joseph felice, penn state university, fluids lab portfolio

8/10/2019 Joseph Felice, Penn State University, Fluids Lab Portfolio

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1

O P 25, 50, 75 100 . A

B H . , H .

E . .

.


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1

Introduction

The goal of this experiment is to operate the Pelton wheel in order to gather data related to itsfunction for calculations which will yield characteristic plots of braking/water horsepower, speedand efficiency.

Pelton Wheel Apparatus

The Pelton wheel apparatus shown in Figure 1 below was the equipment used for this labexperiment. Encased in the white housing is the turbine wheel. The gage in front of the white

housing measures the pressure of thewater jet. Then to the left of the pressuregage is the spear valve. Adjusting thisvalve allows the operator to control theintensity of the jet stream on the wheel.

In this lab the intensity is varied from 25,50, 75 and 100%.

In this apparatus the pressure is suppliedby a water pump also seen in Figure 1.The power source for this pump is anelectric motor. In the image above, thecylindrical white casing for the waterpump can be seen at the bottom.

1 . .

A

. A ,

.

2

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2

Essentially, how a Pelton wheelapparatus works is first the electricmotor supplies power to the water

pump. The electric motor is variablespeed and therefore is regulated bythe input speed controller shown inFigure 3. After a few minutes thepumps builds up pressure. Afterenough pressure has been built upthe operator must then adjust thespear valve to allow the water jet toflow into the chamber containing theturbine wheel.

Experimental Procedure [1]

1. Turn on the electric variable control motor by the power switch

2. Allow the Pelton wheel pump to operate a few minutes to build up pressure.

3. Turn the spear valve to the desired setting. Start with 25%. Then repeat for 50, 75 and100%.

4. Record the required data for the calculations needed for characteristic plots.

Results and Discussion

This section includes the following characteristic plots:

Brake horsepower vs. turbine speed

Water horsepower vs. turbine speed

Turbine efficiency vs. turbine speed

3 . A

, .


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1 B .

2 .


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3 B .

The braking and water horsepower were both at a maximum when the spear valve was adjustedto a 100% setting. However, efficiency was at a maximum for each setting of the spear valvefor medium level turbine speeds.

Conclusion

Efficiency could be increased by maintaining a medium turbine speed. This is where themaximum efficiency seemed to occur for spear setting during operation of the Pelton wheel.

Appendix

25%Open

TurbineLoad(lb f )

TurbineSpeed(rpm)

PressureHead(psig)

Flow(ft 3 /min)

Volts Amps MotorSpeed(rpm)

MotorLoad(lb f )

1 0.1063 1858 15 3.25 180 3.2 2127 1.5302 0.4125 1608 15 3.00 180 3.2 2127 1.5563 0.7313 1508 15 3.12 180 3.2 2127 1.5444 0.9750 1316 15 3.12 180 3.2 2127 1.362

5 1.0750 1223 15 3.12 180 3.2 2127 1.5646 1.2000 1140 15 3.12 180 3.2 2127 1.5747 1.2823 1040 15 3.12 180 3.2 2127 1.5608 1.3750 960 15 3.12 180 3.2 2127 1.5669 1.5063 860 15 3.12 180 3.2 2127 1.556

10 1.8750 0 15 3.12 180 3.2 2127 1.564

2 A 25%.


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5

50%Open

TurbineLoad(lb f )

TurbineSpeed(rpm)

PressureHead(psig)

Flow(ft 3 /min)


MotorLoad(lb f )

1 0.0875 1909 15 5.20 190 3.5 2290 2.1742 0.6500 1710 15 5.20 190 3.5 2290 2.1843 1.1313 1530 15 5.20 190 3.5 2290 2.1824 1.5188 1352 15 5.20 190 3.5 2290 2.1745 1.8500 1170 15 5.20 190 3.5 2290 2.1766 2.1188 1041 15 5.20 190 3.5 2290 2.2037 2.5188 807 15 5.20 190 3.5 2290 2.2048 2.6875 630 15 5.20 190 3.5 2290 2.2089 2.8875 510 15 5.20 190 3.5 2290 2.204

10 3.1000 0 15 5.20 190 3.5 2290 2.184

2 A 50%.

75%Open TurbineLoad(lb f )

TurbineSpeed(rpm)

PressureHead(psig)

Flow(ft 3 /min) Volts Amps MotorSpeed(rpm)

MotorLoad(lb f )

1 0.0813 1942 15 6.50 200 5.0 2460 2.6502 0.9125 1681 15 6.50 200 5.0 2452 2.6723 1.5250 1502 15 6.50 200 5.0 2445 2.6864 1.8688 1309 15 6.50 200 5.0 2460 2.6685 2.5063 1142 15 6.50 200 5.0 2457 2.6526 2.7500 1019 15 6.50 200 5.0 2456 2.6427 3.1125 826 15 6.50 200 5.0 2459 2.6428 3.4188 627 15 6.50 200 5.0 2460 2.6489 3.5563 443 15 6.50 200 5.0 2457 2.664

10 3.8438 0 15 6.50 200 5.0 2453 2.666 3 A 75%.

100%Open

TurbineLoad(lb f )

TurbineSpeed(rpm)

PressureHead(psig)

Flow(ft 3 /min)


MotorLoad(lb f )

1 0.1000 1935 15 7.20 210 5.5 2540 2.9242 1.0875 1660 15 7.20 210 5.5 2541 2.9263 1.6563 1499 15 7.20 210 5.5 2539 2.9284 2.2438 1308 15 7.20 210 5.5 2539 2.9065 2.7313 1121 15 7.20 210 5.5 2536 2.918

6 3.0875 996 15 7.20 210 5.5 2539 2.9227 3.4875 803 15 7.20 210 5.5 2544 2.9248 3.7375 629 15 7.20 210 5.5 2543 2.9349 3.9188 490 15 7.20 210 5.5 2549 2.952

10 4.1063 0 15 7.20 210 5.5 2551 2.946

4 A 100%.


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6

25% Open WaterHorsepower

(WHP)

TurbineBraking

Horsepower(BHP T)

PumpBraking

Horsepower(BHP P )

PumpEfficiency

( )

TurbineEfficiency

( )

1 0.249532 0.019733 0.477401 0.522688 0.079084

2 0.249532 0.066300 0.477401

0.522688

0.2656983 0.249532 0.110220 0.477401 0.522688 0.4417064 0.249532 0.128400 0.477401 0.522688 0.5145645 0.249532 0.131400 0.477401 0.522688 0.5265866 0.249532 0.136800 0.477401 0.522688 0.5482267 0.249532 0.133180 0.477401 0.522688 0.5337188 0.249532 0.131940 0.477401 0.522688 0.5287509 0.249532 0.129400 0.477401 0.522688 0.518570

10 0.249532 0 0.477401 0.522688 0 5 A 1

25%.

50% Open WaterHorsepower(WHP)

TurbineBrakingHorsepower

(BHP T)

PumpBrakingHorsepower

(BHP P )

PumpEfficiency( )

TurbineEfficiency( )

1 0.430745 0.01670 0.73184 0.58858 0.0387702 0.430745 0.11110 0.73184 0.58858 0.2579263 0.430745 0.17302 0.73184 0.58858 0.4016764 0.430745 0.25200 0.73184 0.58858 0.4763845 0.430745 0.21640 0.73184 0.58858 0.5023866 0.430745 0.22047 0.73184 0.58858 0.5118347 0.430745 0.20319 0.73184 0.58858 0.4717188 0.430745 0.16924 0.73184 0.58858 0.392901

9 0.430745 0.14720 0.73184 0.58858 0.34173410 0.430745 0 0.73184 0.58858 0 6 A 2

50%.


(WHP)

TurbineBraking

Horsepower(BHP T)

PumpBraking

Horsepower(BHP P )

PumpEfficiency

( )

TurbineEfficiency

( )

1 0.55476 0.01578 0.95324 0.58197 0.028442 0.55476 0.15334 0.95324 0.58197 0.276403 0.55476 0.22900 0.95324 0.58197 0.41278

4 0.55476 0.24440 0.95324 0.58197 0.440565 0.55476 0.28600 0.95324 0.58197 0.515546 0.55476 0.28002 0.95324 0.58197 0.504767 0.55476 0.25700 0.95324 0.58197 0.463248 0.55476 0.21426 0.95324 0.58197 0.386229 0.55476 0.15748 0.95324 0.58197 0.28388

10 0.55476 0 0.95324 0.58197 0 7 A 3

75%.


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(WHP)

TurbineBraking

Horsepower(BHP T)

PumpBraking

Horsepower(BHP P )

PumpEfficiency

( )

TurbineEfficiency

( )

1 0.62591 0.01934 1.08652 0.57607 0.030902 0.62591 0.18046 1.08652 0.57607 0.288323 0.62591 0.24820 1.08652 0.57607 0.396544 0.62591 0.29340 1.08652 0.57607 0.468765 0.62591 0.30600 1.08652 0.57607 0.488886 0.62591 0.29920 1.08652 0.57607 0.478027 0.62591 0.27980 1.08652 0.57607 0.447028 0.62591 0.23500 1.08652 0.57607 0.375469 0.62591 0.19194 1.08652 0.57607 0.30666

10 0.62591 0 1.08652 0.57607 0 8 A 4

100%.

B A ( )

Pelton Wheel Apparatus

A ( ) ( )6.3 9.2 1.6

9 A .

Sample Calculations

Turbine Braking Horsepower @ 25%

[(6.3/12 feet)*(1858 rpm)*(1.7/16 lbs)*2*pi] /33000 = 0.01973 hp

Velocity @ 25%

Q = VA

[3.12 cubic feet/min]/60 = pi*[(9.2/12 feet)/2] 2*V

V = 0.1126 ft/s

Water horsepower @ 25%

[[[15*144 lb/ft 2]/[(1.94 slug/ft 3)*(32.2 ft/square second)] + (0.1126 ft/s) 2/[2*32.2ft/s 2]]*3.12/0.1337 gal/min*10]/33000 = 0.249532 hp

Turbine Efficiency @ 25%

0.019733 hp/0.249532 hp = 0.079084


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References

[1] Summarized from ME 308 Lecture Notes, Fall 2014, Pelton Experiment Description, Slides1-3. Pennsylvania State University, Angel Course Webpage.


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1

Joseph R. Felice

Pennsylvania State University

11/21/2014

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COPR = 114 B / 37.1 B / / 122 B / 114 B / = 9.6

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COPR = 109 B / 37.1 B / / 122 B / 109 B / = 5.5

C , . A ,

.

COPE = 920 907.7 / 329.8 326.3 = 3.5

A 3.5 H R 45 .

= I /A = (122 B / 114 B / )/(122 B / 155 B / ) = 1.14 114%

C , .

= ( ) = (0.41 / )*(8.35 / )*(0.999 B / F)*(82 F 66 F) = 54.72B / 4

4 . 66 F 82 F 74 F.

(329.8 326.3 ) / (45 /60 ) * 0.05 * 2 = 0.467


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5

D E = 122 B / 115 B / = 7 B /

D E = 123 B / 114 B / = 9 B /

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H . H ,

D E = 122 B / 111 B / = 11 B /

D E = 122 B / 115 B / = 8 B /

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= 0.59 / *(122 B / 115 B / ) = 4.13 B /

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= 0.59 / *(37.8 B / 121 B / ) = 49.09 B /

= 0.59 / *(114 B / 26.2 B / ) = 51.80 B /

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26.2 B / (A , 8) E 37.1 B / (A 7). 0 B / E .

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E /E = (114 B / 26.2 B / ) + 7 B / /(121 B / 37.8 B / ) = 1.139

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11.6 B / . , , 1:1 H .

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COPC = 117 B / 37.1 B / / 124 B / 117 B / = 11.4

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11.4. , COP .

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COPC = 115 B / 36.8 B / / 123 B / 115 B / = 9.8

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9.8 COPC .


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( / ) 120

14.7 82 ( / ) 0.266

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( / ) 115

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3 A 38 68 .

( / ) 122

109 119 ( / ) 0.231

4 A 109 119 .

( / ) 121

110 113 ( / ) 0.228

5 A 110 113 .


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115 79 ( / ) 0.0786

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( / ) 37.1110 77 ( / ) 0.0773

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( / ) 26.2

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( / ) 114

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9 A 67 .

2 ( / ) 117

14.7 67 ( / ) 0.26

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Operation of the Pelton wheel apparatus will involve adjusting the mass flow rate of the

nozzle jet stream for four open settings of the spear valve- 25, 50, 75 and 100 percent. At each setting data will be recorded allowing for a computational analysis which willyield characteristic plots for Braking Horsepower vs. Turbine Speed, Water Horsepowervs. Turbine Speed and Turbine Efficiency vs. Turbine Speed.

Figure 1 Shown above is an image of a Rankine Cycler System,Image courtesy of Turbine Technologies, Ltd [1].

C

Joseph R. Felice

Pennsylvania State University 12/1/14


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Objective:

The purpose of this laboratory experiment is to operate the Rankine Cycler System inorder to conduct technical calculations regarding turbine efficiency.

Introduction:The rankine cycle is the process of converting heat to work [2]. This particularexperiment will utilize the Rankine Cycler System with a data acquisition computer tocollect values for temperature, pressure, speed, voltage and current. After these datapoints are collected they will be downloaded into an Excel file where plots will begenerated. After these plots are made they will serve to aid in calculations for turbineefficiency.

Specifically, the plots for turbine inlet/outlet temperatures and pressures will beanalyzed for times when steady-state conditions occurred. Due to the absence of apump in this Rankine Cycler System genuine steady-state conditions cannot beachieved. Therefore, times when conditions were as close to steady-state as possiblewill be used for turbine efficiency calculations. Two different times will be selected todetermine if there is any variation in the efficiency during operation of the RankineCycler System.

These will be performed by entering the turbine inlet/outlet temperature and pressurevalues into a steam properties calculator which will then yield the necessary enthalpiesfor performing the computations. Values for entropy will also be collected. Shownbelow in Figure 2 is an image of a turbine in a Rankine Cycler System [1].

Figure 2 Shown above is an image of a turbine in a Rankine Cycler System, ImageCourtesy of Turbine Technologies, Ltd .


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Raw Data Plots:

Figure 3 Above is a plot of boiler pressure vs. time. Due to the absence of a pump atransient state occurs during operation of the Rankine Cycler System.

Figure 4 Above is a plot of boiler temperature vs. time.


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Figure 5 Above is a plot of fuel flow vs. time. The sudden drop in flow is most likely ananomaly in the acquisition of the data by the computer.

Figure 6 Above is a plot of turbine inlet pressure vs. time.


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Figure 7 Above is a plot of turbine inlet temperature vs. time.

Figure 8 Above is a plot of turbine outlet pressure vs. time.


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Figure 9 Above is a plot of turbine outlet temperature vs. time.

Figure 10 Above is a plot of turbine rpm vs. time.


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Figure 11 Above is a plot of generator dc amps output vs. time.

Figure 12 Above is a plot of generator dc voltage output vs. time.


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Figure 13 Above is a plot of propane energy release vs. time. The sudden drop in thisdata relates to Figure 5 since flow rate was involved in the energy computation.

Figure 14 Above is a plot of generator power output vs. time.


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Figure 15 Above is a plot of cycle efficiency vs. time.

Calculations:

The isentropic efficiency for the turbine is determined using

n turb = h in h out,a /h in h out,s

At time 9:21:52 using the online calculator yielded

Turbine Inlet Recorded Data ValuePressure (kPa) 162.2

Recorded @ 9:21:52 Temperature ( C) 113.0

Table 1 Shown above is a table of values obtained by the data acquisition computer.

Turbine Inlet Recorded Data ValueEntropy (kJ/kg*K) 7.232

Recorded @ 9:21:52 Enthalpy (kJ/kg) 2696.62

Table 2 Shown above is a table of values for the thermodynamic properties based onthe values acquired by the data acquisition computer.


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Turbine Outlet Recorded Data ValuePressure (kPa) 130.4



Turbine Outlet Recorded Data ValueEntropy (kJ/kg*K) 7.300



Turbine Outlet - Isentropic Recorded Data Value

Pressure (kPa) 130.4Recorded @ 9:21:52 Temperature ( C) 106.0





Thus, for 9:21:52

n turb = 2696.62 2691.245/2696.62 2684.959 = .461 or 46.1%

For 9:29:24 using the online calculator yielded

Turbine Inlet Recorded Data ValuePressure (kPa) 204.3



Turbine Inlet Recorded Data ValueEntropy (kJ/kg*K) 7.169




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Turbine Outlet Recorded Data ValuePressure (kPa) 130.2






Turbine Outlet - Isentropic Recorded Data Value

Pressure (kPa) 130.2Recorded @ 9:29:24 Temperature ( C) 105.0





Thus, for 9:29:24

n turb = 2726.830 2704.267/2726.830 2683.511 = .521 or 52.1%

Discussion:

In order to increase the isentropic efficiency of the turbine a cooling system should beinstalled in the condenser tower. Thus, more steam would be condensed and returnedto the pump (if one were present in this apparatus) to be reused.

The overall cycle efficiency is given byn sys = generator power output/propane power input

During this trial of the Rankine Cycler System the overall cycle efficiency maximized at9:45:12 at a value of 6.19 * 10 -5 . This value is equivalent to 6 * 10 -3 %. Thus, this is avery inefficient turbine. A suspected faulty bearing is the cause of the systeminefficiency.


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In regard to the turbine efficiency at 9:21:52 it was calculated at 46.1%. At this time theturbine inlet pressure was recorded at 162.2 kPa. A short time later at 9:29:24 theturbine efficiency was calculated at 52.1%. This time the turbine inlet pressure wasmeasured at 204.3 kPa. Thus, the turbine efficiency increased with a greater value forinlet pressure. Essentially a higher value of inlet pressure means that a smallerpercentage of pressurized steam is lost to overcoming the rolling frictional factor of theturbine wheel. Hence, with a higher percentage of the overall inlet steam pressurebeing available for moving the turbine wheel the turbine efficiency increased.

The generator power output maximized at 9:42:28 at a value of 9.19 Watts. At this timethe turbine inlet temperature was 207 C at a pressure of 117 kPa. Also, the turbinerpm was 3,580 rpm, which was the maximum rpm achieved during operation of the labapparatus. Therefore, steam at a high temperature and low pressure drives the turbinewheel to its maximum rpm, thus causing the generator power output to yield itsmaximum value. Since at a high temperature and low pressure the steam will havemore entropy it makes sense that the combination of values for pressure andtemperature at 9:42:28 drives the turbine to its maximum level of rpm.

Changes that could be made to the Rankine Cycler System if space permitted includethe addition of a collector for the condensed steam and a pump. The addition of theseelements to the apparatus would make for a genuine rankine cycle and more realisticdata collection such as achieving steady state boiler pressure instead of a transientstate during operation.


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References

[1] Turbine Technologies, LTD, April 2012, RankineCycler Steam Turbine PowerSystem Sample Lab Experiment Procedure. From.

[2] Ecourses, Thermodynamics Theory: Rankine Cycle. From.

Calculator:

CalcSteam, Calculation of thermodynamic properties of overheated steam. From.

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