LAKEHEAD UNIVERSITY DEPARTMENT OF MECHANICAL ENGINEERING MECHANICAL ENGINEERING LABORATORY ENGI-3555 WD LAB MANUAL LAB COORDINATOR: Dr.

Transcription

1 LAKEHEAD UNIVERSITY DEPARTMENT OF MECHANICAL ENGINEERING MECHANICAL ENGINEERING LABORATORY ENGI-3555 WD LAB MANUAL LAB COORDINATOR: Dr. Basel Ismail, P.Eng. STUART DAVIE GROUP 32 EXPERIMENT 1 RANKINE CYCLER DATE THE EXPERIMENT WAS CONDUCTED: DATE OF SUBMISSION:

2 Summary The Engineering applied science methods for increasing performance indicators of the Rankine Cycle in general have been discussed in detail. Various effects as a result making adjustments to the generalized Rankine cycle have been listed in bullet format in the background section of this report the effects of lowering the condenser pressure, the effects of superheating the steam to a high pressure, and the effects of increasing the boiler pressure have been examined. The output performance indicators such as heat addition given in units of kilo Watts, Work output given in units of Kilo Watts, The Power generated given in units of Watts, The heat rejected given in units of kilo Watts, and the system overall efficiency given as a percentage have been identified as quantities of interest for improvement. With the raw data from the experimental procedure, the calculations that followed, the assumptions made, the limitations recognized appropriate design enhancement techniques have been applied. The design enhancement techniques of improving the Rankine Cycler Apparatus that have been applied have made a significant overall improvement. More specifically these improvements are an 8.07% increase in the heat addition, a % increase in work output, a % increase in power generation a decrease in 5.99 % heat rejection and an overall system efficiency of 71.11%.

3 TABLE OF CONTENTS SUMMARY... #1 INTRODUCTION... #2 PROBLEM #2 BACKGROUND #2-4 PURPOSE #4 LIMITATIONS/ASSUMPTIONS #5 DISCUSSION... #6 TALKING #6 OACETT TR 3.1a ANALYITCALLY SUMMARIZING DATA CONCLUSSIONS... #8 RECOMMENDATIONS... #9 APPENDIX... #10 APPENDIX 6.1A... #10 APPENDIX 6.1B... #11 DOCUMENTATION... #12 APA STYLE REFERENCES #12 Problem

4 Design modifications are required to be made to the Original Rankine Cycler Apparatus that is a current experimental apparatus at Lakehead University. The Rankine Cycler Apparatus consists of the mechanical components such as - a dual-pass, flame tube boiler, a boiler level sight glass with two adjustable bezels, a steam admission valve, an impulse micro steam turbine, a four pole AC/DC electric generator, a condensing tower, a data acquisition computer and a liquid propane cylinder. Figure 1 Figure 2 Figure 1 represents the current system operation process for the Original Rankine Cycler Apparatus. The numbering present on each path between each mechanical component is the corresponding thermodynamic state. For instance in theory state 1 located at the outlet of the condenser has the same thermodynamic properties as state 1 located at the inlet of the boiler this is based on the steady state steady flow assumption, where properties such as enthalpy, entropy, pressure, volume, etc remain constant until undergoing a thermodynamic process such as a polytropic process, an isometric process, and an isothermal process etc. The same theory is extrapolated and applied to thermodynamic state 2, thermodynamic state 3, and thermodynamic state 4, subjected to the influences of the remaining mechanical devices such as the throttling valve and the turbine. Figure 2 is the current Temperature Entropy diagram also known for convience as a T- S diagram in general; but, for this current application applies to the representation of Temperature given in units of Celssius and entropy given in units of kilo-joule per kilo gram Kelvin for the Original Rankine Cycler Apparatus that is depicted in figure 3 and is the focus of study for modification techniques for this research and design activity. Each of the points and numbers represent a thermodynamic state and each of the paths represent a thermodynamic process while noting that this current system is operating on an open system. This process is operating on an open system because of the fact that superheated steam is discharged to the environment from the condenser at state 4 causing a brake in the cycle preventing the pure substance water to be recirculated to the system at state 1 on a continuous looped basis, where the water the steam that has been condensed to water is collected and measured. Table 2 indicates the relevant thermodynamic property such as pressure, temperature, enthalpy, and entropy for each given thermodynamic state.

5 Original Design Parameters Table 1 Quantity Boiler pressure at kpa Boiler temperature ⁰C Q in = m (h2 h1) Turbine pressure at the inlet kpa Turbine pressure at the outlet kpa Turbine Temperature at the inlet ⁰C Turbine Temperature at the outlet ⁰C Air to fuel ratio 17.2:1 by mass DC 0.25 Amps Power generated = ( ngenerated ) Wt 100 DC 5.48 Volts Fuel Flow 5.50 Litres/Min Turbine speed is RPM ngenerated = (Power generated Condensate Collected 680 ml /Wt) 100 Refill Water 4600 ml Mass flow Rate is kg/s With a run time of 31 mintues Value kw Wt = m (h3 h4) kw 1.37 W % Qout = m (h4 h1) kw ncondenser = condensate collected /refillwater % Energy input of propane nsystem overall = ((Power generated)/ (Energy Input of Propane))* W % Table 1 represents the output performance indicators for the current original Rankine Cycler Apparatus that have been obtained through calculations, assumptions, property tables, experimental results, and raw data. The Original Design Parameters for the Rankine Cycler Apparatus have been listed in bullet format alongside table 1. The output performance indicators of interest for improvement through design techniques and modifications are heat addition given in units of kilo Watts, Work output given in units of Kilo Watts, The Power generated given in units of Watts, The heat rejected given in units of kilo Watts, and the system overall efficiency given as a percentage. Background Cengel & Boles state that(2011,chaper 10) The basic idea behind all the modifications to increase thermal efficiency of a power cycle is the same: Increase the average temperature at which heat

6 is transferred to the working fluid in the boiler, or decrease the average temperature at which heat is rejected from the working fluid in the condenser. Effects of Lowering the Condensor Pressure Lowering the operating pressure in the condenser sets the temperature of the steam to a lower value resulting in lower the temperature at which heat is rejected Increases the thermal efficiency of the cycle Develops a concern for air leakage into the condenser Effects of Superheating the Steam to High Temperature Increases heat input Increase in thermal efficiency Decreases moisture content of the steam at the outlet of the turbine Metallurgical considerations place a restriction the temperature to which superheated can take place meaning the materials can only with stand a certain temperature limit Presently the highest steam temperature allowed at the turbine outlet is about 620 ºC (Cengal & Boles, 2011 p. 560) Effects of Increasing the Boiler Pressure Heat addition process increases at the moment the pressure of the boiler increased Raises thermal efficiency Moisture content of steam at the turbine increases, this is not desirable but can be managed The primary purpose of a steam power plant is to generate electrical power by transforming heat to mechanical work then mechanical work to electrical work. For the case of the Original Rankine Cycler Apparatus the electrical power that has been generated is 1.37 W, the Quantity of the rate of heat addition is kw, and the mechanical work output from the turbine is 0.379kW. According to Wikipedia entropy can be defined on its website as In thermodynamics, entropy (usual symbol S) is a measure of the number of specific ways in which a thermodynamic system may be arranged, commonly understood as a measure of disorder. According to the second law of thermodynamics the entropy of an isolated system never decreases; such a system will spontaneously evolve toward thermodynamic equilibrium, the configuration with maximum entropy. Systems that are not isolated may decrease in entropy, provided they increase the entropy of their environment by at least that same amount. Since entropy is a state function, the change in the entropy of a system is the same for any process that goes from a given initial state to a given final state, whether the process is reversible or irreversible. However, irreversible processes increase the combined entropy of the system and its environment. Globally entropy is constantly increasing, during any actual exchange of energy there is a trace of entropy. For instance on a microscopic scale when there is an atomic transition or quantum jump there is an entropy increase meaning that the price of the quantum leap is the expense of an increase in entropy

7 and in more detail that specific atomic transition is not reversible. The increase in entropy can not be decreased and that particular quantum leap can not be reveresed. This is an example of a spontaneous process. On a bigger scale, say steam power plants for instance operating on a Rankine Cycle where the fuel is coal and when burned and replaced at a constant rate acts as a heat source. The process involved is not spontaneous like the quantum leap but is an engineered desired heat transfer process, For every piece of coal that is burned leaves an increase in entropy and a mark on our earth that cannot be reversed. And in contrast we need a sink to dispose of flue gas and a sink to dispose of the cooling medium such as water that is used to cool the steam through a heat exchanger. his transaction also increases entropy seeing that process can not be reversed. Heat is defined by (Cengal & Boles (2011, p.60) as the form of energy that is transferred between two systems and its surroundings The three laws of thermodynamics are 1.) Expression of the Conservation of Energy Principle Energy is a thermodynamic property. 2.) Energy has quality as well as quantity and actual processes occur in the direction of decreasing quality of energy 3.) The entropy of a pure Crystaline substance at absolute zero temperature is zero. Purpose Two common forms of practice to improve a Rankine Cycle can be modified by 1. Reheating the steam as it leaves the turbine and directing it to another Turbine. Increases cyclic efficiency about 4 to 5 percent Reheating the steam in stages Only two stages should be used for values under the critical value of P>22.06MPa. Introduced in the mid 1920 s Abandoned in the 1930 s operational challenges Single heat reintroduced in the late 1940 s double reheat I the late 1950 s Optimal reheat pressure is 1/4 th of the max cycle pressure. Main purpose is to reheat cycle is to protect the turbine blades by reducing the steam at the final stages of the polytropic expansion process. I would like to study Materials and Mechanical Engineering at Queens University so I can play apart in improving these types of process to improve the efficiency of cycles and leave a smaller economical footprint. 2. Regenerative Rankine Cycle Raises the temperature of the feedwater prior to entering the boiler which means less coal has to burned to reach the ideal temperature limit for a proper heat process to occur This method is a sacrificial approach, and can be viewed from a banking stance as an investment by extracting a quality of energy and relaying it to the feedwater prior to rendering the boiler Improves Cyclic efficiency

8 Convent means of dearating the feedwater to prevent cavitation in the pump, which is an important form of predictive preventive maintenance that is Important to us technologists Regeneration is used also to control an excessive volume flow rate of steam at the final stages of the turbine. Regeneration has been an advantageous tech unique in practice since the early 1920 s. 1.) Open Feed Water heaters Mixing chamber device requires extra pump Realistic due to simplicity Inexpensive Bring feed water to saturation state 2.) Closed Feed Water heaters Complex because of required internal tubing More expensive Less effective/2 streams don t mix The Design Modifications of the Rankine Cycler Apparatus that have been applied with the intentions of improving the output performance indicators of interest are listed below in no significant order. The T-S diagram corresponding to the modified design of the Rankine Cycler apparatus is attached. The calculations and analysis for the results when comparing the Modified Rankine Cycler Apparatus to the Original Rankine Cycler apparatus is presented in detail in the section of Analytically summarizing data. Design Modifications 1.) Lowering the operating pressure at the condenser outlet from kpa to atmospheric conditions of kpa. 2.) Increasing the boiler pressure from kpa to 1000 kpa 3.) Reheating the Superheat Vapor with the addition of a Turbine Limitations/Assumptions The major limitations and the assumptions taken into consideration for implementing design modifications to the Rankine Cycler apparatus are represented numerically.

9 1. Being restricted to lowering the pressure of heat rejection from the outlet of the condenser at thermodynamic state 6 to the environment at thermodynamic state 1 having minimum value of kpa. 2. Calculations were taken under the assumption of steady state steady flow as well as assuming an isentropic process from thermodynamic state 3 to thermodynamic state 4 and similarly thermodynamic state 5 to state The maximum temperature of the Rankine Cycler apparatus is 306⁰C 4. The throttling processed was assumed to be fixed starting at thermodynamic state 2 having an expansion process to thermodynamic state 3. The workout from the turbine without the throttling process can be calculated from the initial design values obtained as follows Wt = m(h2 h4) = kg s ( )kJ/kg equating to kw. When we compare these values to those tabulated in table 1 noting a difference of ( ) kw = kw. 5. The condenser efficiency of approximately 15 % restricted the overall performance of the system. 6. The efficiency of the power generation calculated from the initial design values was assumed to be held constant in order to determine the power generation from the modified version. 7. The Rankine Cycler apparatus is running on an open system preventing regeneration but is analyzed as a closed system respectfully 8. The current is held constant at 0.25 A 9. The additional turbine operates at RPM 10. The Mass flow rate is unchanged at an approximate value of Kg/s 11. The amount of Fuel Flow 5.50 Litres/Min remains the same as the original design of the Rankine Cycler Apparatus. 12. An additional Expansion Valve is neglected from Thermodynamic state 5 to thermodynamic state 6.

10 DISCUSSION PAGE 6 Talking A.) A T-S diagram is a Diagram that that gives us a visual representation of the states and processes involved it is essential for us as engineers to display these Diagrams prior to and well doing research. This acts as visual aid so we can see the relation between Temperature and Entropy. Referring to the schematic attached the region to the left of the saturation dome is the area where thermodynamic states are sub cooled, the area under the saturation dome is the mixture of the substance and to the right of the saturation dome represents the thermodynamic states of superheated vapor. Attached to this Technical Report in the Appendices is a clear representation of the T-S diagram that has been developed and is a representation of the proposed modified Rankine Cycle for the apparatus. During the research and modification process. B.) A schematic drawing of the major devices involved in the steam power plant is usually accompanied by a T-S diagram and calculations. This also provides visual add. This is really important especially for communication purposes, a lot of different phrases and words can have the same meaning but are take on different designated names, and this can be confusing so we use diagrams and schematics as a reference. C.) Identifying the processes from state to state will be made clear. Also, it is very important to understand that during a process there are energy interactions in the form of heat and work for considerations. Properties at states are only properties at states energy interactions do not happen at states they happen from state to state, for example the workout from the turbine does not occur at state 5 nor does it happen at state 6 the workout from the turbine happens during a process from state 5 to state 6 and this can be explained by the change in the state properties from state 5 to state 6 as well as from the theoretical reasoning and scientific explanation that work whether in a rate for or as energy is a path function, for analytical purposes we assume that the properties at a state do not change with respect to time. Below are engineering and scientific explanations of what is occurring from a thermodynamic state to a thermodynamic state known as a process which can be outlined corresponding to the schematic attached which again is a design modification of the Rankine Cycler for the Apparatus of experiment one at Lakehead University. As well as referencing the thermodynamic state properties and the values of quantities from table 1 and table 5. State 1 State 2 (saturated liquid superheated vapor) Boiler inlet - Throttling Valve inlet This is a thermodynamic Polytropic heat addition process. At state 1 the distilled water is assumed to be a saturated liquid with a temperature of 23.5 ⁰C, an absolute pressure kpa, an enthalpy of kj/kg, and entropy of kj/kgk. At state 2 the superheated vapor has has a temperature of ⁰C, an absolute pressure of 1000 kpa, an enthalpy of kj/kg, and entropy of kj/kgk. The heat addition can be computed as follows Qin = m(h2 h1) = kw

11 DISCUSSION PAGE 7 State 2 State 3 (superheat vapor-superheated vapor) Throttling valve inlet Turbine inlet This is a thermodynamic Polytropic expansion process. At state 2 the superheated vapor has a temperature of ⁰C, an absolute pressure of 1000 kpa, an enthalpy of kj/kg, and entropy of kj/kgk. At state 3 the superheated vapor has a temperature of 250 ⁰C, an absolute pressure of 500kPa, an enthalpy of 2961 kj/kg and an entropy of kj/kgk. State 3 State 4 (superheated vapor-superheat vapor) Turbine inlet Turbine outlet This is a thermodynamic Isentropic work output process. At state 3 the superheated vapor has a temperature of 250 ⁰C, an absolute pressure of 500kPa, an enthalpy of 2961 kj/kg and an entropy of kj/kgk, At state 4 the superheated vapor has a temperature of 175 ⁰C, a pressure of 300 kpa, an enthalpy of 2800 kj/kg, an entropy of kj/kgk. The work output can be computed as follows Wt = m(h3 h4) = kw State 4 State 5 (superheated vapor- reheated superheat vapor) Turbine outlet Turbine inlet This is a thermodynamic isobaric heat addition process. At state 4 the superheated vapor has a temperature of 175 ⁰C, a pressure of 300 kpa, an enthalpy of 2800 kj/kg, an entropy of kj/kgk. At state 5 the reheated superheated vapor has a temperature of 210 ⁰C, a pressure of 300 kpa, an enthalpy of 2900kJ/kg, and an entropy of 7.35 kj/kgk. The heat addition can be computed as follows Qin = m(h5 h4) = kw State 5 State 6 (reheated superheat vapor- saturated vapor) Turbine inlet Condenser inlet This is a thermodynamic isentropic work output process. At state 5 the reheated superheated vapor has a temperature of 210 ⁰C, an absolute pressure of 300 kpa, an enthalpy of 2900kJ/kg, and an entropy of 7.35 kj/kgk. At state 6 the saturated vapor has a temperature of 99 ⁰C, an absolute pressure of kpa, An enthalpy of kj/kg, and an entropy of 7.35 kj/kgk. The work output can be computed as follows Wt = m(h5 h6) = kw

12 DISCUSSION PAGE 7 State 6 State 1 (saturated vapor-saturated liquid) Condenser inlet Condenser Outlet Open Loop but assumed to be cycling back to state 1 This is a thermodynamic heat rejection process. At state 6 the saturated vapor has a temperature of 99 ⁰C, an absolute pressure of kpa, An enthalpy of kj/kg, and an entropy of 7.35 kj/kgk. At state 1 the distilled water is assumed to be a saturated liquid with a temperature of 23.5 ⁰C, an absolute pressure kpa, an enthalpy of kj/kg, and entropy of kj/kgk. The heat rejection can be computed as follows Qout = m(h6 h1) = kw EXPERIMENTAL PROCEDURE Figure 2 Figure 1 is a graphical image of the Rankine Cycler apparatus located in RL-1001 of Lakehead University Thunderbay Ontario. The environmental conditions in RL-1001 at Lakehead University can be obtained through the local weather network. The properties such as temperature and air need to be recorded and applied to the thermodynamic state 1 so that at a later time the other thermodynamic state properties can be obtained from the saturated liquid pure substance water property table in an available text book or from an online resource. Following the OPERATING INSTRUCTIONS as provided from the engineering lab instructor turn on and run the Rankine Cycler until 10 minutes of steady state operation

13 DISCUSSION PAGE 7 has been reached with or without a Pleatue of 350 degrees Celsius in the boiler temperature or until the level in the Sight glass has reached the one inch Mark. Follow the shut down procedure as instructed by the engineering lab instructor. Measure the volume of water required to refill the boiler by collecting the condensate from the condenser. A list of data will be provided by the lab instructor, this data includes the following where the known steady state values will be substituted and with those values a plot of boiler temperature with respect to time will need to be created using a software of either availability or preference. A discussion will need to be followed with relevance to steady state. Steady state values Boiler Pres. Turbine Pres. Turbine Pres. Boiler Temp. Turbine Temp. Turbine Temp. DC - A DC - V Fuel Flow Turbine PSIG (in) PSIG (out) PSIG Degrees C (in) Degrees C (out) Degrees C AMPS VOLTS LTRS/MIN RPM Atmospheric Press. PSI. condensate collected refill water run time Time Date B P T IN P T OUT P B T T IN T T OUT T DC - A DC - V Fuel Flow Turbine PSIG PSIG PSIG ー C ー C ー C AMPS VOLTS LTRS/MIN RPM Figure 3 Figure 2 represents the list of data will be provided by the lab instructor, this data includes the following where the known steady state values will be substituted and with those values a plot of boiler temperature with respect to time will need to be created using a software of either availability or preference. A discussion will need to be developed with relevance to the steady state assumption, a discussion will need to be developed regarding the condenser efficiency from a cost and environmental perspective. Also a T-S diagram will have to be formed with defined thermodynamic states. Performing the following calculations will the steady state values. Qin = m (h2 h1) - Heat addition from the boiler process Wt = m (h3 h4) Work rate of the turbine P = IV The Power that is generated Qout = m (h4 h1) The Heat rejection out of the system at the condenser

14 Temperature(⁰C) DISCUSSION PAGE 7 ncondenser = (condensate collected)/(refill water) Condenser efficiency nsystem = P/(energy of Propane) Total efficiency of the system (electrical power output verses the fossil fuel input) Energy input of propane = (l/minfuelflow)*(m^3 /1000l)*(J/m^3 for propane)*(min./60sec) J Where ; = m 3 forpropane 1 And ; m = (refill water ml )/(run time min. ) ( ) ( m3 ) (min. 1 ) 1000ml 1000l 60s (1000kg m 3 ) EXPERIMENTAL RESULTS As follows are predeveloped and concluded experimental results that have been performed and conducted with the outline given in the EXPERIMENTAL PROCEDURE section on page while referencing (LAKEHEAD UNIVERSITY LAB MANUAL MECHANICAL ENGINEERING ENGI-3555). Time Vs Boiler Temperature (⁰C) 4.00E E E E E+00 10:12:00 10:19:12 10:26:24 10:33:36 10:40:48 10:48:00 10:55:12 Time (am) Figure 4 Figure 3 shows the behavior of the boiler temperature with respect to time. SSSF is reached with a corresponding temperature of 306 ⁰C and an elapsed approximate time of 31 minutes to reach SSSF.

15 DISCUSSION PAGE 7 Table 2 Thermodynamic State Pressure kpa Temperature (⁰C) Enthalpy (kj/kg) Entropy (kj/kg ⁰K) Table 2 displays the thermodynamic steady state properties for the Rankine cycle on the Rankine Cycler Apparatus. Recall table 1 on page List the performance indicators and results for the Rankine Cycle on the Rankine Cycle Apparatus. Sources of error Not Steady State Hasn t Plateued at 350 ⁰C The condenser efficicency is important because of economics and environmental concerns. Economics because of the financial raise of dollars per unit of volume of water that is required to operate the Heat Engine which ultimately raises the pumping costs respectfully. Economics, because the level of fresh water could decrease which can have negative impacts on our indigenous ecosystem, as well as the steam contributions to therm pollution and exhaust of fossils fuels. SAMPLE CALCULATIONS Figure 5

16 DISCUSSION PAGE 7 The T-S diagram is attached in the appendix that has the relevant original design thermodynamic state properties under the original relevant thermodynamic processes. Analytically Summarizing Data Table 3 Quantity Value Q in = m ((h2 h1) + (h5 h4)) kw Wt = m ((h3 h4) + (h5 h6)) kw Power generated = ( ngenerated ) Wt W ngenerated = Power generated/wt % Qout = m (h6 h1) kw ncondenser = condensate collected /refillwater % Energy input of propane W nsystem overall = ((Power generated)/ (Energy Input of Propane))* %

17 Tabulated in table 3 are the values resulting from the redesign modification on the Rankine Cycler Apparatus at Lakehead University. Where the overall heat addition is kw, The Power output from the turbines are 1.317, the power generated is W, the efficiency of the power generated is 0.360%, the heat rejected is 8.319kW, the condenser efficiency is 14.78%, the energy output of propane is W, and the overall efficiency of the system is %. Table 4 Quantity Original Design Modified Design Relative Diff % Q in kw kw 8.07% Wt kw kw 72.59% Power generated 1.37 W W 71.11% ngenerated % % - Qout kw kw -5.99% ncondenser % % - Energy input of Propane W W - nsystem overall % % %

18 Table 4 represents the quantity of interest relative to the original design, the modified design and the relative difference in percentage. Note that the relative percentage difference for the heat addition in rate form is 8.07% increase, the work output in rate form from the combined turbines is 72.59% increase, The Power generated is increased by %, the quantity of heat rejected in rate form is decreased by a relative percentage of 5.99%. The overall efficiency of the system has been approved by 71.11%. ORIGINAL DESIGN Vs MODIFIED DESIGN Q in kw Wt kw Power generated W ngenerated % Original Design Qout kw ncondenser % Modified Design Energy input of Propanek W nsystem overall % Figure 6 Figure 5 is a visual representation of the original design in blue and the modified design in red. Notice how the generator efficiency remains constant, the condenser efficiency remains constant, and the energy input of propane remains constant. The relative difference for each performance quantity has been computed and noted under table 4

19 this is based on the assumptions that have been made listed on page 5 of the limitations/assumption section in the discussion branch of this formal report. Table 5 Thermodynamic State Pressure kpa Temperature (⁰C) Enthalpy (kj/kg) Entropy (kj/kg K) Table 5 represents the thermodynamic state properties that have been obtained through property tables in the appendix of... The additional thermodynamic state 5 and state 6 have are present based on the reheating modification to the Rankine Cycler Apparatus relative to the original design where the thermodynamic state properties are represented in table2. The corresponding processes have been identified and the calculations have been conducted to obtain the performance indicators in the talking section of the discussion branch of this formal report. These thermodynamic states and the corresponding thermodynamic state properties are aligned with the schematic attached.

20 CONCLUSIONS With the raw data from the experimental procedure, the calculations that followed, the assumptions made, the limitations recognized an appropriate design enhancement technique has been applied resulting in the success of the improvement of the output performance indicators of interest. As a result the heat addition has raised to kw with a percentage increase of 8.07 %, the work out put has been raised to kw with a percentage increase of 72.59%, The power generated has raised to W (with a constant current of 0.25 A the voltage has raised to V), The heat rejection has been reduced to kw with a percentage decrease of 5.99%, the overall system efficiency has been increased to % with a percentage increase of 71.11%.

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22 The Engineering applied science methods for increasing performance indicators of the Rankine Cycle in general have been discussed in detail. Various effects as a result making adjustments to the generalized Rankine cycle have been listed in bullet format in the background section of this report the effects of lowering the condenser pressure, the effects of superheating the steam to a high pressure, and the effects of increasing the boiler pressure have been examined. The output performance indicators such as heat addition given in units of kilo Watts, Work output given in units of Kilo Watts, The Power generated given in units of Watts, The heat rejected given in units of kilo Watts, and the system overall efficiency given as a percentage have been identified as quantities of interest for improvement. With the raw data from the experimental procedure, the calculations that followed, the assumptions made, the limitations recognized appropriate design enhancement techniques have been applied. The design enhancement techniques of improving the Rankine Cycler Apparatus that have been applied have made a significant overall improvement. More specifically these improvements are an 8.07% increase in the heat addition, a % increase in work output, a % increase in power generation a decrease in 5.99 % heat rejection and an overall system efficiency of 71.11%.

23 Recommendations page 9 The calculations provided meet the requirements and are a communicative form of recommendations.

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25 APPENDIX PAGE11 APPENDIX B

26 DOCUMENTATION PAGE 12 BACKGROUND Cengel, A.Yunus.,& Boles,A.Michael.(2011). THERMODYNAMICS An Engineering Approach (SI Units).New Delhi, Tata Mcgraw Hill Education Private Limited

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