
.59
.79
1.02
1.27
10"
ft.
.14
.16
.19
.26
.33
.41
.46
.50
Friction Loss
TECHNICAL DATA
STEEL PIPE: FRICTION LOSS (IN FEET OF HEAD) PER 100 FT.
GPM
GPH
1
2
3
4
5
6
7
8
9
10
12
15
20
25
30
35
40
45
70
100
150
200
250
300
350
400
450
500
550
600
650
700
750
800
850
900
950
1000
60
120
180
240
300
360
420
480
540
600
720
900
1,200
1,500
1,800
2,100
2,400
2,700
4,200
6,000
9,000
12,000
15,000
18,000
21,000
24,000
27,000
30,000
33,000
36,000
39,000
42,000
45,000
48,000
51,000
54,000
57,000
60,000
⁄8"
ft.
4.30
15.00
31.80
54.90
83.50
3
½"
ft.
1.86
4.78
10.00
17.10
25.80
36.50
48.70
62.70
¾"
ft.
.26
1.21
2.50
4.21
6.32
8.87
11.80
15.00
18.80
23.00
32.60
49.70
86.10
1"
ft.
.38
.77
1.30
1.93
2.68
3.56
4.54
5.65
6.86
9.62
14.70
25.10
38.60
54.60
73.40
95.00
1¼"
ft.
.34
.51
.70
.93
1.18
1.46
1.77
2.48
3.74
6.34
9.65
13.60
18.20
23.50
30.70
68.80
1½"
ft.
2"
ft.
.24
.33
.44
.56
.69
.83
1.16
1.75
2.94
4.48
6.26
8.37
10.79
13.45
31.30
62.20
.10
.13
.17
.21
.25
.34
.52
.87
1.30
1.82
2.42
3.10
3.85
8.86
17.40
38.00
66.30
90.70
2
2½"
ft.
3"
ft.
4"
ft.
5"
ft.
6"
ft.
8"
ft.
10"
ft.
.11
.15
.22
.36
.54
.75
1.00
1.28
1.60
3.63
7.11
15.40
26.70
42.80
58.50
79.20
103.00
130.00
160.00
193.00
230.00
.04
.05
.08
.13
.19
.26
.35
.44
.55
1.22
2.39
5.14
8.90
14.10
19.20
26.90
33.90
42.75
52.50
63.20
74.80
87.50
101.00
116.00
131.00
148.00
165.00
184.00
204.00
.35
.63
1.32
2.27
3.60
4.89
6.72
8.47
10.65
13.00
15.70
18.60
21.70
25.00
28.60
32.40
36.50
40.80
45.30
50.20
.736
1.20
1.58
2.18
2.72
3.47
4.16
4.98
5.88
6.87
7.93
9.05
10.22
11.50
12.90
14.30
15.80
.30
.49
.64
.88
1.09
1.36
1.66
1.99
2.34
2.73
3.13
3.57
4.03
4.53
5.05
5.60
6.17
.08
.13
.16
.23
.279
.348
.424
.507
.597
.694
.797
.907
1.02
1.147
1.27
1.41
1.56
.0542
.0719
.0917
.114
.138
.164
.192
.224
.256
.291
.328
.368
.410
.455
.500
Friction Loss
TECHNICAL DATA
COPPER PIPE: FRICTION LOSS (IN FEET OF HEAD) PER 100 FT.
GPM
GPH
1
2
5
7
10
15
18
20
25
30
35
40
45
50
60
70
75
80
90
100
125
150
175
200
250
300
350
400
450
500
750
1000
60
120
300
420
600
900
1,080
1,200
1,500
1,800
2,100
2,400
2,700
3,000
3,600
4,200
4,500
4,800
5,400
6,000
7,500
9,000
10,500
12,000
15,000
18,000
21,000
24,000
27,000
30,000
45,000
60,000
⁄8"
ft.
6.2
19.6
3
½"
ft.
1.8
6.0
30.0
53.0
¾"
ft.
.39
1.2
5.8
11.0
19.6
37.0
55.4
1"
ft.
1¼"
ft.
1.6
3.2
5.3
9.9
16.1
18.5
27.7
39.3
48.5
2.2
3.9
6.2
6.9
10.4
14.3
18.7
25.4
30.0
39.3
3
1½"
ft.
2.1
3.2
3.9
5.3
7.6
10.2
13.2
16.2
19.4
27.7
40.0
41.6
45.0
50.8
2"
ft.
1.5
2.1
2.8
3.5
4.2
5.1
6.9
9.2
9.9
11.6
13.9
16.9
25.4
32.3
41.6
57.8
2½"
ft.
1.2
1.6
1.8
2.5
3.5
3.7
4.2
4.8
6.2
8.6
11.6
16.2
20.8
32.3
41.6
3"
ft.
1.1
1.4
1.6
1.8
2.2
2.8
3.7
4.8
6.9
9.0
13.9
18.5
32.3
39.3
44.0
4"
ft.
1.2
1.7
2.2
3.5
4.6
5.8
7.2
9.2
11.1
23.1
37.0
Friction Loss
TECHNICAL DATA
ALUMINUM PIPE: FRICTION LOSS (IN FEET OF HEAD) PER 100 FT.
GPM
5
10
20
30
40
50
60
70
80
90
100
120
140
160
180
200
220
240
260
280
300
350
400
2" OD
.05"
Wall
.07
.32
1.20
2.58
4.49
6.85
9.67
12.95
16.70
20.80
25.40
3" OD
.05"
Wall
.04
.15
.32
.56
.85
1.21
1.61
2.06
2.58
3.18
4.51
6.00
7.76
9.67
11.83
14.12
16.72
19.42
22.40
25.45
4" OD
.063"
Wall
.04
.08
.13
.20
.28
.38
.49
.60
.74
1.06
1.41
1.82
2.27
2.78
3.31
3.91
4.56
5.26
5.98
8.03
10.36
5" OD
.063"
Wall
.04
.07
.09
.12
.16
.20
.24
.34
.46
.59
.73
.89
1.07
1.27
1.47
1.71
1.93
2.59
3.33
6" OD
.063"
Wall
.03
.04
.05
.06
.08
.10
.14
.19
.24
.30
.36
.44
.52
.60
.69
.79
1.05
1.35
7" OD
.078"
Wall
.03
.04
.05
.07
.09
.11
.14
.17
.20
.24
.28
.33
.37
.50
.64
8" OD
.094"
Wall
GPM
2" OD
.05"
Wall
3" OD
.05"
Wall
450
500
550
600
650
700
750
800
850
900
950
1000
1100
1200
1300
1400
1500
1600
1700
1800
1900
2000
.03
.04
.05
.06
.07
.09
.11
.13
.15
.17
.19
.26
.33
4" OD
.063"
Wall
12.90
15.73
19.12
22.46
26.10
5" OD
.063"
Wall
4.15
5.07
6.16
7.24
8.42
9.68
11.05
12.48
13.95
15.65
17.35
19.10
22.85
26.95
6" OD
.063"
Wall
1.69
2.06
2.50
2.94
3.41
3.92
4.46
5.03
5.64
6.35
7.02
7.72
9.22
10.88
12.62
14.65
16.67
18.80
20.95
23.60
7" OD
.078"
Wall
.80
.97
1.18
1.38
1.62
1.86
2.11
2.38
2.67
2.98
3.32
3.64
4.37
5.16
5.96
6.90
7.87
8.89
9.95
11.15
12.35
13.65
8" OD
.094"
Wall
.41
.50
.62
.72
.84
.97
1.10
1.24
1.39
1.56
1.73
1.90
2.27
2.68
3.10
3.60
4.07
4.62
5.16
5.79
6.42
7.10
3"
21
28
39
49
74
106
143
182
224
270
394
525
4"
4.9
6.7
9.3
11.8
17.1
23
30
40
51
63
100
141
185
230
(Above table computed for aluminum pipe with coupler.
RUBBER HOSE: FRICTION LOSS (IN FEET OF HEAD) PER 100 FT.
GPM
15
20
25
30
40
50
60
70
80
90
100
125
150
175
200
¾"
70
122
182
259
1"
23
32
51
72
122
185
233
Actual Inside Diameter in Inches
1¼"
1½"
2"
2½"
5.8
2.5
.9
.2
10
4.2
1.6
.5
15
6.7
2.3
.7
21.2
9.3
3.2
.9
35
15.5
5.5
1.4
55
23
8.3
2.3
81
32
11.8
3.2
104
44
15.2
4.2
134
55
19.8
5.3
164
70
25
7
203
85
29
8.1
305
127
46
12.2
422
180
62
17.3
230
85
23.1
308
106
30
3"
.2
.7
1.2
1.4
1.8
2.5
3.5
4
5.8
8.1
10.6
13.6
GPM
4"
250
300
350
400
500
600
700
800
900
1000
1250
1500
1750
2000
.7
.9
1.4
1.6
2.5
3.2
4
¾"
1"
Actual Inside Diameter in Inches
1¼"
1½"
2"
2½"
162
44
219
62
292
83
106
163
242
344
440
Friction Loss
TECHNICAL DATA
EQUIVALENT NUMBER OF FEET STRAIGHT PIPE FOR DIFFERENT FITTINGS
Size of fittings, Inches
½"
¾"
1"
1¼"
1½"
2"
2½"
3"
4"
5"
6"
8"
10"
90° Ell
45° Ell
Long Sweep Ell
Close Return Bend
Tee-Straight Run
Tee-Side Inlet or Outlet
or Pitless Adapter
Ball or Globe Valve Open
Angle Valve Open
Gate Valve-Fully Open
Check Valve (Swing)
In Line Check Valve
(Spring)
or Foot Valve
1.5
0.8
1.0
3.6
1
2.0
1.0
1.4
5.0
2
2.7
1.3
1.7
6.0
2
3.5
1.7
2.3
8.3
3
4.3
2.0
2.7
10.0
3
5.5
2.5
3.5
13.0
4
6.5
3.0
4.2
15.0
5
8.0
3.8
5.2
18.0
10.0
5.0
7.0
24.0
14.0
6.3
9.0
31.0
15
7.1
11.0
37.0
20
9.4
14.0
39.0
25
12
3.3
4.5
5.7
7.6
9.0
12.0
14.0
17.0
22.0
27.0
31.0
40.0
17.0
8.4
0.4
4
22.0
12.0
0.5
5
27.0
15.0
0.6
7
36.0
18.0
0.8
9
43.0
22.0
1.0
11
55.0
28.0
1.2
13
67.0
33.0
1.4
16
82.0
42.0
1.7
20
110.0
58.0
2.3
26
140.0
70.0
2.9
33
160.0
83.0
3.5
39
220.0
110.0
4.5
52
4
6
8
12
14
19
23
32
43
58
Example:
(A) 100 ft. of 2" plastic pipe with one (1) 90º elbow and one (1)
swing check valve.
90º elbow – equivalent to
5.5 ft. of straight pipe
Swing check – equivalent to 13.0 ft. of straight pipe
100 ft. of pipe – equivalent to 100 ft. of straight pipe
118.5 ft. = Total equivalent pipe
Figure friction loss for 118.5 ft. of pipe.
65
(B) Assume flow to be 80 GPM through 2" plastic pipe.
1. Friction loss table shows 11.43 ft. loss per 100 ft. of pipe.
2. In step (A) above we have determined total ft. of pipe to be 118.5 ft.
3. Convert 118.5 ft. to percentage 118.5 ÷ 100 = 1.185
4. Multiply
11.43
x 1.185
13.54455 or 13.5 ft. = Total friction loss in this system.
OFFSET JET PUMP PIPE FRICTION
Where the jet pump is offset horizontally from the well site, add the following distances to the vertical lift to approximate capacity to be received.
PIPE FRICTION FOR OFFSET JET PUMPS
Friction Loss in Feet Per 100 Feet Offset
JET SIZE
SUCTION AND PRESSURE PIPE SIZES (in inches)
HP
1¼ x 1
1¼ x 1¼
1½ x 1¼
1½ x 1½
1
⁄3
12
8
6
4
½
18
12
8
22
¾
1
1½
2
Operations Below Line
Not Recommended
2 x 1½
2x2
6
3
2
16
11
6
4
25
16
9
6
13
20
3
NOTE: Friction loss is to be added to vertical lift.
5
2½ x 2
2½ x 2½
8
5
3
13
7
5
13
9
3 x 2½
3x3
6
4
Jet and Submersible
Pump Selection
TECHNICAL DATA
PRIVATE RESIDENCES
Outlets
Flow Rate GPM
Shower or Bathtub
Lavatory
Toilet
Kitchen Sink
Automatic Washer
Dishwasher
Normal seven minute*
peak demand (gallons)
Minimum sized pump required
to meet peak demand without
supplemental supply
5
4
4
5
5
2
Total Usage Gallons
Bathrooms in Home
1½
2-2 ½
35
53
4
6
10
15
3
3
18
18
–
3
70
98
1
35
2
5
3
–
–
45
35
2
5
3
35
14
7 GPM (420 GPH)
10 GPM (600 GPH)
3-4
70
8
20
3
18
3
122
14 GPM (840 GPH)
17 GPM (1020 GPH)
Notes:
Values given are average and do not include higher or lower extremes.
* Peak demand can occur several times during morning and evening hours.
** Count the number of fixtures in a home including outside hose bibs. Supply one gallon per minute each.
YARD FIXTURES
Garden Hose – 1⁄2"
Garden Hose – 3⁄4"
Sprinkler– Lawn
FARM USE
3 GPM
6 GPM
3-7 GPM
Horse, Steer
Dry Cow
Milking Cow
Hog
Sheep
Chickens/100
Turkeys/100
Fire
PUBLIC BUILDINGS
Pump Capacity Required in U.S. Gallons per Minute
per fixture for Public Buildings
Total Number of Fixtures
Type of Building
25 or
2651101- 201- 401Less
50
100
200
400
600
Hospitals
1.00
1.00
.80
.60
.50
.45
Mercantile Buildings 1.30
1.00
.80
.71
.60
.54
Office Buildings
1.20
.90
.72
.65
.50
.40
Schools
1.20
.85
.65
.60
.55
.45
Hotels, Motels
.80
.60
.55
.45
.40
.35
Apartment Buildings .60
.50
.37
.30
.28
.25
12 Gallons per day
15 Gallons per day
35 Gallons per day
4 Gallons per day
2 Gallons per day
6 Gallons per day
20 Gallons per day
20-60 GPM
BOILER FEED REQUIREMENTS
HP
20
25
30
35
40
45
50
Over
600
.40
.48
.35
.33
.24
Boiler
Boiler
GPM HP
GPM
1.38 55
3.80
1.73 60
4.14
2.07 65
4.49
2.42 70
4.83
2.76 75
5.18
3.11 80
5.52
3.45 85
5.87
Boiler
HP
GPM
90
6.21
100
6.90
110
7.59
120
8.29
130
8.97
140
9.66
150
10.4
HP
160
170
180
190
200
225
250
Boiler
GPM
11.1
11.7
12.4
13.1
13.8
15.5
17.3
HP
275
300
325
350
400
450
500
Boiler
GPM
19.0
20.7
22.5
24.2
27.6
31.1
34.5
1. Boiler Horsepower equals 34.5 lb. water evaporated at and from 212ºF, and
requires feed water at a rate of 0.069 gpm.
Select the boiler feed pump with a capacity of 2 to 3 times greater than the figures given above at a pressure 20 to 25% above that of boiler, because the table
gives equivalents of boiler horsepower without reference to fluctuating demands.
1. For less than 25 fixtures, pump capacity should not be less than 75% of
capacity required for 25 fixtures.
2. Where additional water is required for some special process, this should be
added to pump capacity.
3. Where laundries or swimming pools are to be supplied, add approximately
10% to pump capacity for either.
4. Where the majority of occupants are women, add approximately 20% to
pump capacity.
6
Tank Selection
TECHNICAL DATA
Hydro-Pro® Tanks
TABLE 1 – TANK MODELS
Model
No.
V6P
V15P
V25P
V45P
V45B
V45
V60B
V60
V80
V80EX
V100
V100S
V140B
V140
V200B
V200
V250
V260
V350
Total
Volume
(Gals.)
2.0
4.5
8.2
13.9
13.9
13.9
19.9
19.9
25.9
25.9
31.8
31.8
45.2
45.2
65.1
65.1
83.5
84.9
115.9
Drawdown in Gals. at System
Pre-Chgd.
Max.
Operating Pressure Range of
System
at:
Drawdown
Connection
20/40
30/50
40/60
(lbs.)
Vol. (Gals.)
PSIG
PSIG
PSIG
0.7
0.6
0.5
1.2
38
¾" NPTM
¾" NPTM
1.7
1.4
1.2
2.7
38
3.1
2.6
2.2
4.5
38
¾" NPTM
5.1
4.3
3.7
8.4
38
1" NPTM
5.1
4.3
3.7
8.4
38
1" NPTM
5.1
4.3
3.7
8.4
38
1" NPTF
7.3
6.1
5.3
12.1
38
1" NPTM
7.3
6.1
5.3
12.1
38
1" NPTF
8.9
7.7
6.7
13.9
38
1" NPTF
8.9
7.7
6.7
13.9
38
1" NPTF
11.8
9.9
8.6
13.8
38
1" NPTF
11.8
9.9
8.6
13.8
38
1" NPTF
16.5
13.9
12.1
27.3
38
1¼" NPTM
16.5
13.9
12.1
27.3
38
1¼" NPTF
23.9
20.0
17.4
39.3
38
1¼" NPTM
23.9
20.0
17.4
39.3
38
1¼" NPTF
30.9
25.9
22.5
50.8
38
1¼" NPTF
31.2
26.2
22.8
44.7
38
1¼" NPTF
42.9
35.9
31.3
70.5
38
1¼" NPTF
Dimensions
Diameter
8
11
11
153⁄8
153⁄8
153⁄8
153⁄8
153⁄8
153⁄8
153⁄8
153⁄8
22
22
22
22
22
26
22
26
Height From
Shipping Floor to Center
Weight of Base Opening
Height
1115⁄16
1315⁄16
231⁄16
211⁄16
211⁄16
2415⁄16
28 ½
323⁄8
399⁄16
425⁄8
47¼
28
323⁄16
369⁄16
441⁄4
485⁄8
46
6011⁄16
615⁄16
7.5
11.9
21.1
23.8
22.6
23.4
32.9
33.7
43.0
43.0
51.7
51.7
62.3
64.1
86.9
88.9
116.0
113.0
161.0
31⁄8
NOTES:
P = Pipe mounted
EX = Base extension
B = Buried
MP = Mounted pump
(All dimensions are
in inches and
weight in lbs.
Do not use for
construction
purposes.)
31⁄8
7¼
31⁄8
31⁄8
33⁄8
33⁄8
3½
33⁄8
3½
TABLE 2 – PRESSURE FACTORS
25
30
35
40
45
50
Pump Cut-In Pressure – PSIG
55
60
65
70
75
80
85
30
35
.20
40
.27
.18
45
.34
.25
.17
50
.39
.31
.23
.15
55
.43
.36
.29
.22
.14
60
.47
.40
.33
.27
.20
.13
65
.50
.44
.38
.31
.25
.19
.13
70
.53
.47
.41
.35
.30
.24
.18
.12
75
.50
.45
.39
.33
.28
.22
.17
.11
80
.53
.48
.42
.37
.32
.26
.21
.16
.11
85
.50
.45
.40
.35
.30
.25
.20
.15
.10
90
.53
.48
.43
.38
.33
.29
.24
.19
.14
.10
95
.50
.46
.41
.36
.32
.27
.23
.18
.14
.09
100
.52
.48
.44
.39
.35
.31
.26
.22
.17
.13
105
.50
.46
.42
.38
.33
.29
.25
.21
.17
110
.52
.46
.44
.40
.36
.32
.28
.24
.20
115
.50
.46
.42
.39
.35
.31
.27
.23
120
.52
.48
.45
.41
.37
.33
.30
.26
125
.50
.47
.43
.39
.36
.32
.29
To determine tank drawdown of operating pressure ranges other than those listed in table, use following procedure:
Multiply total tank volume (table 1) by pressure factor (table 4).
Example: Operating range: 35/55
Tank being used: V-200
65.1 = Total volume of tank (table 1)
x .29
Pressure factor (table 4)
18.9 = Drawdown in gallons at 35/55 PSI operating range.
Pump Cut-Out Pressure – PSIG
20
.22
.30
.37
.42
.46
.50
.54
7
90
95
100
105
110
115
.09
.13
.16
.19
.22
.25
.08
.12
.15
.19
.21
.12
.15
.16
.06
.11
.14
.11
.07
Tank Selection
TECHNICAL DATA
VERTICAL
TANK TABLE
Percent of
Tank Volume
87.2
84.5 86.0
80.3 82.7
77.3
73.2
70.4
67.2
15.5%
63.0
57.7
When using large standard galvanized tanks, a constant air cushion is required for
proper operation of the water system.
The illustrations show the percent of tank volume as related to the pressure gauge
reading. To determine the amount of water you will receive as drawoff from the
tank, you should subtract the smaller number from the larger number to get the
percentage. Then multiply by the size of the tank to get the gallons drawoff.
Example:
50 lbs. = 77.3
minus 30 lbs. = 67.2
= 10.1%
x 120 gallon size
(size of tank)
= 12.12 gallons
drawoff
90
80
70
60
15
50.5
50
10
40.5
40
5
25.4
Percent of Tank Height
Gauge
Pressure
lb./sq. in.
100
90
80
70
60
50
40
35
30
25
20
30
Based on an
atmospheric
pressure of
14.7 lb./sq. in.
at sea level.
20
10
HORIZONTAL
TANK TABLE
30
25
90
70
35
86.0 87.2
84.5
82.7 80.3
77.3
73.2
70.4
67.2
63.0
90
80
70
15.5%
60
20
15
57.7
50.5
50
10
40.5
40
5
Gauge
Pressure
lb./sq. in.
25.4
Percent
of Tank Volume
30
Percent of Tank Height
100
80
60
50
40
20
10
8
Tank Selection
TECHNICAL DATA
CAPACITIES OF TANKS OF VARIOUS DIMENSIONS
Dia. in
inches
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
19
20
21
22
23
24
25
26
27
28
29
30
32
34
36
1"
0.01
0.03
0.05
0.08
0.12
0.17
0.22
0.28
0.34
0.41
0.49
0.57
0.67
0.77
0.87
0.98
1.10
1.23
1.36
1.50
1.65
1.80
1.96
2.12
2.30
2.48
2.67
2.86
3.06
3.48
3.93
4.41
1'
0.04
0.16
0.37
0.65
1.02
1.47
2.00
2.61
3.31
4.08
4.94
5.88
6.90
8.00
9.18
10.4
11.8
13.2
14.7
16.3
18.0
19.8
21.6
23.5
25.5
27.6
29.7
32.0
34.3
36.7
41.8
47.2
52.9
5'
0.20
0.80
1.84
3.26
5.10
7.34
10.0
13.0
16.5
20.4
24.6
29.4
34.6
40.0
46.0
52.0
59.0
66.0
73.6
81.6
90.0
99.0
108.0
118.0
128.0
138.0
148.0
160.0
171.0
183.0
209.0
236.0
264.0
6'
0.24
0.96
2.20
3.92
6.12
8.80
12.0
15.6
19.8
24.4
29.6
35.2
41.6
48.0
55.2
62.4
70.8
79.2
88.4
98.0
108.0
119.0
130.0
141.0
153.0
166.0
178.0
192.0
206.0
220.0
251.0
283.0
317.0
7'
0.28
1.12
2.56
4.58
7.14
10.3
14.0
18.2
23.1
28.4
34.6
41.0
48.6
56.0
64.4
72.8
81.6
92.4
103.0
114.0
126.0
139.0
151.0
165.0
179.0
193.0
208.0
224.0
240.0
257.0
293.0
330.0
370.0
8'
0.32
1.28
2.92
5.24
8.16
11.8
16.0
20.8
26.4
32.6
39.4
46.8
55.2
64.0
73.6
83.2
94.4
106.0
118.0
130.0
144.0
158.0
173.0
188.0
204.0
221.0
238.0
256.0
274.0
294.0
334.0
378.0
422.0
9'
0.36
1.44
3.30
5.88
9.18
13.2
18.0
23.4
29.8
36.8
44.4
52.8
62.2
72.0
82.8
93.6
106.0
119.0
132.0
147.0
162.0
178.0
194.0
212.0
230.0
248.0
267.0
288.0
309.0
330.0
376.0
424.0
476.0
Length of Cylinder
10'
11'
12'
13'
0.40
0.44 0.48 0.52
1.60
1.76 1.92 2.08
3.68
4.04 4.40 4.76
6.52
7.18 7.84 8.50
10.2
11.2 12.2 13.3
14.7
16.1 17.6 19.1
20.0
22.0 24.0 26.0
26.0
28.6 31.2 33.8
33.0
36.4 39.6 43.0
40.8
44.8 48.8 52.8
49.2
54.2 59.2 64.2
58.8
64.6 70.4 76.2
69.2
76.2 83.2 90.2
80.0
88.0 96.0 104.0
92.0 101.0 110.0 120.0
104.0 114.0 125.0 135.0
118.0 130.0 142.0 153.0
132.0 145.0 158.0 172.0
147.0 162.0 177.0 192.0
163.0 180.0 196.0 212.0
180.0 198.0 216.0 238.0
198.0 218.0 238.0 257.0
216.0 238.0 259.0 281.0
235.0 259.0 282.0 306.0
255.0 281.0 306.0 332.0
276.0 304.0 331.0 359.0
297.0 326.0 356.0 386.0
320.0 352.0 384.0 416.0
343.0 377.0 412.0 446.0
367.0 404.0 440.0 476.0
418.0 460.0 502.0 544.0
472.0 520.0 566.0 614.0
528.0 582.0 634.0 688.0
Capacities, in U.S. Gallons, of cylinders of various diameters and lengths.
Volume =πd 2 x H (Cylinder), L x W x H (Cube)
4
9
14'
0.56
2.24
5.12
9.16
14.3
20.6
28.0
36.4
46.2
56.8
69.2
82.0
97.2
112.0
129.0
146.0
163.0
185.0
206.0
229.0
252.0
277.0
302.0
330.0
358.0
386.0
416.0
448.0
480.0
514.0
586.0
660.0
740.0
15'
0.60
2.40
5.48
9.82
15.3
22.0
30.0
39.0
49.6
61.0
74.0
87.8
104.0
120.0
138.0
156.0
177.0
198.0
221.0
245.0
270.0
297.0
324.0
353.0
383.0
414.0
426.0
480.0
514.0
550.0
628.0
708.0
792.0
16'
0.64
2.56
5.84
10.5
16.3
23.6
32.0
41.6
52.8
65.2
78.8
93.6
110.0
128.0
147.0
166.0
189.0
211.0
235.0
261.0
288.0
317.0
346.0
376.0
408.0
442.0
476.0
512.0
548.0
588.0
668.0
756.0
844.0
17'
0.68
2.72
6.22
11.1
17.3
25.0
34.0
44.2
56.2
69.4
83.8
99.6
117.0
136.0
156.0
177.0
201.0
224.0
250.0
277.0
306.0
337.0
367.0
400.0
434.0
470.0
504.0
544.0
584.0
624.0
710.0
802.0
898.0
18'
20'
0.72
0.80
2.88
3.20
6.60
7.36
11.8
13.0
18.4
20.4
26.4
29.4
36.0
40.0
46.8
52.0
60.0
66.0
73.6
81.6
88.8
98.4
106.0 118.0
124.0 138.0
144.0 160.0
166.0 184.0
187.0 208.0
212.0 236.0
240.0 264.0
265.0 294.0
294.0 326.0
324.0 360.0
356.0 396.0
389.0 432.0
424.0 470.0
460.0 510.0
496.0 552.0
534.0 594.0
576.0 640.0
618.0 686.0
660.0 734.0
752.0 836.0
848.0 944.0
952.0 1056.0
22'
0.88
3.52
8.08
14.4
22.4
32.2
44.0
57.2
72.4
89.6
104.0
129.0
152.0
176.0
202.0
229.0
260.0
290.0
324.0
359.0
396.0
436.0
476.0
518.0
562.0
608.0
652.0
704.0
754.0
808.0
920.0
1040.0
1164.0
24'
0.96
3.84
8.80
15.7
24.4
35.2
48.0
62.4
79.2
97.6
118.0
141.0
166.0
192.0
220.0
250.0
283.0
317.0
354.0
392.0
432.0
476.0
518.0
564.0
612.0
662.0
712.0
768.0
824.0
880.0
1004.0
1132.0
1268.0
Centrifugal Pump
Fundamentals
TECHNICAL DATA
NET POSITIVE SUCTION HEAD (NPSH) AND CAVITATION
The Hydraulic Institute defines NPSH as the total suction head in
feet absolute, determined at the suction nozzle and corrected to
datum, less the vapor pressure of the liquid in feet absolute.
Simply stated, it is an analysis of energy conditions on the suction
side of a pump to determine if the liquid will vaporize at the
lowest pressure point in the pump.
The pressure which a liquid exerts on its surroundings is dependent upon its temperature. This pressure, called vapor pressure, is
a unique characteristic of every fluid and increases with increasing
temperature. When the vapor pressure within the fluid reaches the
pressure of the surrounding medium, the fluid begins to vaporize or boil. The temperature at which this vaporization occurs will
decrease as the pressure of the surrounding medium decreases.
A liquid increases greatly in volume when it vaporizes. One cubic
foot of water at room temperature becomes 1700 cu. ft. of vapor
at the same temperature.
It is obvious from the above that if we are to pump a fluid
effectively, we must keep it in liquid form. NPSH is simply a
measure of the amount of suction head present to prevent this
vaporization at the lowest pressure point in the pump.
NPSH Required is a function of the pump design. As the liquid
passes from the pump suction to the eye of the impeller, the
velocity increases and the pressure decreases. There are also
pressure losses due to shock and turbulence as the liquid strikes
the impeller. The centrifugal force of the impeller vanes further
increases the velocity and decreases the pressure of the liquid. The
NPSH Required is the positive head in feet absolute required at the
pump suction to overcome these pressure drops in the pump and
maintain the liquid above its vapor pressure. The NPSH Required
varies with speed and capacity within any particular pump. Pump
manufacturer’s curves normally provide this information.
NPSH Available is a function of the system in which the pump
operates. It is the excess pressure of the liquid in feet absolute
over its vapor pressure as it arrives at the pump suction. Fig. 4
shows four typical suction systems with the NPSH Available formulas applicable to each. It is important to correct for the specific
gravity of the liquid and to convert all terms to units of “feet
absolute” in using the formulas.
In an existing system, the NPSH Available can be determined by a
gage reading on the pump suction. The following formula applies:
NPSHA = PB - VP ± Gr + hV
Where Gr = Gage reading at the pump suction expressed in feet
(plus if above atmospheric, minus if below
atmospheric) corrected to the pump centerline.
hv = Velocity head in the suction pipe at the gage
connection, expressed in feet.
Cavitation is a term used to describe the phenomenon which
occurs in a pump when there is insufficient NPSH Available. The
pressure of the liquid is reduced to a value equal to or below its
vapor pressure and small vapor bubbles or pockets begin to form.
As these vapor bubbles move along the impeller vanes to a higher
pressure area, they rapidly collapse.
The collapse, or “implosion” is so rapid that it may be heard as a
rumbling noise, as if you were pumping gravel. The forces during
the collapse are generally high enough to cause minute pockets of
fatigue failure on the impeller vane surfaces. This action may be
progressive, and under severe conditions can cause serious pitting
damage to the impeller.
The accompanying noise is the easiest way to recognize cavitation.
Besides impeller damage, cavitation normally results in reduced
capacity due to the vapor present in the pump. Also, the head
may be reduced and unstable and the power consumption may be
erratic. Vibration and mechanical damage such as bearing failure
can also occur as a result of operating in cavitation.
The only way to prevent the undesirable effects of cavitation is to
insure that the NPSH Available in the system is greater than the
NPSH Required by the pump.
10
Centrifugal Pump
Fundamentals
TECHNICAL DATA
NET POSITIVE SUCTION HEAD (NPSH) AND CAVITATION
4a SUCTION SUPPLY OPEN TO ATMOSPHERE
– with Suction Lift
4b SUCTION SUPPLY OPEN TO ATMOSPHERE
– with Suction Head
PB
CL
PB
NPSHA = PB + LH – (VP + hf)
LH
LS
CL
NPSHA = PB – (VP + LS + hf)
4c CLOSED SUCTION SUPPLY
– with Suction Lift
4d CLOSED SUCTION SUPPLY
– with Suction Head
p
LS
NPSHA = p + LH – (VP + hf)
LH
CL
CL
NPSHA = p – (LS + VP + hf)
p
PB = Barometric pressure, in feet absolute.
VP = Vapor pressure of the liquid at maximum pumping temperature, in feet absolute (see next page).
p = Pressure on surface of liquid in closed suction tank, in feet absolute.
LS = Maximum static suction lift in feet.
LH = Minimum static suction head in feet.
hf = Friction loss in feet in suction pipe at required capacity.
Note: See page 25, atmospheric pressure chart.
11
Centrifugal Pump
Fundamentals
TECHNICAL DATA
VAPOR PRESSURE OF WATER
35
30
Deduct Vapor Pressure in
Feet of Water From the
Maximum Allowable Suction
Head at Sea Level.
Vapor Pressure in Feet of Water
25
20
15
10
5
40
60
80
100
120
140
Water Temperature ºF.
12
160
180
200
220
Electrical Data
TECHNICAL DATA
TRANSFORMER SIZES
A full three phase supply is recommended for all three phase
motors, consisting of three individual transformers or one three
phase transformer. “Open” delta or wye connections using only
two transformers can be used, but are more likely to cause
problems from current unbalance.
Transformer ratings should be no smaller than listed in the table
for supply power to the motor alone.
TRANSFORMER CAPACITY REQUIRED
FOR SUBMERSIBLE MOTORS
Submersible
3ø Motor
HP Rating
Total Effective
KVA
Required
1½
2
3
5
7½
10
15
20
25
30
40
50
60
75
100
3
4
5
7½
10
15
20
25
30
40
50
60
75
90
120
Smallest KVA Rating –
Each Transformer
Open WYE
WYE or
DELTA 2
DELTA 3
Transformers
Transformers
2
1
2
1½
3
2
5
3
7½
5
10
5
15
7½
15
10
20
10
25
15
30
20
35
20
40
25
50
30
65
40
OPEN DELTA OR WYE
FULL THREE PHASE
13
Application
TECHNICAL DATA
Three Phase Motors
THREE PHASE POWER UNBALANCE
Phase designation of leads for CCW rotation viewing shaft
end.
To reverse rotation, interchange any two leads.
Phase 1 or “A” – Black Motor Lead or T1
Phase 2 or “B” – Yellow Motor Lead or T2
Phase 3 or “C” – Red Motor Lead or T3
Notice: Phase 1, 2 and 3 may not be L1, L2 and L3.
A full three phase supply is recommended for all three phase
motors, consisting of three individual transformers or one three
phase transformer. So-called “open” delta or wye connections
using only two transformers can be used, but are more likely to
cause problems, such as poor performance overload tripping or
early motor failure due to current unbalance.
Transformer ratings should be no smaller than listed on
Transformer Size Chart on previous page.
Checking and correcting rotation and current unbalance
1. Establish correct motor rotation by running in both directions.
Change rotation by exchanging any two of the three motor
leads. The rotation that gives the most water flow is always
the correct rotation.
2. After correct rotation has been established, check the current
in each of the three motor leads and calculate the current
unbalance as explained in 3 below.
If the current unbalance is 2% or less, leave the leads as connected.
If the current unbalance is more than 2%, current readings
should be checked on each leg using each of the three possible hook-ups. Roll the motor leads across the starter in the
same direction to prevent motor reversal.
3. To calculate percent of current unbalance:
A. Add the three line amp values together.
B. Divide the sum by three, yielding average current.
C. Pick the amp value which is furthest from the average current (either high or low).
D. Determine the difference between this amp value (furthest
from average) and the average.
E. Divide the difference by the average.
Multiply the result by 100 to determine percent of
unbalance.
4. Current unbalance should not exceed 5% at service factor load
or 10% at rated input load. If the unbalance cannot be corrected by rolling leads, the source of the unbalance must be
located and corrected. If, on the three possible hookups, the
leg farthest from the average stays on the same power lead,
most of the unbalance is coming from the power source. However, if the reading farthest from average moves with the same
motor lead, the primary source of unbalance is on the “motor
side” of the starter. In this instance, consider a damaged cable,
leaking splice, poor connection, or faulty motor winding.
L1
Hookup 1
L2 L3
L1
Hookup 2
L2 L3
L1
Hookup 3
L2
L3
Starter
Terminals
Motor
Leads
T1
T2
T3
T1
T2
T3
T1
T2
T3
R
T3
B
T1
Y
T2
Y
T2
R
T3
B
T1
B
T1
Y
T2
R
T3
Example:
T3-R = 51 amps
T1-B = 46 amps
T2-Y = 53 amps
Total = 150 amps
÷ 3 = 50 amps
— 46 = 4 amps
4 ÷ 50 = .08 or 8%
T2-Y = 50 amps
T3-R = 48 amps
T1-B = 52 amps
Total = 150 amps
÷ 3 = 50 amps
— 48 = 2 amps
2 ÷ 50 = .04 or 4%
T1-B = 50 amps
T2-Y = 49 amps
T3-R = 51 amps
Total = 150 amps
÷ 3 = 50 amps
— 49 = 1 amps
1 ÷ 50 = .02 or 2%
OPEN DELTA
OR WYE
FULL THREE
PHASE
FIGURE 12
14
Electrical Data
TECHNICAL DATA
NEMA CONTROL PANEL ENCLOSURES
Enclosure Rating
NEMA 1
Purpose
NEMA 2
Driptight
NEMA 3
Weatherproof
(Weatherproof Resistant)
NEMA 3R
tight
NEMA 4
Watertight
NEMA 4X
Watertight & Corrosion Resistant
NEMA 5
Dusttight
NEMA 6
Watertight, Dusttight
NEMA 7
Locations
Class I
NEMA 8
Hazardous Locations
A, B, C or D
Class II – Oil Immersed
NEMA 9
Class II – Locations
NEMA 10
Bureau of Mines
Permissible
NEMA 11
Dripproof
Corrosion Resistant
NEMA 12
Driptight, Dusttight
Explanation
To prevent accidental contact with enclosed apparatus. Suitable for application indoors where not General
exposed to unusual service conditions.
To prevent accidental contact, and in addition, to exclude falling moisture or dirt.
Protection against specified weather hazards. Suitable for use outdoors.
Protects against entrance of water from a beating rain. Suitable for general outdoor application not Rainrequiring sleetproof.
Designed to exclude water applied in form of hose stream. To protect against stream of water during
cleaning operations, etc.
Designed to exclude water applied in form of hose stream. To protect against stream of water during
cleaning operations, etc. Corrosion Resistant.
Constructed so that dust will not enter enclosed case. Being replaced in some equipment by Dust Tight
NEMA 12.
Intended to permit enclosed apparatus to be operated successfully when temporarily submerged in
water.
Designed to meet application requirements of National Electrical Code for Class 1, Hazardous Hazardous
Locations (explosive atmospheres). Circuit interruption occurs in air.
Identical to NEMA 7 above, except the apparatus is immersed in oil.
Designed to meet application requirements of National Electrical Code for Class II Hazardous Hazardous
Locations (combustible dusts, etc.). E, F and G.
Meets requirements of U.S. Bureau of Mines. Suitable for use in coal mines.
Provides oil immersion of apparatus such that it is suitable for application where equipment is
subject to acid or other corrosive fumes.
For use in those industries where it is desired to exclude dust, lint, fibers and flyings, or oil or Industrial
coolant seepage.
15
Determining Water
Level
TECHNICAL DATA
Install 1⁄8" or ¼" tubing long
enough to be 10' to 15' below
low water level. Measure the
tubing length as it is lowered
into the well.
Once the tubing is fixed in a
stationary position at the top,
connect an air line and pressure gauge. Add air to
the tubing until the pressure
gauge reaches a point that it
doesn't read any higher. Take
a gauge reading at this point.
A. Depth to water
(to be determined).
B. Total length of air line
(in feet).
C. Water pressure on air
tubing. Gauge reads in
pounds. Convert to feet by
multiplying by 2.31.
Example:
If the air tube is 100' long,
and the gauge reads 20 lbs.
20 lbs. x 2.31 = 46.2 ft.
Length of tube = 100 ft.
minus 46.2 ft. = 53.8 ft.
Depth to water (A) would
be 53.8 ft.
C
A
B
16
Tail Pipe
TECHNICAL DATA
HOW TO USE TAIL PIPE ON DEEP WELL JET PUMPS
Pipe below the jet, or “tail
pipe” as it is commonly
known, is used when you
have a weak deep well. Under
normal conditions, the jet
assembly with the foot valve
attached is lowered into the
well. You receive your rated
capacity at the level you locate
the jet assembly. On a weak
well, as the water level lowers
to the level of the foot valve
(attached to the bottom of the
jet assembly), air enters the
system. By adding 34' of tail
pipe below the jet assembly
with the foot valve attached to
the bottom of the 34' length
of pipe, it will not be possible
to pull the well down and
allow air to enter the system.
The drawing indicates the approximate percentage of rated
capacity you will receive with
tail pipe.
Using a tail pipe, the pump
delivery remains at 100% at
sea level of the rated capacity down to the jet assembly
level. If water level falls below
that, flow decreases in proportion to drawdown as shown
in the illustration. When pump
delivery equals well inflow,
the water level remains constant until the pump shuts off.
This rule can also be used
when determining suction
pipe length on shallow well
systems.
STATIC LEVEL
DRIVE PIPE
SUCTION PIPE
JET ASSEMBLY
100%
10' PIPE 80%
15' PIPE 70%
20' PIPE 57%
TAIL PIPE
34 FT. WILL PREVENT
BREAKING SUCTION
25' PIPE 40%
28' PIPE 25%
29' PIPE 17%
33.9' MAXIMUM
DRAW DOWN 0%
17
Determining Flow
Rates
TECHNICAL DATA
FULL PIPE FLOW – CALCULATION OF DISCHARGE RATE USING HORIZONTAL OPEN DISCHARGE FORMULA
An L-shaped measuring square can be used to estimate flow
capacity, using the chart below. As shown in illustration, place 4"
side of square so that it hangs down and touches the water. The
horizontal distance shown “A” is located in the first column of the
chart and you read across to the pipe diameter (ID) to find the
gallons per minute discharge rate.
Example: A is 8" from a 4" ID pipe
= a discharge rate of 166 GPM.
A
4"
PIPE NOT RUNNING FULL – CALCULATION OF DISCHARGE RATE USING AREA FACTOR METHOD
D
F
12"
Flow From Horizontal Pipe (Not Full)
Flow (GPM) = A x D x 1.093 x F
A = Area of pipe in square inches
D = Horizontal distance in inches
F = Effective area factor shown below
Area of pipe equals inside Dia.2 x 0.7854
Example:
D = 20 inches – Pipe inside diameter = 10 inches –
F = 21⁄2 inches
A = 10 x 10 x 0.7854 = 78.54 square inches
R = 21⁄2/10 = 25%
F = 0.805
Flow = 78.54 x 20 x 1.039 x 0.805 = 1314 GPM
Ratio
F/D = R %
5
10
15
20
25
30
35
40
45
50
Eff. Area
Factor F
0.981
0.948
0.905
0.858
0.805
0.747
0.688
0.627
0.564
0.500
Ratio
F/D = R %
55
60
65
70
75
80
85
90
95
100
Eff. Area
Factor F
0.436
0.373
0.312
0.253
0.195
0.142
0.095
0.052
0.019
0.000
DISCHARGE RATE IN GALLONS PER MINUTE/NOMINAL PIPE SIZE (ID)
Horizontal
Dist. (A)
Inches
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
19
20
21
22
23
24
1"
1¼"
1½"
2"
2½"
3"
4"
5.7
7.1
8.5
10.0
11.3
12.8
14.2
15.6
17.0
18.5
20.0
21.3
22.7
9.8
12.2
14.7
17.1
19.6
22.0
24.5
27.0
29.0
31.5
34.0
36.3
39.0
41.5
13.3
16.6
20.0
23.2
26.5
29.8
33.2
36.5
40.0
43.0
46.5
50.0
53.0
56.5
60.0
22.0
27.5
33.0
38.5
44.0
49.5
55.5
60.5
66.0
71.5
77.0
82.5
88.0
93.0
99.0
110
31.3
39.0
47.0
55.0
62.5
70.0
78.2
86.0
94.0
102
109
117
125
133
144
148
156
48.5
61.0
73.0
85.0
97.5
110
122
134
146
158
170
183
196
207
220
232
244
256
83.5
104
125
146
166
187
208
229
250
270
292
312
334
355
375
395
415
435
460
18
5"
163
195
228
260
293
326
360
390
425
456
490
520
550
590
620
650
685
720
750
6"
8"
10"
285
334
380
430
476
525
570
620
670
710
760
810
860
910
950
1000
1050
1100
1140
380
665
750
830
915
1000
1080
1160
1250
1330
1410
1500
1580
1660
1750
1830
1910
2000
1060
1190
1330
1460
1600
1730
1860
2000
2120
2260
2390
2520
2660
2800
2920
3060
3200
12"
1660
1850
2100
2220
2400
2590
2780
2960
3140
3330
3500
3700
Determining Flow
Rates
TECHNICAL DATA
THEORETICAL DISCHARGE OF NOZZLES IN U.S. GALLONS PER MINUTE
Head
Pounds
10
15
20
25
30
35
40
45
50
55
60
65
70
75
80
85
90
95
100
105
110
115
120
125
130
135
140
145
150
175
200
Feet
23.1
34.6
46.2
57.7
69.3
80.8
92.4
103.9
115.5
127.0
138.6
150.1
161.7
173.2
184.8
196.3
207.9
219.4
230.9
242.4
254.0
265.5
277.1
288.6
300.2
311.7
323.3
334.8
346.4
404.1
461.9
Velocity of
Discharge
Feet
Per Second
38.6
47.25
54.55
61.0
66.85
72.2
77.2
81.8
86.25
90.4
94.5
98.3
102.1
105.7
109.1
112.5
115.8
119.0
122.0
125.0
128.0
130.9
133.7
136.4
139.1
141.8
144.3
146.9
149.5
161.4
172.6
Diameter of Nozzle in Inches
⁄16
1
0.37
0.45
0.52
0.58
0.64
0.69
0.74
0.78
0.83
0.87
0.90
0.94
0.98
1.01
1.05
1.08
1.11
1.14
1.17
1.20
1.23
1.25
1.28
1.31
1.33
1.36
1.38
1.41
1.43
1.55
1.65
⁄8
1
1.48
1.81
2.09
2.34
2.56
2.77
2.96
3.13
3.30
3.46
3.62
3.77
3.91
4.05
4.18
4.31
4.43
4.56
4.67
4.79
4.90
5.01
5.12
5.22
5.33
5.43
5.53
5.62
5.72
6.18
6.61
⁄16
⁄4
3
1
3.32
4.06
4.69
5.25
5.75
6.21
6.64
7.03
7.41
7.77
8.12
8.45
8.78
9.08
9.39
9.67
9.95
10.2
10.5
10.8
11.0
11.2
11.5
11.7
12.0
12.2
12.4
12.6
12.9
13.9
14.8
5.91
7.24
8.35
9.34
10.2
11.1
11.8
12.5
13.2
13.8
14.5
15.1
15.7
16.2
16.7
17.3
17.7
18.2
18.7
19.2
19.6
20.0
20.5
20.9
21.3
21.7
22.1
22.5
22.9
24.7
26.4
⁄8
3
13.3
16.3
18.8
21.0
23.0
24.8
26.6
28.2
29.7
31.1
32.5
33.8
35.2
36.4
37.6
38.8
39.9
41.0
42.1
43.1
44.1
45.1
46.0
47.0
48.0
48.9
49.8
50.6
51.5
55.6
59.5
⁄2
1
23.6
28.9
33.4
37.3
40.9
44.2
47.3
50.1
52.8
55.3
57.8
60.2
62.5
64.7
66.8
68.9
70.8
72.8
74.7
76.5
78.4
80.1
81.8
83.5
85.2
86.7
88.4
89.9
91.5
98.8
106
⁄8
5
36.9
45.2
52.2
58.3
63.9
69.0
73.8
78.2
82.5
86.4
90.4
94.0
97.7
101
104
108
111
114
117
120
122
125
128
130
133
136
138
140
143
154
165
⁄4
3
53.1
65.0
75.1
84.0
92.0
99.5
106
113
119
125
130
136
141
146
150
155
160
164
168
172
176
180
184
188
192
195
199
202
206
222
238
⁄8
7
72.4
88.5
102
114
125
135
145
153
162
169
177
184
191
198
205
211
217
223
229
234
240
245
251
256
261
266
271
275
280
302
323
Note:
The actual quantities will vary from these figures, the amount of variation depending upon the shape of nozzle and size of pipe at the point where the pressure is
determined. With smooth taper nozzles the actual discharge is about 94 percent of the figures given in the tables.
19
Determining Flow
Rates
TECHNICAL DATA
THEORETICAL DISCHARGE OF NOZZLES IN U.S. GALLONS PER MINUTE (continued)
Head
Pounds
10
15
20
25
30
35
40
45
50
55
60
65
70
75
80
85
90
95
100
105
110
115
120
125
130
135
140
145
150
175
200
Feet
23.1
34.6
46.2
57.7
69.3
80.8
92.4
103.9
115.5
127.0
138.6
150.1
161.7
173.2
184.8
196.3
207.9
219.4
230.9
242.4
254.0
265.5
277.1
288.6
300.2
311.7
323.3
334.8
346.4
404.1
461.9
Velocity of
Discharge
Feet
Per Second
38.6
47.25
54.55
61.0
66.85
72.2
77.2
81.8
86.25
90.4
94.5
98.3
102.1
105.7
109.1
112.5
115.8
119.0
122.0
125.0
128.0
130.9
133.7
136.4
139.1
141.8
144.3
146.9
149.5
161.4
172.6
Diameter of Nozzle in Inches
1
1
1 ⁄8
1
1 ⁄4
13⁄8
11⁄2
13⁄4
2
21⁄4
21⁄2
94.5
116
134
149
164
177
188
200
211
221
231
241
250
259
267
276
284
292
299
306
314
320
327
334
341
347
354
360
366
395
423
120
147
169
189
207
224
239
253
267
280
293
305
317
327
338
349
359
369
378
388
397
406
414
423
432
439
448
455
463
500
535
148
181
209
234
256
277
296
313
330
346
362
376
391
404
418
431
443
456
467
479
490
501
512
522
533
543
553
562
572
618
660
179
219
253
283
309
334
357
379
399
418
438
455
473
489
505
521
536
551
565
579
593
606
619
632
645
656
668
680
692
747
790
213
260
301
336
368
398
425
451
475
498
521
542
563
582
602
620
638
656
672
689
705
720
736
751
767
780
795
809
824
890
950
289
354
409
458
501
541
578
613
647
678
708
737
765
792
818
844
868
892
915
937
960
980
1002
1022
1043
1063
1082
1100
1120
1210
1294
378
463
535
598
655
708
756
801
845
886
926
964
1001
1037
1070
1103
1136
1168
1196
1226
1255
1282
1310
1338
1365
1390
1415
1440
1466
1582
1691
479
585
676
756
828
895
957
1015
1070
1121
1172
1220
1267
1310
1354
1395
1436
1476
1512
1550
1588
1621
1659
1690
1726
1759
1790
1820
1853
2000
2140
591
723
835
934
1023
1106
1182
1252
1320
1385
1447
1506
1565
1619
1672
1723
1773
1824
1870
1916
1961
2005
2050
2090
2132
2173
2212
2250
2290
2473
2645
Note:
The actual quantities will vary from these figures, the amount of variation depending upon the shape of nozzle and size of pipe at the point where the pressure is
determined. With smooth taper nozzles the actual discharge is about 94 percent of the figures given in the tables.
20
Terms and Usable
Formulas
TECHNICAL DATA
CALCULATING SUCTION LIFT
Suction lift is measured with a vacuum gauge.
The gauge can be calibrated in feet suction lift
or inches vacuum.
A. 1 inch vacuum equals 1.13 feet
suction lift.
22.6'
Vertical Lift
Plus Friction
C. Atmospheric pressure of 14.7 x 2.31 =
33.9 feet which is the maximum suction lift at sea level.
Vacuum
Gauge
14.7 lbs.
x 2.31 ft.
33.9 ft.
20"
B.
A.
C.
2.31 ft.
14.7 lbs.
1 lb.
A reading of 20" on a vacuum gauge placed on the
suction side of the pump would tell you that you had a
vacuum or suction lift of 22.6 feet.
20" x 1.13' = 22.6 feet
A vacuum gauge indicates total suction lift (vertical lift + friction
loss = total lift) in inches of mercury. 1" on the gauge = 1.13 ft.
of total suction lift (based on pump located at sea level).
very high vacuum (22 inches or more), this indicates that the end
of suction pipe is buried in mud, the foot valve or check valve is
stuck closed or the suction lift exceeds capability of pump.
RULE OF THUMB
Practical suction lift at sea level is 25 ft. Deduct 1 ft. of
suction lift for each 1000 ft. of elevation above sea level.
High Vacuum (22 inches or more)
• Suction pipe end buried in mud
• Foot valve or check valve stuck closed
• Suction lift exceeds capability of the pump
Shallow Well System
Install vacuum gauge in shallow well adapter. When pump is
running, the gauge will show no vacuum if the end of suction pipe
is not submerged or there is a suction leak. If the gauge shows a
Low Vacuum (or 0 vacuum)
• Suction pipe not submerged
• Suction leak
21
Terms and Usable
Formulas
TECHNICAL DATA
The term “head” by itself is
rather misleading. It is
commonly taken to mean the
difference in elevation
between the suction level and
the discharge level of the liquid
being pumped. Although this
is partially correct, it does not
include all of the conditions
that should be included to give
an accurate description.
■ Friction Head:
The pressure expressed in lbs./
sq. in. or feet of liquid needed
to overcome the resistance to
the flow in the pipe and
fittings.
■ Suction Lift: Exists when
the source of supply is below
the center line of the pump.
■ Suction Head: Exists when
the source of supply is above
the center line of the pump.
■ Static Suction Lift:
The vertical distance from
the center line of the pump
down to the free level of the
liquid source.
■ Static Suction Head:
The vertical distance from the
center line of the pump up
to the free level of the liquid
source.
■ Static Discharge Head:
The vertical elevation from the
center line of the pump to the
point of free discharge.
■ Dynamic Suction Lift:
Includes static suction lift,
friction head loss and velocity
head.
■ Dynamic Suction Head:
Includes static suction head
minus friction head minus
velocity head.
■ Dynamic Discharge Head:
Includes static discharge head
plus friction head plus velocity
head.
■ Total Dynamic Head:
Includes the dynamic discharge
head plus dynamic suction lift
or minus dynamic suction head.
■ Velocity Head: The head
needed to accelerate the
liquid. Knowing the velocity
of the liquid, the velocity head
loss can be calculated by a
simple formula Head = V2/2g
in which g is acceleration due
to gravity or 32.16 ft./sec.
Although the velocity head
loss is a factor in figuring the
dynamic heads, the value is
usually small and in most cases
negligible. See table.
BASIC FORMULAS AND SYMBOLS
Formulas
GPM = Lb./Hr.
500 x Sp. Gr.
BHP = GPM x H x Sp. Gr.
3960 x Eff.
H = 2.31 x psi
Sp. Gr.
Eff. = GPM x H x Sp. Gr.
3960 x BHP
H = 1.134 x In. Hg.
Sp. Gr.
NS = N√GPM
H3/4
HV = V2 = 0.155 V2
2g
H = V2
2g
Approximate Cost of Operating Electric Motors
Motor
HP
⁄3
⁄2
3
⁄4
1
11⁄2
2
3
5
71⁄2
10
1
1
V = GPM x 0.321 = GPM x 0.409
A
(I.D.)2
Symbols
GPM = gallons per minute
Lb.
= pounds
Hr.
= hour
Sp. Gr. = specific gravity
H
= head in feet
psi
= pounds per square inch
In. Hg. = inches of mercury
hv
= velocity head in feet
V
= velocity in feet per second
g
= 32.16 ft./sec.2
(acceleration of gravity)
A
= area in square inches (πr2)
(for a circle or pipe)
ID = inside diameter in inches
BHP = brake horsepower
Eff. = pump efficiency
expressed as a decimal
NS = specific speed
N = speed in revolutions
per minute
D = impeller in inches
22
*Average kilowatts input
or cost based on 1 cent
per kilowatt hour
1 Phase
3 Phase
.408
.535
.520
.760
.768
1.00
.960
1.50
1.41
2.00
1.82
2.95
2.70
4.65
4.50
6.90
6.75
9.30
9.00
Motor
HP
20
25
30
40
50
60
75
100
125
150
200
*Av. kw input or cost
per hr. based on
1 cent per kw hour
3 Phase
16.9
20.8
26.0
33.2
41.3
49.5
61.5
81.5
102
122
162
Terms and Usable
Formulas
TECHNICAL DATA
BASIC FORMULAS AND SYMBOLS
Temperature conversion
DEG. C = (DEG. F – 32) x .555
DEG. F = (DEG. C x 1.8) + 32
d
Area of a Circle
A = area; C = circumference.
A = π r2; π = 3.14
C = 2π r
r
CIRCLE
D = diameter
r = radius
Water Horsepower = GPM x 8.33 x Head = GPM x Head
33000
3960
Where:
GPM
8.33
33000
Head
Laboratory BHP = Head x GPM x Sp. Gr.
3960 x Eff.
Field BHP = Laboratory BHP + Shaft Loss
Total BHP = Field BHP + Thrust Bearing Loss
Where:
GPM = Gallons per Minute
Head = Lab. Head (including column loss)
Eff. = Lab. Eff. of Pump Bowls
Shaft Loss = HP loss due to mechanical friction of lineshaft bearings
Thrust Bearing Loss = HP Loss in driver thrust bearings
(See (1) below under Misc.)
Input Horsepower =Total BPH
Motor Eff.
Motor Eff. from Motor mfg. (as a decimal)
Field Efficiency = Water Horsepower
Total BHP
Water HP as determined above
Total BHP as determined above
Overall Plant Efficiency =Water Horsepower
Input Horsepower
(See (2) below under Misc.)
Water HP as determined above
Input HP as determined above
= Gallons per Minute
= Pounds of water per gallon
= Ft. Lbs. per minute in one horsepower
= Difference in energy head in feet (field head).
Input Horsepower= BHP = 4.826 x K x M x R = 1.732 x E x I x PF
Mot. Eff.
T
746
Electrical
BHP
= Brake Horsepower as determined above
Mot. Eff. = Rated Motor Efficiency
K
= Power Company Meter Constant
M
= Power Company Meter Multiplier, or Ratio of Current and Potential
Transformers connected with meter
R
= Revolutions of meter disk
T
= Time in Sec. for R
E
= Voltage per Leg applied to motor
I
= Amperes per Leg applied to motor
PF
= Power factor of motor
1.732 = Factor for 3-phase motors. This reduces to 1 for single phase motors
Kilowatt input to Motor = .746 x I.H.P. = 1.732 x E x I x PF
1000
KW-Hrs. Per 1000 Gallons of Cold Water Pumped Per Hour = HD in ft. x 0.00315
Pump Eff. x Mot. Eff.
(1) Thrust Bearing Loss = .0075 HP per 100 RPM per 1000 lbs. thrust.*
(2) Overall Plant Efficiency sometimes referred to as “Wire to Water” Efficiency
*Thrust (in lbs.) = (thrust constant (k) laboratory head) + (setting in feet x shaft wt. per ft.)
Note: Obtain thrust constant from curve sheets
Miscellaneous
Discharge Head (in feet of fluid pumped) = Discharge Pressure (psi) x 2.31
Sp. Gr. of Fluid Pumped
23
Affinity Laws
TECHNICAL DATA
The affinity laws express the mathematical
relationship between several variables involved
in pump performance. They apply to all types of
centrifugal and axial flow pumps. They are as
follows:
Q
= Capacity, GPM
H
= Total Head, Feet
BHP = Brake Horsepower
N
= Pump Speed, RPM
D
= Impeller Diameter (in.)
()
()
Equation 5 H2 = D2
D1
2
Equation 6 BHP2 = D2
D1
3
3
The 6 inch information is put into the
formulas and the new 5 inch diameter
point is calculated:
Q2 = 5" dia. x 200 GPM = 167 GPM
6" dia.
2
6. BHP1 = D1
BHP2
D2
3
6” DIA.
120
x BHP1
()
()
5. H1 = D1
H2
D2
FIGURE 1
140
x H1
4. Q1 = D1
Q2
D2
Use equations
4 through 6
with impeller
diameter
changes and
speed
remains
constant
2
3. BHP1 = N1
BHP2
N2
Equation 4 Q2 = D2 x Q1
D1
POINT 1
100
5” DIA.
80
POINT 2
60
40
20
0
0
100
200
300
CAPACITY (Q)
400 GPM
( )
( )
The 5 inch diameter Head/Capacity performance point can be plotted on the graph
(figure 1; point 2). By taking additional Head/Capacity points on the 6" diameter
curve line and using this procedure, a new Head/Capacity curve line can be
produced for the 5 inch diameter impeller.
3
BHP2 = 5" dia. x 7.5 BHP = 4.3 BHP This same procedure and equations 1 through 3 can be used when pump speed
6" dia.
changes and the impeller diameter remains constant.
H2 = 5" dia.
6" dia.
Calculating impeller trim using
Affinity Laws:
Example:
Assume a requirement of 225 GPM
at 160' of Head (point 2, figure 2).
Note this point falls between 2
existing curve lines with standard
impeller diameters. To determine the
trimmed impeller diameter to meet
our requirement, draw a line from the
required point (point 2) perpendicular to an existing curve line (point
1). Notice point 1 has an impeller
diameter (D1) of 63⁄4" and produces
230 GPM (Q1) at 172' TDH (H1).
Applying Affinity Law 5 to solve for
our new impeller diameter (D2).
()
()
2. H1 = N1
H2
N2
TOTAL HEAD (H)
To illustrate the use of these laws, lets
look at a particular point (1) on a pump
curve (figure 1). The diameter of the impeller
for this curve is 6 inches. We will determine
by the use of the Affinity Laws what
happens to this point if we trim the impeller
to 5 inches.
From the 6 inch diameter curve we
obtain the following information:
D1 = 6" Dia.
D2 = 5" Dia.
Q1 = 200 GPM Q2 = To be determined
H1 = 100 Ft.
H2 = To be determined
BHP1 = 7.5 HP BHP2 = To be determined
The equations 4 through 6 above with
speed (N) held constant will be used and
rearranged to solve for the following:
1. Q1 = N1
Q2
N2
Use equations
1 through 3
when speed
changes and
impeller
diameter
remains
constant
2
x 100 Ft. = 69 Ft.
Point 1 (Known)
D1 = 63⁄4" Dia. Impeller
H1 = 172' TDH
Q1 = 230 GPM
Point 2 (Unknown)
D2 = Unknown
H2 = 160' TDH
Q2 = 225 GPM
Rearranging law 5 to solve for D2 :
D2 = D1 x
FIGURE 2
240
200
63⁄4"
EFF. 40
DIA. 50
8'
60
65
70
10'
12'
73
POINT 1
160 57⁄8"
120
POINT 2
15'
73
20'
70
65
53⁄8"
60
45⁄8"
80
15
41⁄8"
40
3
H2
H1
0
0
50
HP
5
7.
5
HP
10
HP
HP
HP
100 150 200 250 300 350 400 GPM
CAPACITY (Q)
Determine that the new impeller will meet the required capacity:
Rearranging law 4 to solve for Q2 :
Q2 = D2 x Q1 = 6.55 x 230 = 223
D1
6.75
D2 = 6.75 x
160
172
D2 = 6.55 = 69⁄16"
24
Conversion Charts
TECHNICAL DATA
ATMOSPHERIC PRESSURE, BAROMETER READING AND
BOILING POINT OF WATER AT VARIOUS ALTITUDES
DECIMAL AND MILLIMETER EQUIVALENTS OF FRACTION
Inches
Fractions Decimals
1
⁄64
.015625
1
⁄32
.03125
3
⁄64
.046875
1
⁄16
.0625
5
⁄64
.078125
3
⁄32
.09375
7
⁄64
.109375
1
⁄8
.125
9
⁄64
.140625
5
⁄32
.15625
11
⁄64
.171875
3
⁄16
.1875
13
⁄64
.203125
7
⁄32
.21875
15
⁄64
.234375
1
⁄4
.250
17
⁄64
.265625
9
⁄32
.28125
19
⁄64
.296875
5
⁄16
.3125
21
⁄64
.328125
11
⁄32
.34375
23
⁄64
.359375
3
⁄8
.375
25
⁄64
.390625
13
⁄32
.40625
27
⁄64
.421875
7
⁄16
.4375
29
⁄64
.453125
15
⁄32
.46875
31
⁄64
.484375
1
⁄2
.500
Millimeters
.397
.794
1.191
1.588
1.984
2.381
2.778
3.175
3.572
3.969
4.366
4.763
5.159
5.556
5.953
6.350
6.747
7.144
7.541
7.938
8.334
8.731
9.128
9.525
9.922
10.319
10.716
11.113
11.509
11.906
12.303
12.700
Inches
Fractions Decimals
33
⁄64
.515625
17
⁄32
.53125
35
⁄64
.546875
9
⁄16
.5625
37
⁄64
.578125
19
⁄32
.59375
39
⁄64
.609375
5
⁄8
.625
41
⁄64
.640625
21
⁄32
.65625
43
⁄64
.671875
11
⁄16
.6875
45
⁄64
.703125
23
⁄32
.71875
47
⁄64
.734375
3
⁄4
.750
49
⁄64
.765625
25
⁄32
.78125
51
⁄64
.796875
13
⁄16
.8125
53
⁄64
.828125
27
⁄32
.84375
55
⁄64
.859375
7
⁄8
.875
57
⁄64
.890625
29
⁄32
.90625
59
⁄64
.921875
15
⁄16
.9375
61
⁄64
.953125
31
⁄32
.96875
63
⁄64
.984375
1
1.000
Millimeters
Altitude
Feet
Meters
- 1000 - 304.8
- 500 - 152.4
0
0.0
+ 500 + 152.4
+ 1000
304.8
1500
457.2
2000
609.6
2500
762.0
3000
914.4
3500
1066.8
4000
1219.2
4500
1371.6
5000
1524.0
5500
1676.4
6000
1828.8
6500
1981.2
7000
2133.6
7500
2286.0
8000
2438.4
8500
2590.8
9000
2743.2
9500
2895.6
10000
3048.0
15000
4572.0
13.097
13.494
13.891
14.288
14.684
15.081
15.487
15.875
16.272
16.669
17.066
17.463
17.859
18.256
18.653
19.050
19.447
19.844
20.241
20.638
21.034
21.431
21.828
22.225
22.622
23.019
23.416
23.813
24.209
24.606
25.003
25.400
Barometer Reading
In. Hg. Mm. Hg.
31.0
788
30.5
775
29.9
760
29.4
747
28.9
734
28.3
719
27.8
706
27.3
694
26.8
681
26.3
668
25.8
655
25.4
645
24.9
633
24.4
620
24.0
610
23.5
597
23.1
587
22.7
577
22.2
564
21.8
554
21.4
544
21.0
533
20.6
523
16.9
429
Atmos. Press.
Boiling Pt.
Psia
Ft. Water of Water ºF
15.2
35.2
213.8
15.0
34.6
212.9
14.7
33.9
212.0
14.4
33.3
211.1
14.2
32.8
210.2
13.9
32.1
209.3
13.7
31.5
208.4
13.4
31.0
207.4
13.2
30.4
206.5
12.9
29.8
205.6
12.7
29.2
204.7
12.4
28.8
203.8
12.2
28.2
202.9
12.0
27.6
201.9
11.8
27.2
201.0
11.5
26.7
200.1
11.3
26.2
199.2
11.1
25.7
198.3
10.9
25.2
197.4
10.7
24.7
196.5
10.5
24.3
195.5
10.3
23.8
194.6
10.1
23.4
193.7
8.3
19.2
184.0
HEAD AND PRESSURE EQUIVALENTS
1. Feet Head of Water and Equivalent Pressures
To change head in feet to pressure in pounds, multiply by .434
Feet
Pounds Feet
Pounds Feet
Pounds
Feet
Pounds
Head per Sq. In. Head per Sq. In. Head per Sq. In. Head per Sq. In.
1
.43
30
12.99
140
60.63
300
129.93
2
.87
40
17.32
150
64.96
325
140.75
3
1.30
50
21.65
160
69.29
350
151.58
4
1.73
60
25.99
170
73.63
400
173.24
5
2.17
70
30.32
180
77.96
500
216.55
6
2.60
80
34.65
190
82.29
600
259.85
7
3.03
90
38.98
200
86.62
700
303.16
8
3.46
100
43.31
225
97.45
800
346.47
9
3.90
110
47.64
250
108.27
900
389.78
10
4.33
120
51.97
275
119.10
1000
433.09
20
8.66
130
56.30
-
2. Pressure and Equivalent Feet Head of Water
To change pounds pressure to feet head, multiply by 2.3
Pounds Feet Pounds
Feet
Pounds
Feet Pounds
per Sq. In. Head per Sq. In. Head per Sq. In. Head per Sq. In.
1
2.31
20
46.18
120
277.07
225
2
4.62
25
57.72
125
288.62
250
3
6.93
30
69.27
130
300.16
275
4
9.24
40
92.36
140
323.25
300
5
11.54
50
115.45
150
346.34
325
6
13.85
60
138.54
160
369.43
350
7
16.16
70
161.63
170
392.52
375
8
18.47
80
184.72
180
415.61
400
9
20.78
90
207.81
190
438.90
500
10
23.09
100
230.90
200
461.78 1000
15
34.63
110
253.98
-
25
Feet
Head
519.51
577.24
643.03
692.69
750.41
808.13
865.89
922.58
1154.48
2309.00
-
Conversion Charts
TECHNICAL DATA
CONVERSION CHARTS
English measures – unless otherwise designated, are those used in
the United States.
Gallon – designates the U.S. gallon. To convert into the Imperial gallon,
multiply the U.S. gallon by 0.83267. Likewise, the word ton designates a short
ton, 2,000 pounds.
Multiply
Acres
Acres
Acres
Acres
Atmospheres
Atmospheres
Atmospheres
Atmospheres
Atmospheres
Atmospheres
Barrels-Oil
Barrels-Beer
Barrels-Whiskey
Barrels/Day-Oil
Bags or sacks-cement
Board feet
B.T.U./min.
B.T.U./min.
B.T.U./min.
B.T.U./min.
Centimeters
Centimeters
Centimeters
Cubic feet
Cubic feet
Cubic feet
Cubic feet
Cubic feet
Cubic feet
Cubic feet
Cubic feet
Cubic feet/min.
Cubic feet/min.
Cubic feet/min.
Cubic feet/min.
Cubic feet/sec.
Cubic feet/sec.
Cubic inches
Cubic inches
Cubic inches
Cubic inches
By
43,560
4047
1.562 x 103
4840
76.0
29.92
33.90
10,332
14.70
1.058
42
31
45
0.02917
94
144 sq. in. x 1 in.
12.96
0.02356
0.01757
17.57
0.3937
0.01
10
2.832 x 104
1728
0.02832
0.03704
7.48052
28.32
59.84
29.92
472.0
0.1247
0.4719
62.43
0.646317
448.831
16.39
5.787 x 10–4
1.639 x 10–5
2.143 x 10–5
Properties of water – it freezes at 32ºF., and is at its maximum density at 39.2ºF.
In the multipliers using the properties of water, calculations are based on water
at 39.2ºF. in a vacuum, weighing 62.427 pounds per cubic foot, or 8.345 pounds
per U.S. gallon.
To Obtain
Square feet
Square meters
Square miles
Square yards
Cms. of mercury
Inches of mercury
Feet of water
Kgs./sq. meter
Lbs./sq. inch
Tons/sq. ft.
Gallons-Oil
Gallons-Beer
Gallons-Whiskey
Gallons/Min-Oil
Pounds-cement
Cubic inches
Foot-lbs./sec.
Horsepower
Kilowatts
Watts
Inches
Meters
Millimeters
Cubic cms.
Cubic inches
Cubic meters
Cubic yards
Gallons
Liters
Pints (liq.)
Quarts (liq.)
Cubic cms./sec.
Gallons/sec.
Liters/sec.
Lbs. of water/min.
Millions gals./day
Gallons/min.
Cubic centimeters
Cubic feet
Cubic meters
Cubic yards
Multiply
Cubic inches
Cubic inches
Cubic inches
Cubic inches
Cubic yards
Cubic yards
Cubic yards
Cubic yards
Cubic yards
Cubic yards
Cubic yards
Cubic yards
Cubic yards/min.
Cubic yards/min.
Cubic yards/min.
Fathoms
Feet
Feet
Feet
Feet
Feet of water
Feet of water
Feet of water
Feet of water
Feet of water
Feet/min.
Feet/min.
Feet/min.
Feet/min.
Feet/min.
Feet/sec.
Feet/sec.
Feet/sec.
Feet/sec.
Feet/sec.
Feet/sec.
Feet/sec./sec.
Feet/sec./sec.
Foot-pounds
Foot-pounds
Foot-pounds
26
By
4.329 x 10–3
1.639 x 10–2
0.03463
0.01732
764,544.86
27
46,656
0.7646
202.0
764.5
1616
807.9
0.45
3.366
12.74
6
30.48
12
0.3048
1/3
0.0295
0.8826
304.8
62.43
0.4335
0.5080
0.01667
0.01829
0.3048
0.01136
30.48
1.097
0.5924
18.29
0.6818
0.01136
30.48
0.3048
1.286 x 103
5.050 x 107
3.240 x 104
To Obtain
Gallons
Liters
Pints (liq.)
Quarts (liq.)
Cubic centimeters
Cubic feet
Cubic inches
Cubic meters
Gallons
Liters
Pints (liq.)
Quarts (liq.)
Cubic feet/sec.
Gallons/sec.
Liters/sec.
Feet
Centimeters
Inches
Meters
Yards
Atmospheres
Inches of mercury
Kgs./sq. meter
Lbs./Sq. ft.
Lbs./sq. inch
Centimeters/sec.
Feet/sec.
Kilometers/hr.
Meters/min.
Miles/hr.
Centimeters/sec.
Kilometers/hr.
Knots
Meters/min.
Miles/hr.
Miles/min.
Cms./sec./sec.
Meters/sec./sec.
British Thermal Units
Horsepower-hrs.
Kilogram-calories
Conversion Charts
TECHNICAL DATA
Multiply
Foot-pounds
Foot-pounds
Gallons
Gallons
Gallons
Gallons
Gallons
Gallons
Gallons
Gallons
Gallons-Imperial
Gallons-U.S.
Gallons water
Gallons/min.
Gallons/min.
Gallons/min.
Gallons/min.
Grains/U.S. gal.
Grains/U.S. gal.
Grains/Imp. gal.
Grams
Grams
Grams
Grams
Grams
Horsepower
Horsepower
Horsepower
Horsepower
Horsepower
Horsepower
Horsepower (boiler)
Horsepower (boiler)
Horsepower-hours
Horsepower-hours
Horsepower-hours
Horsepower-hours
Inches
Inches of mercury
Inches of mercury
Inches of mercury
Inches of mercury
Inches of mercury (32°F)
Inches of water
Inches of water
Inches of water
Inches of water
Inches of water
Inches of water
Kilograms
By
0.1383
3.766 x 107
3785
0.1337
231
3.785 x 10–3
4.951 x 10–3
3.785
8
4
1.20095
0.83267
8.345
2.228 x 10–3
0.06308
8.0208
.2271
17.118
142.86
14.254
15.43
.001
1000
0.03527
2.205 x 10–3
42.44
33,000
550
1.014
0.7457
745.7
33,493
9.809
2546
1.98 x 106
2.737 x 105
0.7457
2.540
0.03342
1.133
345.3
70.73
0.491
0.002458
0.07355
25.40
0.578
5.202
0.03613
2.205
To Obtain
Kilogram-meters
Kilowatt-hours
Cubic centimeters
Cubic feet
Cubic inches
Cubic meters
Cubic yards
Liters
Pints (liq.)
Quarts (liq.)
U.S. gallons
Imperial gallons
Pounds of water
Cubic feet/sec.
Liters/sec.
Cu. ft./hr.
Meters3/hr.
Parts/million
Lbs./million gal.
Parts/million
Grains
Kilograms
Milligrams
Ounces
Pounds
B.T.U./min.
Foot-lbs./min.
Foot-lbs./sec.
Horsepower (metric)
Kilowatts
Watts
B.T.U./hr.
Kilowatts
B.T.U.
Foot-lbs.
Kilogram-meters
Kilowatt-hours
Centimeters
Atmospheres
Feet of water
Kgs./sq. meter
Lbs./sq. ft.
Lbs./sq. inch
Atmospheres
Inches of mercury
Kgs./sq. meter
Ounces/sq. inch
Lbs. sq. foot
Lbs./sq. inch
Lbs.
Multiply
Kilograms
Kilograms
Kiloliters
Kilometers
Kilometers
Kilometers
Kilometers
Kilometers
Kilometers/hr.
Kilometers/hr.
Kilometers/hr.
Kilometers/hr.
Kilometers/hr.
Kilowatts
Kilowatts
Kilowatts
Kilowatts
Kilowatts
Kilowatt-hours
Kilowatt-hours
Kilowatt-hours
Kilowatt-hours
Liters
Liters
Liters
Liters
Liters
Liters
Liters
Liters
Liters/min.
Liters/min.
Lumber Width (in.) x
Thickness (in.)
12
Meters
Meters
Meters
Meters
Meters
Meters
Miles
Miles
Miles
Miles
Miles/hr.
Miles/hr.
Miles/hr.
Miles/hr.
Miles/hr.
27
By
1.102 x 10–3
103
103
105
3281
103
0.6214
1094
27.78
54.68
0.9113
.5399
16.67
56.907
4.425 x 104
737.6
1.341
103
3414.4
2.655 x 106
1.341
3.671 x 105
103
0.03531
61.02
10–3
1.308 x 10–3
0.2642
2.113
1.057
5.886 x 10–4
4.403 x 10–3
To Obtain
Tons (short)
Grams
Liters
Centimeters
Feet
Meters
Miles
Yards
Centimeters/sec.
Feet/min.
Feet/sec.
Knots
Meters/min.
B.T.U./min.
Foot-lbs./min.
Foot-lbs./sec.
Horsepower
Watts
B.T.U.
Foot-lbs.
Horsepower-hrs.
Kilogram-meters
Cubic centimeters
Cubic feet
Cubic inches
Cubic meters
Cubic yards
Gallons
Pints (liq.)
Quarts (liq.)
Cubic ft./sec.
Gals./sec.
Length (ft.)
Board feet
100
3.281
39.37
10–3
103
1.094
1.609 x 105
5280
1.609
1760
44.70
88
1.467
1.609
0.8689
Centimeters
Feet
inches
Kilometers
Millimeters
Yards
Centimeters
Feet
Kilometers
Yards
Centimeters/sec.
Feet/min.
Feet/sec.
Kilometers/hr.
Knots
Conversion Charts
TECHNICAL DATA
Multiply
Miles/hr.
Miles/min.
Miles/min.
Miles/min.
Miles/min.
Ounces
Ounces
Ounces
Ounces
Ounces
Parts/million
Parts/million
Parts/million
Pounds
Pounds
Pounds
Pounds
Pounds
Pounds of water
Pounds of water
Pounds of water
Pounds of water/min.
Pounds/cubic foot
Pounds/cubic foot
Pounds/cubic foot
Pounds/cubic inch
Pounds/cubic inch
Pounds/cubic inch
Pounds/foot
Pounds/inch
Pounds/sq. foot
Pounds/sq. foot
Pounds/sq. foot
Pounds/sq. inch
PSI
PSI
PSI
Quarts (dry)
Quarts (liq.)
Square feet
Square feet
Square feet
Square feet
Square feet
Square feet
1
sq. ft./gal./min.
Square inches
Square inches
Square inches
By
26.82
2682
88
1.609
60
16
437.5
0.0625
28.3495
2.835 x 10–5
0.0584
0.07015
8.345
16
256
7000
0.0005
453.5924
0.01602
27.68
0.1198
2.670 x 10–4
0.01602
16.02
5.787 x 10–4
27.68
2.768 x 104
1728
1.488
1152
0.01602
4.882
6.944 x 10–3
0.06804
2.307
2.036
703.1
67.20
57.75
2.296 x 10–5
929.0
144
0.09290
3.587 x 10–4
1/9
8.0208
6.452
6.944 x 10–3
645.2
To Obtain
Meters/min.
Centimeters/sec.
Feet/sec.
Kilometers/min.
Miles/hr.
Drams
Grains
Pounds
Grams
Tons (metric)
Grains/U.S. gal.
Grains/Imp. gal.
Lbs./million gal.
Ounces
Drams
Grains
Tons (short)
Grams
Cubic feet
Cubic inches
Gallons
Cubic ft./sec.
Grams/cubic cm.
Kgs./cubic meters
Lbs./cubic inch
Grams/cubic cm.
Kgs./cubic meter
Lbs./cubic foot
Kgs./meter
Grams/cm.
Feet of water
Kgs./sq. meter
Pounds/sq. inch
Atmospheres
Feet of water
Inches of mercury
Kgs./sq. meter
Cubic inches
Cubic inches
Acres
Square centimeters
Square inches
Square meters
Square miles
Square yards
Overflow rate
(ft./hr.)
Square centimeters
Square feet
Square millimeters
Multiply
Square kilometers
Square kilometers
Square kilometers
Square kilometers
Square kilometers
Square meters
Square meters
Square meters
Square meters
Square miles
Square miles
Square miles
Square miles
Square yards
Square yards
Square yards
Square yards
Temp (ºC)+273
Temp. (ºC)+17.78
Temp. (ºF)+460
Temp. (ºF)-32
Tons (metric)
Tons (metric)
Tons (short)
Tons (short)
Tons (short)
Tons (short)
Tons (short)
Tons of water/24 hrs.
Tons of water/24 hrs.
Tons of water/24 hrs.
Watts
Watts
Watts
Watts
Watts
Watts
Watt-hours
Watt-hours
Watt-hours
Watt-hours
Watt-hours
Watt-hours
Yards
Yards
Yards
Yards
28
By
247.1
10.76 x 106
106
0.3861
1.196 x 106
2.471 x 10–4
10.76
3.861 x 10–7
1.196
640
27.88 x 106
2.590
3.098 x 106
2.066 x 10–4
9
0.8361
3.228 x 10–7
1
1.8
1
5/9
103
2205
2000
32,000
907.1843
0.89287
0.90718
83.333
0.16643
1.3349
0.05686
44.25
0.7376
1.341 x 10–3
0.01434
10–3
3.414
2655
1.341 x 10–3
0.8604
367.1
10–3
91.44
3
36
0.9144
To Obtain
Acres
Square feet
Square meters
Square miles
Square yards
Acres
Square feet
Square miles
Square yards
Acres
Square feet
Square kilometers
Square yards
Acres
Square feet
Square meters
Square miles
Abs. temp. (ºC)
Temp. (ºF)
Abs. temp. (ºF)
Temp (ºC)
Kilograms
Pounds
Pounds
Ounces
Kilograms
Tons (long)
Tons (metric)
Pounds water/hr.
Gallons/min.
Cu. ft./hr.
B.T.U./min.
Foot-lbs./min.
Foot-lbs./sec.
Horsepower
Kg.-calories/min.
Kilowatts
B.T.U.
Foot-lbs.
Horsepower-hrs.
Kilogram-calories
Kilogram-meters
Kilowatt-hours
Centimeters
Feet
Inches
Meters
Jet Pumps
Typical Installations
TECHNICAL DATA
SHALLOW
WELL SYSTEM
PACKER
DEEP WELL
SYSTEM
TWIN PIPE
DEEP WELL
SYSTEM
2-PIPE
PITLESS
ADAPTER
OVER THE WELL
Typical Goulds Jet Pump Installations
29
AW 42 ADAPTER
4" Submersibles
Typical Installations
TECHNICAL DATA
30
High Capacity
Submersible Pumps
Typical Installations
TECHNICAL DATA
Typical High Capacity Submersible Pump Installations
NOTE: Header pipe must be large
enough to get enough water to all
tanks equally.
31
Centrifugal Booster
Pump Installations
TECHNICAL DATA
AUTOMATIC OPERATION
HOUSE WATER MAIN
UNION
CHECK
VALVE
Use flow control or manual valve on
discharge to throttle pump. Must be
sized, or set, to load motor below
max. nameplate amps.
GATE
BALL
VALVE GAUGE
VALVE
UNION
MAIN POWER BOX
FUSE BOX
OR
SWITCH
TO SIZE TANK
PROPERLY –
MATCH
DRAWDOWN OF
TANK TO CAPACITY
OF PUMP.
UNION
PRESSURE
SWITCH
CHECK
VALVE
*RELIEF
VALVE
MANUAL OPERATION
* NOTE: Required if system pressure can exceed 100 PSI.
HOUSE WATER MAIN
UNION
CHECK
VALVE
Use flow control or manual valve on
discharge to throttle pump. Must be
sized, or set, to load motor below
max. nameplate amps.
GATE
VALVE
PRESSURE
GAUGE
MAIN POWER BOX
BALL
VALVE
UNION
PUMP DISCHARGE
TO SPRINKLERS
UNION
CHECK
VALVE
32
FUSE BOX
OR
SWITCH
Jet Booster
Pump Installations
TECHNICAL DATA
AUTOMATIC OPERATION
JET PUMP - SHALLOW WELL OR CONVERTIBLE WITH INJECTOR
HOUSE WATER MAIN
UNION
Use flow control
or manual valve on
suction to throttle
pump. Must be sized,
or set, to load motor
below max. nameplate
amps.
BALL
VALVE
CHECK
VALVE
GATE
VALVE
GAUGE
UNION
UNION
MAIN POWER BOX
TO SIZE TANK
PROPERLY –
MATCH
DRAWDOWN OF
TANK TO CAPACITY
OF PUMP.
FUSE BOX
OR
SWITCH
CHECK
VALVE
PRESSURE *RELIEF
SWITCH VALVE
* NOTE: Required if system pressure can exceed 100 PSI.
SIZING THE BOOSTER PUMP
Booster system pumps are sized the same as shallow well jet pumps with the exception being, we add the incoming city pressure to
what the pump provides. The required flow is determined by the number of bathrooms or number of fixtures being used at any given
time. City water is supplied under pressure, low incoming pressure is caused by undersized, crushed or severely corroded pipes or
large elevation differences, such as a hill, between the city water line and the house.
Verify the incoming pressure with the water flowing to find the “dynamic suction pressure”, static pressure is what you see with no
water flowing. Use the dynamic suction pressure to calculate pump performance and selection. The J5S and the high pressure version,
J5SH are very popular as booster pumps. The J5SH is a good choice for booster applications because of its narrow flow range and
higher pressure capability. In the absence of performance data for 0’ we use the 5’ Total Suction Lift performance data. Add the
incoming dynamic pressure to the pump’s discharge pressure to find the total discharge pressure. Make a chart showing the flow,
incoming dynamic pressure, pump discharge pressure and total discharge pressure for each job. It would look like this if using a J5SH
pump with 15 PSI of incoming dynamic pressure:
Flow Rate
GPM
11.5
11.3
11
7.7
4.8
0
Pump Discharge
Pressure (PSI)
20
30
40
50
60
83
Incoming Dynamic
Pressure (PSI)
15
15
15
15
15
15
Total Discharge
Pressure (PSI)
35
45
55
65
75
98
33
Pipe Volume and
Velocity
TECHNICAL DATA
STORAGE OF WATER IN VARIOUS SIZE PIPES
Pipe Size
1¼
1½
2
3
4
Volume in
Gallons per Foot
.06
.09
.16
.36
.652
Pipe Size
6
8
10
12
MINIMUM FLOW TO MAINTAIN 2FT./SEC. *SCOURING
VELOCITY IN VARIOUS PIPES
Volume in
Gallons per Foot
1.4
2.6
4.07
5.87
Pipe Size
1¼
1½
2
3
4
Minimum GPM
9
13
21
46
80
Pipe Size
6
8
10
12
Minimum GPM
180
325
500
700
* Failure to maintain or exceed this velocity will result in clogged pipes.
Based on schedule 40 nominal pipe.
STORAGE OF WATER IN VARIOUS SIZES OF WELLS
D2 = Gals. of Storage per Foot
24.5
Where: D = Inside diameter of well casing in inches
Examples:
2" Casing = .16 Gals. per ft. Storage
8" Casing = 2.6 Gals. per ft. Storage
3" Casing = .36 Gals. per ft. Storage
10" Casing = 4.07 Gals. per ft. Storage
4" Casing = .652 Gals. per ft. Storage 12" Casing = 5.87 Gals. per ft. Storage
5" Casing = 1.02 Gals. per ft. Storage 14" Casing = 7.99 Gals. per ft. Storage
6" Casing = 1.4 Gals. per ft. Storage
16" Casing = 10.44 Gals. per ft. Storage
34
Application
TECHNICAL DATA
Jet Pump
Motor Data and
Electrical Components
GOULDS PUMPS AND A.O. SMITH MOTOR DATA
GP Number
J04853
J05853
J06853
J07858
J08854
② J09853
② J04853L
② J05853L
② J06853L
② J07858L
①② J08854L
SFJ04853
SFJ05853
SFJ06853
② SFJ04860
② SFJ05860
② SFJ06860
Where Used
A.O. Smith Number
J05, HB705
C48J2DB11C3HF
JL07N, HSJ07, XSH07, HB
C48K2DB11A4HH
JL10N, HSJ10, SJ10, XSH10, HB
C48L2DB11A4HH
HSJ15, SJ15, HB, XSH15
C48M2DB11A1HH
HSJ20, HSC20, XSH20
K48N2DB11A2HH
XSH30, GT30
C56P2U11A3HH
J5(S), GB
C48A93A06
J7(S), GB, GT07, (H)SJ07, HSC07
C48A94A06
J10(S), GB, GT10, (H)SJ10, HSC10
C48A95A06
J15(S), GB, GT15, HSJ15, HSC15
C48M2DC11A1
HSJ20, GB, GT20, HSC20
K48A34A06
JB05
S48A90A06
JB07
C48A77A06
JB10
C48A78A06
JRS5, JRD5, JB05
C48C04A06
JRS7, JRD7, JB07
C48C05A06
JRS10, JRD10, JB10
C48C06A06
① Effective July, 1998, 230 V only.
HP
½
¾
1
1½
2
3
½
¾
1
1½
2
½
¾
1
½
¾
1
Volts
115/230
115/230
115/230
115/230
115/230
230
115/230
115/230
115/230
115/230
230
115/230
115/230
115/230
115/230
115/230
115/230
Phase
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
Service Factor
1.6
1.5
1.4
1.3
1.2
1.15
1.6
1.5
1.4
1.3
1.2
1.6
1.5
1.4
1.6
1.5
1.4
Max. Load Amps
10.8/5.4
14.8/7.4
16.2/8.1
20.0/10.0
22.6/11.3
17.2
10.8/5.4
14.8/7.4
16.2/8.1
21.4/10.7
12.9
9.4/4.7
13.6/6.8
15.8/7.9
12.6/6.3
14.8/7.4
16.2/8.1
Watts
880
1280
1440
1866
2100
3280
968
1336
1592
1950
2100
900
1160
1400
990
1200
1400
Circuit Breaker
25/15
30/15
30/20
40/20
25/15
30
25/15
30/15
30/20
40/20
25
20/10
25/15
30/20
25/15
30/15
30/20
➁ Current production motor
ELECTRICAL COMPONENTS
Goulds Pumps
A.O. Smith
Motor Model
Motor Model
J04853
C48J2DB11C3HF
J05853
C48K2DB11A4HH
J06853
C48L2DB11A4HH
J07858
C48M2DB11A1HH
J08854
K48N2DB11A2HH
J09853
C56P2U11A3HH
J04853L
C48A93A06
J05853L
C48A94A06
J06853L
C48A95A06
J07858L
C48M2DC11A1HH
J08854L
K48A34A06
SFJ04853
S48A90A06
SFJ05853
C48A77A06
SFJ06853
C48A78A06
SFJ04860
C48C04A06
SFJ05860
C48C05A06
SFJ06860
C48C06A06
4
Motor Overload with Leads
Old Number
③ New Number
T.I. Number
614246 71
MET38ABN
614246 20
CET63ABN
614246 9
CET52ABN
614246 79
CET38ABM
611307 29
BRT44ABM
611106 22
611106 36
BRB2938
614246 98
627121 43
MET39ABN-CL
614246 20
627121 38
CET63ABN
614246 9
627121 7
CET52ABN
614246 153
627121 47
CET36WX
616861 10
627119 10
CET31ABN
621863 1
MEJ38ABN
621863 4
CET55ABN
621863 5
CET49ABN
614246 67
627121 48
MET36ABN
614246 20
627121 38
CET63ABN
614246 9
627121 7
CET52ABN
Run Capacitor
and MFD
614529 4: 25
623450 8: 30
③ These new overload part numbers are for use with the new plastic terminal board with the quick change voltage plug.
4 Use this suffix if your motor has the old style brown terminal board without quick change voltage plug.
⑤ 629002 2 replaces 614234 1, 2, and 6.
35
Start Capacitor
MFD Rating
610807 1: 124/148
610807 2: 161/192
610807 2: 161/192
610807 2: 161/192
610807 1: 124/148
610807 32: 189/227
610807 1:124/148
610807 2:161/192
610807 2:161/192
610807 2:161/192
610807 33: 64-77
N/A
610807 2: 161/192
610807 2: 161/192
610807 2: 161/192
610807 2: 161/192
610807 2: 161/192
Switch⑤
629002 2
629002 2
629002 2
629002 2
629002 2
629002 2
629002 2
629002 2
629002 2
629002 2
629002 2
3945C91A01
3945C91A01
3945C91A01
629002 2
629002 2
629002 2
Application
TECHNICAL DATA
Jet Pump Motor Wiring
A.O. Smith Motors
TERMINAL BOARD AND VOLTAGE CHANGE PLUG
■ Screws with ¼" drive: The
terminal screw accepts either
a ¼" nut driver or a slotted
screw driver.
■ Line Wire Connection: The
space under the screw will
accept #16, #14, #12, #10,
or #8 wire. The rib at the
bottom edge of the screw
allows the wire to be placed
straight into the space under
the screw. This rib retains the
wire under the head of the
screw and for #12, #10, or
#8 wire it is not necessary
to wrap the wire around the
screw.
A change has been made to
use a new terminal board on
the A.O. Smith two compartment motor models. This
terminal board is used on both
dual voltage and single
voltage motors.
FEATURES
■ Voltage Plug: Dual voltage
motors use a voltage plug
that retains the terminals for
the Black and Black Tracer
leads. To change voltage, lift
the black plug and align the
arrow with the desired voltage
on terminal board. See Figure
1 for an example of the dual
voltage connection diagram.
■ ½ HP wired 115 V, ¾ HP
and up wired 230 V at factory.
■ Quick Connect Terminals:
Each terminal has provision for
¼" quick connect terminals in
addition to the screw.
■ Molded Plastic Material:
The terminal board is made
from an extremely tough white
plastic material with L1, L2,
and A markings molded into
the board.
■ Lead Channel: A channel
adjacent to the conduit hole
directs wiring to the top of
the board.
■ Governor Guard: An integral backplate prevents leads
from entering the area around
the governor.
■ Ground Guard: To prevent
the bare ground wire from
touching the “live” L2 terminal, the ground wire must be
placed above this guard.
VOLTAGE CHANGES ARE MADE INSIDE THE MOTOR COVER
NOT IN THE PRESSURE SWITCH.
WARNING:
DISCONNECT POWER SOURCE BEFORE CHECKING. DO NOT MAKE ANY CHANGES WITH POWER ON.
CAPACITOR START INDUCTION RUN – SINGLE SPEED
(NEW STYLE – AFTER APRIL, 1999)
CAPACITOR START INDUCTION RUN – SINGLE SPEED
(OLD STYLE – UP TO APRIL, 1999)
FIGURE 1
115 V 230 V
A
L2
YELLOW
RED
BLACK
PURPLE
2
1 3
BLACK
TRACER
B
A
L2
L1
MAIN
L1
RED
PHASE
MAIN
YELLOW
WHITE
LINE
GRD
Green (Ground)
“Black Tracer” is a black and white wire
Align black plug to 115 V or 230 V arrow.
½ HP wired 115 V, ¾ HP and up wired
230 V at factory.
36
L2
BLACK
TRACER
230 V
L1
L2
B
BLACK
115 V
A
L1
TO WIRE FOR 230 V:
BLACK TRACER TO B
BLACK TO A
TO WIRE FOR 115 V:
BLACK TRACER TO A
BLACK TO L1
Emerson Motor
Wiring
115/230 VOLTAGE CONNECTIONS
115 Voltage
230 Voltage
Black — A
Wht./Blk. Tracer — 1
Line 1 — 2
Line 2 — A
(Blue — 3)
Black — 1
Wht./Blk. Tracer — B
Line 1 — 2
Line 2 — A
(Blue — 3)
TO CHANGE MOTOR VOLTAGE:
Models without a Switch
115V to 230V
230V to 115V
Move Wht./Blk. tracer to B
Move Blk. to A
Move Blk. to 1
Move Wht./Blk. tracer to 1
Models with Voltage Change Switch
• Move toggle switch between 115V or 230V.
CONNECTIONS
115 VOLTAGE
A – has 2 male connectors and
1 screw connector
2 – has 2 male connectors and
1 screw connector
B – is a dummy terminal used to hold
the Wht./Blk. Tracer for 230V
wiring
230 VOLTAGE
LINE 1
LINE 1
2
2
WHT/BLK
TRACER
3
BLACK
3
1
1
B
B
LINE 2
BLACK
A
Motor is non-reversible CCW rotation shaft end.
Supply connections, use wires sized on the basis of 60ºC ampacity and rated minimum 90ºC.
37
WHT/BLK
TRACER
LINE 2
A
Pressure Switch
Wiring and
Adjustments
SQUARE "D" SWITCHES
ADJUSTMENT
Adjust in proper sequence:
1. CUT-IN: Turn nut down for higher cut-in pressure, or
up for lower cut-in.
Differential: adjust
for cut-out point
2. CUT-OUT: Turn nut down for higher cut-out pressure,
or up for lower cut-out.
Line
L1
CAUTION: TO AVOID DAMAGE, DO NOT EXCEED THE
MAXIMUM ALLOWABLE SYSTEM PRESSURE.
CHECK SWITCH OPERATION AFTER RESETTING.
Load
Grounding
Provisions
#8-32 screws
Load
Line
L2
Range: adjust
for cut-in point
FURNAS PRO CONTROL
MAIN SPRING ADJUSTMENT
Turn clockwise to increase both cut-out
and cut-in pressure. (2 PSI/turn)
LINE LOAD LOAD LINE
L1
MOTOR
L2
38
DIFFERENTIAL
ADJUSTMENT
Turn clockwise to increase
cut-out pressure without
affecting cut-in. (3 PSI/turn)
Wiring Diagrams
AWA501 / AWA502
FACTORY WIRED FOR 230 VAC.
FOR 115 VAC POWER SUPPLY,
WIRE HOT LEG TO (L1) AND
NEUTRAL TO (L2), JUMP
(L2) TO (N).
S1
1
PUMP NO. 1
1T
2
3 HP MAX
S2
1
L1
230 VAC
PUMP NO. 2
2T
SINGLE PHASE
60 HZ
2
L2
N
GND
1
R1
2
LEAD PUMP ON/OFF
R1
A
TD
RUN
S1–AUX
HAND
S2–AUX
OFF
A
5
AUTO
6
TO CHEMICAL
FEED PUMP
S2
RUN
R1
3
4
LAG PUMP ON/OFF
A
HAND
OFF
AUTO
39
S2
Wiring Diagrams
Power / Pump
Connections:
AWA501 / AWA502
POWER CONNECTION AWA501 115 VOLT
POWER CONNECTION 230 VOLT
AWA501, AWA502
L1
L1
L2
N
1
2
1
1T
L2
N
2
FACTORY WIRED FOR 230 VAC.
FOR 115 VAC POWER SUPPLY,
WIRE HOT LEG TO (L1) AND
NEUTRAL TO (L2), JUMP
(L2) TO (N).
2T
FIELD-INSTALLED
JUMPER
PUMP
NO. 2
PUMP
NO. 1
INCOMING
SINGLE PHASE
POWER
115 VAC ONLY
INCOMING
SINGLE PHASE
POWER
230 VAC ONLY
FIELD CONNECTIONS: AWA501, AWA502
S1-AUX
OPTIONAL FRANKLIN CONTROL BOX AND
PUMPTEC WITH AWA501 AND AWA502 ONLY
1
2
1
S2-AUX
1
2
1T
2T
PUMP
TECH
PUMP
TECH
2
LEAD PUMP
START/STOP
PRESSURE SWITCH
CONTROL BOX
3
4
5
LAG PUMP
START/STOP
PRESSURE SWITCH
(OPTIONAL)
SEPARATE
115 VAC
SUPPLY
CONTROL BOX
CHEMICAL FEED PUMP (OPTIONAL)
PUMP
NO. 1
PUMP
NO. 2
40
6
Low Yield Well
Components
COMPONENTS FOR A LOW YIELD WELL WITH A BOOSTER SYSTEM
• Submersible or jet pump to fill atmospheric tank
• Storage tank - usually at least a 500 gallon size
• Magnetic contactor - makes wiring simple and fast
• Normally closed float switch for automatic operation
• Booster pump - sub or jet to pressurize water from storage tank
• Pressure tank sized for 1 minute minimum pump cycle
• Pressure switch
• Check valve and gate valve between the open storage tank and jet pump,
or a gate valve between the submersible and pressure tank
IF A 2 WIRE PUMP IS USED
DELETE THE CONTROL BOX
PUMP
CONTROL
BOX
MOTOR
MINDER
OR
PUMPTEC
INCOMING POWER
SUPPLY
MAGNETIC
CONTACTOR
STORAGE TANK
NORMALLY
CLOSED
SWITCH
WELL
PUMP
STORAGE TANK
P
PUM
PRESSURE
TANK
GATE
VALVE
JET PUMP
CHECK
VALVE
41
PRESSURE
TANK
Goulds Pumps is a brand of ITT Water Technology, Inc. –
a subsidiary of ITT Industries, Inc.
Goulds Pumps and the ITT Engineered Blocks Symbol are
registered trademarks and tradenames of ITT Industries.