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AD-AQ91 052 COAST GUARD RESEARCH AND DEAELOPMENT CENTER GROTON CT F/6 13/11HAZARDOUS CHEMICAL PUMP TESTS.IU)JUL 80 S J ROSENBERG, R F CHRISTENSEN
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2 1Report Documentation Patt.R s2. G4.0.nitt Accession No. R tecs.ent'i Catsog N.
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6 AZARDOUS CHEMICAL PUMP TESTS* , 98.
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United States Coast GuardResearch and Development Center )I Contr,,t oGr,,..
Avery PointGroton. Connecticut 06340 .!.±. I .%.w P ...., .,,, d
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Department of Transportation /iUnited States Coast GuardOffice of Research and Development Pd. So--,o,.l Ag.ny CC.d.
Washinaton. DC 20593 '_
Three hydraulically powered submersible centrifugal pumps, the Framo TK-4, FramoTK-5 and Thune Eureka 150, were tested to document their performance in pumping
viscous liquids. The tests were performed using an ADAPTS 40 HP prime mover ora NAVSEA 80 HP prime mover under controlled viscosity (temperature) and dischargepressure to simulate the various hazardous chemicals and long discharge linesexpected during the offloading of stricken vessels. All three pumps performedadequately under the test conditions. In particular, the Framo TK-5 can providea greater discharqe flow rate than the Framo TK-4 under the same test conditions.The Framo TK-5 performed well with the ADAPTS prime mover. Both the Framo TK-5and the Thune. Eureka 150 pumps performed well with the NAVSEA prime mover. TheNAVSEA prime mover has the capability to operate two Framo TK-5 pumps simultaneously.The results will be used to help in preparing procurement specifications for a CoastGuard hazardous chemical pumping system.
OC 131980
AHAZARDOUS CHEMICAL DISCHARGE AMEIOATON
HAZADOU CHMICL DSCHRGEAMELIORATION, Document is available to the U.S. publicPUMPING EQUIPMENT, VISCOUS FLOW, TRANSFER, through the National Technical InformatiTESTS, HYDRAULIC EQUIPMENT, HAZARDOUS Service, Springfield, Virginia 22161CHEMICAL OFFLOADING EQUIPMENT
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UNCLASSIFIED UNCLASSIFIEDForm DOT P 1700.7 (8?2 Reproduction mf form and completed page is authorized
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TABLE OF CONTENTS
*PAGE
1.0 BACKGROUND1
*2.0 OBJECTIVE 2
3.0 EQUIPMENT AND SYSTEM DESCRIPTION 3
3.1 The Hydraulic System Di 33.2 The Pumping System 3
4.0 RESULTS t5
4.1 Pump Characteristics 54.1.1 Pump Head tL54.1.2 Pump Flow Rate 7T .5
4.1.3 Pump Speed 64.1.4 Pump Characteristic Curves 6
4.2 Hydraulic Prime Movers 7
5.0 DISCUSSION 19
5.1 Pump Performance 195.2 Pumping System Performance 215.3 Physical Characteristics of the Pumps and Prime Movers 22
6.0 CONCLUSIONS 26
REFERENCES 27
APPENDIX A - FUEL OIL VISCOSITIES A-iAPPENDIX B - RAW TEST DATA B-iAPPENDIX C - CORRUGATED HOSE FLOW CHARACTERISTICS C-i
LIST OF TABLES
TABLE PAGE
1 Scheduled Pump Tests 22 Hydraulic Prime Mover Limitations 8
LIST OF ILLUSTRATIONS
FIGURE PAGE
1 Diagram of Test System 42 Framo TK-4 Pump Performance Curve Using the ADAPTS 40HP
Prime Mover and Fresh Water 93 Framo TK-4 Pump Performance Curve Using the ADAPTS 40HP
Prime Mover and #4 Fuel Oil 10
FIGURE LIST OF ILLUSTRATIONS (continued) PAGE
4 Framo TK-4 Pump Performance Curve Using the NAVSEA 80HPPrime Mover and Fresh Water 11
5 Framo TK-5 Pump Performance Curve Using the ADAPTS 40HPPrime Mover and Fresh Water 12
6 Framo TK-5 Pump Performance Curve Using the ADAPTS 40HPPrime Mover and #4 Fuel Oil 13
7 Framo TK-5 Pump Performance Curve Using the NAVSEA 80HPPrime Mover and Fresh Water 14
8 Framo TK-5 Pump Performance Curve Using the NAVSEA 80HPPrime Mover and #4 Fuel Oil 15
9 Eureka 150 Pump Performance Curve Using the ADAPTS 40HPPrime Mover and Fresh Water 16
10 Eureka 150 Pump Performance Curve Using the ADAPTS 40HPPrime Mover and #4 Fuel Oil 17
11 Eureka 150 Pump Performance Curve Using the NAVSEA 80HPPrime Mover and #4 Fuel Oil 18
12 Comparison of Pump Characteristic Curves Manufacturer andTest Results With the Framo TK-5 Prime Mover and Fresh Water 20
13 Comparison of Pump Characteristic Curves Manufacturer andTest Results With the Eureka 150 Prime Mover and Fresh Water 20
14 Comparison of Potential Operating Points Using ADAPTS 40HPPrime Mover and Fresh Water 23
15 Comparison of Potential Operating Points Using ADAPTS 40HPPrime Mover and #4 Fuel Oil 24
16 Comparison of Potential Operating Points Using NAVSEA 80HPPrime Mover and #4 Fuel Oil 25
GLOSSARY OF SYMBOLS
Symbol Meaning Units
Ht Total pump head ftH2O, PsiP Pressure psiVr Specific weight lbs/ft3
V Velocity ft/secZ Height ftg Gravitational constant 32.2 ft/sec2
Q Volume flow rate gal/mint Time mlnN Speed rev/minM Mass flow rate lb/secT Torque Ibi-ft0 Displacement inA Area in2
Subscripts
Hyd HydraulicI Inletd Dischargew Pumped fluid
iv
ACKNOWLEDGEMENT
The authors gratefully acknowledge the technical and management assistanceprovided by Mr. 0. L. Motherway and Dr. L. H. Chen of the Ocean EngineeringBranch, U.S. Coast Guard Research and Development Center. The U.S. CoastGuard Strike Teams and Mr. M. Jones of NCSC, are also gratefully acknowledgedfor their assistance in the data acquisition phase of this project.
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1.0 BACKGROUND
The Hazardous Chemical Discharge Prevention and Reduction Project is oneof six projects in the Coast Guards program area of Hazardous ChemicalDischarge Amelioration which has the ultimate objective of developingequipment and methods for responding to discharges of hazardous chemicals intothe waters of the U.S.
Specifically, this project is tasked with the investigation anddevelopment of equipment and methods to prevent hazardous chemical dischargefrom an endangered marine vessel and to stop or reduce the discharge from amarine transport container which is already leaking. It is intended that theend user of the hardware developed will be Coast Guard pollution responsepersonnel.
One of the project objectives is the development of a light-weighthazardous chemical off-loading system. In conjunction with this objective,tests were conducted on commercially available submersible centrifugal pumpsto document their performance and as an aid in developing a procurementspecification for a hazardous chemical pumping system.
This report documents the results of the testing program.
}1
2.0 OBJECTIVE
The objective of this program was to document the performance of theFramo TK-4, and TK-5 pumps as well as the Thune-Eureka 150 pump in pumpingliquids of various viscosities with the ADAPTS (Air Deployable Anti-PollutionTransfer System) and NAVSEA (Naval Sea Systems Command) prime mover. TheThune-Eureka 150 pump and the NAVSEA prime mover constitutes the U.S. CoastGuard viscous oil pumping system (VOPS). Extra emphasis was placed on thecomparison of the Framo TK-4 and TK-5 operating off an ADAPTS prime mover.The data generated for the Framo pumps will be used to help in preparingprocurement specifications. The scheduled pump tests are indicated in Table 1.
Water and #4 fuel oil were used as "simulants" for hazardous chemicals.Water was used to provide a test fluid with a viscosity of I centistoke (cS)while the #4 fuel oil provided a test fluid with a viscosity of 110-120 cS*.
Table 1Scheduled Pump Tests
Framo TK-4 Framo TK-5 Thune-Eureka 150ADAPTS NAVSEA ADAPTS NAVSEA ADAPTS NAVSEA
Fluid Pumped 40 HP 80 HP 40 HP 80 HP 40 HP 80 HP
Fresh Water X X X X#4 Fuel 0il(110-120 cS) X X X X
* A viscosity of 110-120 cS was chosen as an upper limit for these tests asit encompasses more than 75% of the CHRIS liquid chemicals shipped in bulk.
2
3.0 EQUIPMENT AND SYSTEM DESCRIPTION
The pump tests were conducted by R&D Center and Strike Team personnelduring the period of 7-18 January 1980 at the Naval Coastal Systems Center(NCSC), Panama City, Florida. As a result of previous work, NCSC has anon-propelled yard oiler, YON-284, with storage tank heating and coolingcapabilities (300F to 1100F). This enables the viscosity of the fluid tobe regulated (See Appendix A). The test system contains two subsystems, thehydraulic system and the pump system, which are connected by a commnon shaft atthe pump.
3.1 The Hydraulic System
The hydraulic system consists of two major components; the hydraulicprime mover and the hydraulic motor driving the pump. These two componentsare connected by two (2) one-inch hydraulic hoses, one supply and one return.The hydraulic supply and return pressures were monitored at the pump motor forthe oil tests and at the prime mover for the water tests, The flow wasmeasured by a dynamic flow meter in the return line to the prime mover. Thehydraulic system arrangement is shown in Figure 1.
3.2 The Pumping System
The pumping system consisted of the pump and a manifold constructedto direct the flow of the pumped fluid. The manifold used for the TK-5, andVOPS pumps was made of six-inch steel piping. The discharge head pressureswere regulated by the use of a six-inch gate valve. The TK-4 pump used afour-inch steel manifold with a four-inch gate valve. The pump dischargepressure was sensed at the discharge of the pump and read remotely. The tanklevel was obtained using a flotation gauge except when pumping #6 fuel oilwhere it was measured by sounding the tank. The arrangement of the pumpingsystem is shown in Figure 1.
I3
-
DIAGRAM OF TEST SYSTEM
HYDRAULIC PRIME MOYER
HYD. PUMP
HYDRAULIC SUPPLY HOSE
(1,*,500 pal max)
PREURE///
4
4.0 RESULTS
4.1 Pump Characteristics
Pump performance characteristics are generally shown as a plot ofthe pump head versus the pump flow rate at a constant speed. The raw testdata (Appendix B) was corrected for various constant speeds and used tocalculate the pump head and the pump flow rate. The raw data was reduced inthe following manner.
4.1.1 Pump Head
The total pump head (HT) is a measure of the energyimparted to the fluid being pumped. By applying Bernoullis' Theorem, thetotal pump head is found to be the following:
HT= Pd- Pi + Vd2 -Vi2 + Zd -Zi
This relationship may be simplified by making the following assumptions:
1. The fluid specific weight (,f) is constant through the pump.Yd= X
2. The difference in height (Z) between the inlet anddischarge of the pump is negligible. Zd - Zi= 0
3. The effect of increased velocity is much less than that ofincreased pressure through the pump.
Vd 2 _i << d - P'i
4. The change in pressure (Pd - Pi) across the pump isequal to the discharge pressure of the pump.
These assumptions reduce the equation for the total pump head to the following:
HT = P
For simplicity, the pump head will be plotted in pounds per square inch (psi).
4.1.2 Pump Flow Rate
The pump flow rate (Qw) of the pump was derived from themeasured quantity of water pumped over a measured period of time (t). Thedimensions of the tank are such that a liquid level change of one inch isequal to 318 gallons. The following relationship exists:
Qw 318 (inches pumped)
5
4.1.3 Pump Speed
The pump performance is plotted at a constant pump speed;however, the pump tests were not conducted at a constant pump speed. Thismeans that the raw test data must be corrected to the desired pump speed.This was done by applying the following ritionships from the HydraulicInstitute Standardsk.U
Pump Capacity QW2 = N2 QW,
Pump Head Hp2 = N2 2 Hpj
where, N1 = the test pump speedN2 = the desired pump speedQW1 = the test pump flow rateQW2 = the corrected pump flow rateHp1 = the test pump headHP2 = the corrected pump head
During the pump tests, the pump speed was not monitoredbut the hydraulic flow rate was. The hydraulic flow rate is the product ofthe pump speed and the pump displacement. The pump displacement for eachrespective pump was constant throughout the pump test. From this, it can bededuced that the ratio of the rated pump speed (N2 ) to the test pump speed(N1) is equivalent to the ratio of the rated hydraulic flow rate (QHyO2)to the test hydraulic flow rate (QHYD1), or,
N2 = QHYD2
By substitution of the hydraulic flow rate ratio for the pump speed ratio, theraw test data may be corrected for speed by applying the following:
Pump Capacity QW2 = QHYD2 QW1
Pump Head Hp2 = QHYD2 2 Hp1
The pump performance is plotted for various constant speeds. These speedswere chosen to coincide with the speeds used by the manufacturer, andhydraulic flow limitations of the hydraulic prime movers.
4.1.4 Pump Characteristic Curves
Figures 2 through 11, are the resulting pumpcharacteristic curves for the pumps tested*. The pump, hydraulic prime mover,
* Figures 2 and 3 were generated from previous Framo TK-4 pump test data.( 2)
6
and fluid pumped are indicated in the upper right corner of the figure foreach test. The constant pump speed is indicated on each characteristiccurve. The data used for determining the pump characteristic curves appearsbelow each respective figure. It should be noted that the resulting pumpcharacteristic curves are independent of the prime mover used. The dashedline in each of the figures indicates the maximum pump performance as limitedby one specific hydraulic prime mover used in the test. This will bediscussed further in the next section.
4.2 Hydraulic Prime Mover
The capabilities of the hydraulic prime mover may limit the pumpperformance. The hydraulic prime mover limits the power, hydraulic flow rate,and hydraulic pressure available to the pump motor. Table 2 indicates thelimits imposed by the prime movers used during these tests. The maximum pumpspeed, that can be obtained with a given prime mover, is determined by thedisplacement of each respective pump motor and the hydraulic flow provided(see section 4.1.3). The maximum rated speed for each respective pump withthe prime movers used during these tests is indicated in table 2.
In order to bring the pump up to the rated speed, the pump motormust be capable of supplying more torque than is required by the pumpimpeller. If the pump motor is assumed to be 100% efficient in transmittingpower, the following relationship is found to exist.
where Q = hydraulic flow - gpm&= pressure change across pump motor -psi
N = pump speed - rpmT - torque - ft lbs
7= 3.1416
By substituting the product of pump speed and pump displacement forthe hydraulic flow rate (Q=NO) in the above relationship, it is found that thetorque is directly proportional to the displacement and pressure drop acrossthe pump motor. From this it should be recognized that the pressure, orpower, available can further limit the maximum speed that the pump mayobtain. This limitation on the pump speed can not be directly determinedbecause of the efficiencies encountered when transmitting the power from theprime mover to the work done by the pump. It was not within the scope of thistest to evaluate the hydraulic prime mover and its efficiency of powertransmission.
A dashed line estimating the maximum pump operation, as limited bythe hydraulic prime mover, is indicated on figures 2 through 11. In all thepump tests, the prime mover was operated at its maximum capacity except wherelimited by the pump design. The only test where the prime mover operation waslimited by the pump design occurred in the Framo TK-4, NAVSEA 80 HP test. Inall other tests, the pump operation was limited by the maximum power,hydraulic flow rate or hydraulic pressure available from the hydraulic primemover.
Table 2Hydraulic Prime Mover Limitations
ADAPTS 40 NAVSEA 80Maximum hydraulic flow (gpm) 29.2 52Maximum hydraulic pressure (psi) 2200 2500Maximum power (hp) 40 87
Maium rated pump speed (rpm)FRAI4O TK-4 (Vickers 25M42A) 2360 3200*FRAMO TK-4 (Vickers 25M55A) 1918 3415FRAI4O TK-5 3946 4750*EUREKA 150 1555 2770
* Maximum design Pump Speed specified by manufacturer
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*: 0 wx Hp-. to,,. HI:,... Hp- ,:.r,, p. i ,pi, i . I 1 p:. i p!:r pi I , : h :
*.:. : ' ..0 . O . 4Z'. 3 10. .¢0.1 14.5 5 ;. 4 1. 440 1 . 0 15.0 245. " . -"5.7 . :44.4 4- 1: I4.S . 2 IF" .C Z 14.b0 j
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- 174.0 ":0. 0 165.3 427.1 i ., ** -I ?*" ' I .O 40.,;) 142 .7 3 . - 17.1 .. 4S.4 1 .5.7 2":':,::2;.,0 1 .0 50.0 .9, 5 ., i!, %-6,3 1 , 7E."~ i59 :.: 0 .0. L.0 4::.0 'O.O 40.. 43.5 4 .2 . 57.3 5.4 5. , 11.
FFAMO TK 4 WITH VIr:I'EF' 2M42A-1C120 HDPFA'ULI. MTORDATA F P I' F'FEVIOUS FFAIhO Tl; 4 PLIIIP TEST
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FIGURE 6
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FLOWI RATE ro l )
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FIGURE 7
TE'T .500 kFm1 S'C160 IFrl MQ FF1 41'-O PF.
--- -dx 18,2. 26.0 26 , .7
Vh, d 01., Hp QOwx Hpx: Q,, Hr:. H .' ,. -p
k7 1.' C; o p-1 i .pto pi I *p. r. i pr,l psi Phl ps i
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6 Z;. . 40. 0 523.3 M.3 630.8 41.1 7.4 '55 :' 4o.10 4i-;.a 0 .0 374.8 32.3 451.a 47.0 C, S 61..9 601.7 S3.4
4., 37.3 a.3.5 343.7 Z41.7 5 .1. : ' 98..4 70.4 45. 1.
SHUT OFF hEAD 97psi
'JJAI 14
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1-0 PR I ME HVc)V1R-;R GOI-IF
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60- 1 0
O- Ea~. +-'., 0. 000650
.-0. r0 ,To
FLC'14 RATE kI I I I , " I'
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FIGURE 8
TEST 2500 RPM 3000 RPM .50o RPM 4C,:Fe FFH- - -, O.h, , 1. 5 Ohyd 22 ? Ghv,: 26.0 l ,d) Z 9.
'.d c., Hp Q.: Hpx Owx Hpx C wx Hp, Ixx Hp,-
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i't. 5 4 .. 40.0 44S.4 32.6 540.5 47.3 g':z .2 C4.3 719.9 e4.0
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,.' 0 .0 2.1.. 9 Z38.8 289. 0 56. 4 337.0 71. 7 34.9 100.0
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3.0 PUMP TESTED: EIIREA 150'°°1 140": .. I.'I II".,/EIR : ,D.-PTS 40HP
-,3 - ' FLUID PUIIIPED; FRESH HATER
1~00
2300
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, 60
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oo 3*0 'oo ;/er
FIGURE 9
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C',,'d Ow Hp 0WX HpN Owx Hpx o.: Hpx ow,: Np.
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FuL.&A 1
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PUSP TE3TED: EUFEiA 15too PRI"E [,lOVER. r-_PT-, 4oHP
-3oo 'FLUID PUMPED: -4 FUEL OIL80-- 12 0
-1'10
00
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FLC'H RATE -j--p r
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FIGURE 10
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Ot..' d 00., Hp 0w Hp> o Hp'X Qwx H!, O x H p*1g o gl:.* p$i gprn pS 1 gpM psi ,j;p. p: i ,;pti. psi
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SHUT OFF HEAD 35psi
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o 01,00 300 r 3~
FIGURE 11
TEST 1:0 RPM. 2200 PPM 2.0Cl RPM 3clo RPM-- - 3 * hkdx 4 1. 3 01Ivwdx 48'. 83 CNht~. S6.3
C~~ Q' Hp qe.w x Hp5, Qwx Hp Hpx ok'. Hp,';F.~ i5 i ;" i psi g i:ol J's1
47. 0 1407.~ 1 0. 0 10 12,. 0 13. 5 12 3 65 123.12 146 1.0 323 1 M5.~ C% C47. 0 1 152. 8 40.0 a al..0 120.7 10 12. 9 30. 9 1 1 '?6-9 43. 1 1 '*8,0. S 5 7.4
41i. 5 1390.4 530 .0 E47. 2 26.4 .90.8 3?.4 934.4 55.1 1078. 1 7:3.S
* 44.0 6%75 .8 050 .0 5 19. 1 35. 4 6.14.3 52.9 74?. 5 7:3.1 8 364.7
$I(UT OFF HEAD 70psi
* TSAGRI~J~IJJ~18ft- PAGI C~'S ~i ~ ~ --
5.0 DISCUSSION
5.1 Pump Performance
Most of the pump characteristic curves display the normal operatingcharacteristics of a centrifugal pump. In almost all instances, theperformance of the pump tested was less than the pump manufacturer hadspecified. The pump characteristic curves in Figures 12 and 13 show thecomparison between the manufacturer's specifications and the test results.The difference in the pump characteristic curves could be due to any of thefollowing reasons:
1. The limitations on the volume of fluid available to pump for acontinuous test caused tight time limitations for each test. Thetime limitations did not allow the whole system to completely reachsteady state operation prior to the monitoring at each test point.This error is not expected to be greater than 5% for any parametermonitored.
2. The accuracy of the parameter monitoring instruments used and theaccuracy of the person reading the instrument would constitute someerror. The worst expected error from the instrument readings is asfollows:
Instrument Worst Expected Errorpressure gauges + zzhydraulic flow meter ; 1 gpmtank level (float meter) T I in. *temperature T 1OF
The combined effect of these possible errors account for themajority of the differences between the manufacturer and the testresults. The method used in correcting the raw data to a constantpump speed causes an amplification of the error. The greater thedifference between the test speed and the pump speed desired, thelarger the effect of the error.
•The tank level error represents about 25 gpm error in the flow rate of thefluid pumped.
19
COMPARISON OF PUMP CHARACTERISTIC CURVESMANUFACTURER AND TEST RESULTS
1AANPFACTUR'ER
PUMP: FRAMO TK-5 9. AbAPTS 40NP ........FLUID PUMPED: WATER NAVSE 800IPPUMP SPEED: 3000 RPM
50- "j
FIGURE 12
MAfANOFACrURER'S ~ACAPTS IH-
PUMP: EUREKA 150 A P.FLUI.-PUMPED: WATERPUMP SPEED: 2600 RPM
5/o0 7060 5 0
FIGURE 13
20
3. The assumptions made in the calculation of the parameters used to* evaluate the pump performance are valid within the accuracy of the
monitoring instruments. A correction for the static pressure lossin the pressure sensing lines was not included in the calculations.
* It was felt that this would yield conservative results from thetest. (Actual pressure did not exceed the recorded gauge pressureplus 3 psi.) This amount was relatively constant throughout thetesting and therefore does not affect the comparison of the pumpresults. It is believed that this error is not significant withinthe scope of the pump tests.
5.2 Pumping System Performance
When evaluating the performance of a pump, it is necessary toconsider the intended use of the pump as well as the operational limitationsimposed on the pump. This imediately imposes a restriction on the area ofthe pump performance curve which is applicable for consideration.
Besides the limitations the hydraulic prime mover places on the pumpperformance (section 4.2), the operation point of the pump is determined bythe restrictions of the pumping system, namely head loss. The system headloss consists of two major components, the static head loss and the dynamichead loss. The static head loss is the pressure loss due to the distance thepump must move the fluid vertically. For example, if the fluid is movedvertically 12 feet, there would be a static head loss of about 5 psi. Thedynamic head loss is due to the frictional forces as the fluid flows along thepipe (or hose). The previous Framo TK-4 pump test determined the expecteddynamic head losses for 100 feet of 4-inch corrugated stainless ste~ 1 hose(corrugation pitch = 0.231 in) by using the fluid expansion theory.~ 3) Forsimplicity, the previous test did not account for the losses due to thefittings and bends, both of which would increase the flow losses.
The summnation of the losses allows a curve to be constructed whichwould be representative of the expected system head loss. This curve iscalled the system characteristic curve. The point where the pump performancecurve intersects the intended system characteristic curve would be theoperating point of the pump in the given system.
Figures 14 through 16 allow a comparison of expected operatingpoints for various pumps. The pump performance curves used in this comparisonare from the test results which include the performance limitations imposed bythe hydraulic prime mover. The prime mover and fluid being pumped is indi-cated above the figure and each respective pump performance curve is labeled.
* - The system characteristic curve used for the comparison results from a testset-up consisting of a 12-foot vertical rise and 100 feet of 4-inch corrugatedstainless steel discharge hose (see appendix C-i for derivation of systemequation). This was considered to be a minimal system; bends, increaseddischarge hose, and fittings would increase the rate at which the head loss isincreasing. This would in turn move the operating point to a higher pumpdischarge pressure and lower flow rate.
21
It can be seen from figure 14 and figure 15 that with the ADAPTS 40HP prime mover, pumping either fresh water or number 4 fuel oil (110-120cS),the Framo 1K-5 provides about twice the discharge flow as can be provided bythe Framo fl-4. This implies that the potential pumping time can be cut inhalf under the specified conditions by using the TK-5 as opposed to the TK-4.
Comparing figure 15 and figure 16 it can be seen that with a singleFramo TX-5 there is little advantage in using the larger NAVSEA prime mover.However, the tests Indicated that the larger prime mover has the capacity toprovide sufficient hydraulic flow to operate two Framo TK-5 pumps inparallel. This would not only double the pumping flow rate but also, 1)increase the system reliability, and 2) allow simultaneous offloading of twocargo holds so as to minimize the listing of the stricken vessel. Of course,these advantages could also be accomplished by having two ADAPTS prime moverson scene, which would further increase the overall reliability.
5.3 Physical Characteristics of the Pumps and Prime Movers
The Framo T1-4 and TK-5 pumps are all stainless steel pumps. Theseal materials are Teflon in the TK-4 and TK-5. The combination of thesematerials of construction make the Framo pumps an excellent choice for ahazardous chemical offloading pump. The Eureka 150 pump is ofnickel-aluminum-bronze construction and uses Teflon and Viton seals in areasexposed to the cargo. It can also be made in stainless steel to provide thenecessary chemical resistance to hazardous chemicals.
The weights of these pumps as tested are:
Framo TK-4 175 lbs.Framo TK-5 177 lbs.Eureka 150 287 lbs.
The Framo pumps were all easily handled by two men while the Eureka 150required four men due to handle positioning and weight.
The ADAPTS prime mover consists of two components, the prime moverand the fuel module. The prime mover weighs 1150 lbs. and measures 44" x 34"x 41". The fuel module measures 23-1/2" in diameter and 34-1/2" in lengthwhen filled. Its filled weight is 440 lbs. giving a total system weight of1590 lbs. The ADAPTS prime mover has a protective enclosure, a definiteadvantage considering its intended delivery mode.
The NAVSEA prime mover, which does not have an enclosure like theADAPTS, is a single unit. The unit has a fuel tank as part of the primemover. The NAVSEA prime mover measures 54" x 32" x 96" and weights 3800 lbs.,more than twice that of the ADAPTS.
22
COMPARISON OF POTENTIAL OPERATING POINTS
PRIME MOVER: ADAPTS 40 HPFLUID PUMPED: FRESH WATER
5o80_ SO
/00 TYPICAL SYSTEM*CHARACTERISTIC CURVE
62.8 FRAMO TK-5
0
-15 0
FLOW RATE (gpm)
'IV 2o0 300 400 A /l r 500
FIGURE 14
*System consists of a 12-foot static head and 100 feet 4-inch corrugated
stainless steel discharge hose.
**Framo TK-4 with vickers 25M42A lC20 hydraulic motor data from previouspump test
23
COMPARISON OF POTEiTIAL OPERATING POINTS
PRIME MOVER: ADAPTS 40 HPFLUID PUMPED: #4 FUEL OIL (110-120 cS)
TYPICAL SYSTEM*-250 CHARACTERISTIC CURVE
i 40
-; FRAMO TK-5
-4o0 /0 . FRAMO TK-4
/0 4WO
20-" EUREKA 150
0 I * 5/o I /0 2000~Sco 0000 4c0
FLOW RATE (gpm)
I I I ISoo 300 4oo ei/h¢ foC
FIGURE 15
*System consists of a 12-foot static head and 100 feet 4-inch corrugatedstainless steel discharge hose.
**Framo TK-4 with vickers 25M42A 1C20 hydraulic motor data from previous
pump test.
24
- -- -
COMPARISON OF POTENTIAL OPERATING POINTS
PRIME MOVER: NAVSEA 80 HPFLUID PUMPED: #4 FUEL OIL (110-120 cS)
TYPICAL SYSTEM*0- / CHARACTERISTIC CURVE
/00
- FRAMO TK-5
10 Ae60
IN.>
So_/000 /$Do Z 0
FLOW RATE (gpm)
/00 .200 300 4r00 41 o
FIGURE 16
*System consists of a 12-foot static head and 100 feet 4-inch corrugatedstainleus steel discharge hose.
**NAVSEA 80 HP prime mover has capability to operate two (2) Framo TIC-S
pumps simultaneously.
25
6.0 CONCLUSIONS
From the results of this pump test, the following conclusions can be made.
1. The Framo TK-5 can provide a greater discharge flow rate than theFramo TK-4 under the same test conditions.
2. The Framo TK-5 performed well with the ADAPTS prime mover.
3. Both the Framo 1K-5 and the Thune-Eureka 150 pumps performed wellwith the NAVSEA prime mover.
4. The NAVSEA prime mover has the capability to operate two Framo TK-5pumps simultaneously.
26
26
REFERENCES
1. Hydraulic Institute Standards, Hydraulic Institute Standards forCentrifugal, Rotary & Reciprocating Pumps. 13th ed., Cleveland, Ohio:Hydraulic Institute Standards, 1975.
2. Framo TK-4 Pump Test. Groton, Connecticut: USCG Research andDevelopment Center, 1977.
3. Hawthorne, R.C., "Flow in Corrugated Hose." Product Engineering, June 10,1963, p. 98-100.
4. Karassik, I.J., Pump Handbook. New York: McGraw-Hill Book Co., 1976.
27
L~i
IAPPENDIX A
FUEL OIL VISCOSITIES
A-i
TEST FLUID PROPERTIES
500-
Kinematic 40
Viscosity(centistokes). 300.
/00-
20 40 60 80 /00
TEMPERATURE (OF)
FIGURE A-i
NO. 4 FUEL OIL VISCOSITY GRAPH
500W 0
Kinematic 4X
Viscosity .70000.(centistokes)
2 000
20 40 60 80 /00TE14PERATURE (OF)
FIGURE A-2
NO. 6 FUEL OIL VISCOSITY GRAPH
A- 2
APPENDIX B
RAW TEST DATA
B-1
" ;/ - ,i • .. .. .. -- -,' : " i " s.:' : x;.. ,..
TABLE B-1
PUMP TESTED: FRAMO TK-4HYDRAULIC PRIME MOVER: NAVSEA 80 HPFLUID PUMPED: Fresh Water
HYDRAULIC SYSTEM PUMP _ _
ENGINE TEMP PRESS PRE55 FLOW HEAD # INCHES TIME FLUIDSPEED OIL SUPPLY RETURN RATE PUMPED TEMP
(RPM) (OF) (psi) (psi) (GPM) (psi) (in) (min) (OF)
2000 100 2100 45 40 27 6.125 2.90 521900 100 2065 41 40 30 6.190 2.98 521900 100 2020 40 40 40 6.060 3.22 521880 100 1880 39 40 50 6.000 3.83 521880 100 1700 39 40 60 6.090 4.88 521800 100 1200 40 40 75 2.940 5.87 52
SHUT OFF HEAD 95 psi
TABLE B-2
PUMP TESTED: FRAMO TK-5HYDRAULIC PRIME MOVER: ADAPTS 40 HPFLUID PUMPED: Fresh Water
HYDRAULIC SYSTEM PUMP-MINE TEMP PRESS PRESS FLOW HEAD # INCHES TIME F LUSPEED ENG SUPPLY RETURN RATE PUMPED TEMP(RPM) (OF) (psi) (psi) (GPM) (psi) (in) (min) (OF)
2800 170 2000 60 17 4.5 12 4.05 522800 190 2000 55 17 10.0 12 4.55 522800 215 2000 50 18 20.0 12 5.63 522775 215 2000 50 20 30.0 6 3.40 522750 185 2000 50 21 40.0 6 4.63 522800 205 2000 50 23 50.0 6 5.20 522775 225 2000 40 24 60.0 3 3.28 52
SHUT OFF HEAD 80 psi
B-2
-awb
TABLE 8-3
PUMP TESTED: FRAMO TK-5HYDRAULIC PRIME MOVER: NAVSEA 80 HPFLUID PUMPED: Fresh Water
HYDRAULIC SYSTEM PUMPENGINE TEMP PRESS PRESS FLOW HEAD INCHES TIME FLUIDSPEED OIL SUPPLY RETURN RATE PUMPED TEMP(RPM) (OF) (psi) (psi) (GPM) (psi) (in) (min) (OF)
1150 100 2440 29.0 20 10 12.000 3.62 521150 100 2420 28.5 20 20 12.000 4.35 521100 85 2400 32.0 20 30 6.500 2.52 521150 90 2420 33.0 22 40 6.125 3.13 521250 90 2400 34.0 23 50 6.125 4.18 521250 90 2400 35.0 24 60 5.875 5.08 52
SHUT OFF HEAD 97 psi
TABLE B-4
PUMP TESTED: FRAMO TK-5HYDRAULIC PRIMr VWADAPTS 40 HPFLUID PUMPED: #4 Fuel Oil
HYDRAULIC SYSTEM PUMPENG'INE TM PRESS PRESS FLOW HEAD # NHS TIME FLUID
SPEED ENG SUPPLY RETURN RATE PUMPED TEMP(RPM) (OF) (psi) (psi) (GPM) (psi) (in) (min) (OF)
2800 239 2150 70 17 3 6.35 2 107.52825 237 2150 65 17 10 10.00 4 107.5
* 2800 237 2100 70 19 20 8.25 4 107.52800 232 2100 75 20 30 6.13 4 107.02775 225 2150 75 22 40 5.90 4 107.02725 195 2150 80 23 50 4.20 4 107.25
SHUT OFF HEAD 65 psi
B-3
TABLE B-5
PUMP TESTED: FRAMO TK-5HYDRAULIC PRIME MOVER: NAVSEA 80 HPFLUID PUMPED: #4 Fuel 0il
HYDRAULIC SYSTEM PUMPENGINE TEMP PRESS PRESS FLOW HEAD # INCHES TIME FLUIDSPEED OIL SUPPLY RETURN RATE PUMPED TEMP(RPM) (OF) (psi) (psi) (GPM) (psi) (in) (min) (OF)
1100 102 2450 40 19.0 2 6.50 2 108.01100 102 2450 40 19.0 10 5.30 2 107.31100 102 2450 42 19.5 20 9.80 4 106.71120 100 2450 45 20.0 30 9.25 4 106.51190 100 2450 50 20.5 40 7.25 4 106.01200 90 2450 55 22.0 50 5.13 4 106.01220 80 2450 65 23.0 60 3.75 4 106.0
SHUT OFF HEAD 85 psi
TABLE B-6
PUMP TESTED: EUREKA 150HYDRAULIC PRIME MV ADAPTS 40 HPFLUID PUMPED: Fresh Water
HYDRAULIC SYSTEM PUMPENGINE TEMP PRESS PRESS FLOW HEAD # INCHES TIME FLUIDSPEED ENG SUPPLY RETURN RATE PUMPED TEMP(RPM) (OF) (psi) (psi) (GPM) (psi) (in) (min) (OF)
2820 1000 60 29 6 6 1.58 522800 1000 60 29 10 6 1.80 522820 1000 60 30 29 6 3.55 522800 1200 80 30 30 6 7.05 52
SHUT OFF HEAD 35 psi
B-4
TABLE B-7
PUMP TESTED: EUREKA 150HYDRAULIC PRIME MOVER: ADAPTS 40 HPFLUID PUMPED: #4 Fuel 0il
HYDRAULIC SYSTEM I PUMP TIMEENGINE TEMP PRESS PRESS FLOW HEAD # INCHES TLUSPEED ENG SUPPLY RETURN RATE PUMPED TEMP
(RPM) (OF) (psi) (psi) (GPM) (psi) (in) (min) L (F)
2800 128 1325 200 30 4 14.25 4 1062800 122 1300 205 30 15 9.00 4 1062800 117 1300 200 30 20 10.75 6 1062800 110 1400 230 30 30 4.00 4 106
SHUT OFF HEAD 35 psi
TABLE B-8
PUMP TESTED: EUREKA 150HYDRAULIC PRIME MOVER: NAVSEA 80 HPFLUID PUMPED: #4 Fuel OTl
HYDRAULIC SYSTEM PUMP IENGINE I'MP PRESS PRE55 FLOW HEAD # INCHES TIME FLUIDSPEED OIL SUPPLY RETURN RATE PUMPED TEMP(RPM) (OF)- (psi) (psi) (GPM) (psi) (in) (min) (OF)
2150 100 2450 80 47.0 10 11.50 2 106.02150 100 2450 80 46.5 20 9.85 2 105.02120 95 2450 90 47.0 30 8.85 2 104.52120 90 2425 90 47.0 40 7.25 2 104.52080 80 2450 100 46.5 50 11.20 4 104.52080 67 2425 100 44.0 60 8.50 4 104.0
SHUT OFF HEAD 70 psi
B-5
-- - - -- - - - - .-
APPENDIX C
CORRUGATED HOSE FLOW CHARACTERISTICS
C-i
The fluid expansion theory was used to compute the head loss through the4-inch corrugated stainless steel discharge hose. An explanation of the fluidexpansion theory may be found in Product Engineering magazine (June 1963).All the equations used are extracted from the article, Flow in Corrugated Hose.
The fluid expansion theory assumes that the corrugations behave as aseries of uniformly spaced orifices. This assumption allows theDarey-Weisbach resistance equation with the friction factor (f) a function ofthe corrugation spacing (pitch (s)), hose length (L), and hose inside diameter(D) to be used in calculating the pressure loss. The following relationshipsexist.
p .f L (V2P)
and f = 1 D0. 4 ))
where, P = the pressure loss (psi)V = fluid velocity (fps)P= fluid density (lb per cu. ft.)
and 9266 = unit conversion constant
Table D-1 lists the parameters which were set constant for the examplecase. Applying these constants and substituting the flow rate (Q) divided bythe hose cross-sectional area (A) for the velocity (V) in the pressure lossequation the following relationships result;
For 11% P :and 4uel oil P X10 '
where P • the pressure loss (psi)and Q = the fluid flow rate (gpm)
Table 0-1
Parameter Value
Length (L) 1200 in (100 ft)Dia (0) 4 inPitch (S) 0.231 in/cQrrugatIonDensity (PH20) 62.5 lb/fti
(P#4F.O.) 56.25 lb/ft3
C-2
I --' '- . .. . . . . .. ..... ... . ...