DOCSLIB.ORG

Table 3. Compressed Water and Superheated Steam

Total Page：16

File Type：pdf, Size：1020Kb

Download full-text PDF Read full-text
Table 3. Compressed Water and Superheated Steam Table 3. Compressed Water and Superheated Steam 0.01 MPa (ts = 45.806 °C) 0.02 MPa (ts = 60.058 °C) 0.03 MPa (ts = 69.095 °C) v ρ h s t, °C v ρ h s t, °C v ρ h s 1.010 27 989.83 191.81 0.649 20 ts(L) 1.017 16 983.13 251.42 0.832 02 ts(L) 1.022 24 978.25 289.27 0.944 07 14 670. 0.068 166 2583.9 8.1488 ts(V) 7648.0 0.130 75 2608.9 7.9072 ts(V) 5228.4 0.191 26 2624.5 7.7675 *1.000 20 999.80 -0.03 -0.000 15 0 1.000 20 999.80 -0.02 -0.000 15 0 1.000 19 999.81 -0.01 -0.000 15 1.000 08 999.92 21.03 0.076 25 5 1.000 07 999.93 21.04 0.076 25 5 1.000 07 999.93 21.05 0.076 25 1.000 34 999.66 42.03 0.151 09 10 1.000 34 999.66 42.04 0.151 08 10 1.000 33 999.67 42.05 0.151 08 1.000 94 999.06 62.99 0.224 46 15 1.000 94 999.06 63.00 0.224 46 15 1.000 93 999.07 63.01 0.224 46 1.001 84 998.17 83.92 0.296 48 20 1.001 83 998.17 83.93 0.296 48 20 1.001 83 998.17 83.94 0.296 48 1.003 00 997.01 104.84 0.367 22 25 1.003 00 997.01 104.84 0.367 22 25 1.002 99 997.02 104.85 0.367 22 1.004 41 995.61 125.74 0.436 75 30 1.004 41 995.61 125.75 0.436 75 30 1.004 40 995.62 125.76 0.436 75 1.006 04 993.99 146.64 0.505 13 35 1.006 04 994.00 146.65 0.505 13 35 1.006 03 994.00 146.66 0.505 12 1.007 89 992.18 167.54 0.572 40 40 1.007 88 992.18 167.54 0.572 40 40 1.007 88 992.19 167.55 0.572 39 1.009 92 990.17 188.44 0.638 61 45 1.009 92 990.18 188.44 0.638 61 45 1.009 92 990.18 188.45 0.638 61 14 867. 0.067 263 2592.0 8.1741 50 1.012 15 988.00 209.35 0.703 81 50 1.012 14 988.00 209.36 0.703 80 15 101. 0.066 220 2601.6 8.2036 55 1.014 55 985.66 230.26 0.768 02 55 1.014 55 985.66 230.27 0.768 02 15 335. 0.065 211 2611.2 8.2326 60 1.017 13 983.16 251.18 0.831 29 60 1.017 12 983.16 251.19 0.831 29 15 568. 0.064 233 2620.7 8.2611 65 7764.8 0.128 79 2618.6 7.9360 65 1.019 87 980.52 272.12 0.893 65 15 801. 0.063 285 2630.3 8.2891 70 7882.6 0.126 86 2628.3 7.9646 70 5242.8 0.190 74 2626.3 7.7727 16 034. 0.062 366 2639.8 8.3167 75 8000.2 0.125 00 2638.0 7.9927 75 5322.0 0.187 90 2636.2 7.8013 16 267. 0.061 474 2649.3 8.3439 80 8117.6 0.123 19 2647.7 8.0202 80 5401.0 0.185 15 2646.0 7.8292 16 500. 0.060 607 2658.9 8.3707 85 8234.8 0.121 44 2657.4 8.0474 85 5479.7 0.182 49 2655.8 7.8567 16 732. 0.059 766 2668.4 8.3971 90 8351.8 0.119 73 2667.0 8.0741 90 5558.3 0.179 91 2665.5 7.8837 16 964. 0.058 947 2677.9 8.4232 95 8468.7 0.118 08 2676.6 8.1004 95 5636.8 0.177 41 2675.3 7.9103 17 196. 0.058 152 2687.5 8.4489 100 8585.5 0.116 48 2686.2 8.1263 100 5715.1 0.174 97 2685.0 7.9365 17 428. 0.057 378 2697.0 8.4742 105 8702.2 0.114 91 2695.8 8.1519 105 5793.3 0.172 61 2694.7 7.9623 17 660. 0.056 624 2706.5 8.4993 110 8818.7 0.113 40 2705.4 8.1771 110 5871.4 0.170 32 2704.3 7.9877 17 892. 0.055 890 2716.1 8.5240 115 8935.2 0.111 92 2715.0 8.2020 115 5949.5 0.168 08 2714.0 8.0128 18 124. 0.055 176 2725.6 8.5484 120 9051.6 0.110 48 2724.6 8.2266 120 6027.4 0.165 91 2723.7 8.0375 18 356. 0.054 479 2735.2 8.5726 125 9167.9 0.109 08 2734.2 8.2509 125 6105.3 0.163 79 2733.3 8.0620 18 587. 0.053 800 2744.7 8.5964 130 9284.1 0.107 71 2743.9 8.2749 130 6183.0 0.161 73 2743.0 8.0861 18 819. 0.053 138 2754.3 8.6200 135 9400.3 0.106 38 2753.5 8.2986 135 6260.8 0.159 72 2752.6 8.1099 19 050. 0.052 493 2763.9 8.6434 140 9516.4 0.105 08 2763.1 8.3220 140 6338.5 0.157 77 2762.3 8.1334 19 282. 0.051 863 2773.4 8.6664 145 9632.5 0.103 81 2772.7 8.3451 145 6416.1 0.155 86 2772.0 8.1566 19 513. 0.051 247 2783.0 8.6892 150 9748.6 0.102 58 2782.3 8.3680 150 6493.7 0.154 00 2781.6 8.1796 19 745. 0.050 647 2792.6 8.7118 155 9864.6 0.101 37 2792.0 8.3907 155 6571.2 0.152 18 2791.3 8.2023 19 976. 0.050 060 2802.3 8.7341 160 9980.5 0.100 20 2801.6 8.4131 160 6648.7 0.150 40 2801.0 8.2248 20 207. 0.049 487 2811.9 8.7562 165 10 096. 0.099 045 2811.3 8.4352 165 6726.2 0.148 67 2810.7 8.2470 20 438. 0.048 927 2821.5 8.7781 170 10 212. 0.097 921 2820.9 8.4572 170 6803.6 0.146 98 2820.4 8.2690 20 670. 0.048 380 2831.2 8.7997 175 10 328. 0.096 822 2830.6 8.4789 175 6881.1 0.145 33 2830.1 8.2908 20 901. 0.047 845 2840.8 8.8212 180 10 444. 0.095 748 2840.3 8.5004 180 6958.4 0.143 71 2839.8 8.3123 21 132. 0.047 321 2850.5 8.8424 185 10 560. 0.094 698 2850.0 8.5216 185 7035.8 0.142 13 2849.5 8.3337 21 363. 0.046 809 2860.2 8.8634 190 10 676. 0.093 671 2859.7 8.5427 190 7113.1 0.140 58 2859.2 8.3548 21 594. 0.046 308 2869.9 8.8843 195 10 791. 0.092 666 2869.4 8.5636 195 7190.5 0.139 07 2868.9 8.3757 21 826. 0.045 818 2879.6 8.9049 200 10 907. 0.091 682 2879.1 8.5843 200 7267.7 0.137 59 2878.7 8.3964 22 288. 0.044 868 2899.1 8.9456 210 11 139. 0.089 777 2898.6 8.6250 210 7422.3 0.134 73 2898.2 8.4372 22 750. 0.043 956 2918.6 8.9856 220 11 370. 0.087 950 2918.2 8.6651 220 7576.8 0.131 98 2917.8 8.4773 23 212. 0.043 081 2938.1 9.0248 230 11 601. 0.086 197 2937.8 8.7044 230 7731.2 0.129 35 2937.4 8.5167 23 674. 0.042 240 2957.8 9.0635 240 11 833. 0.084 512 2957.4 8.7431 240 7885.5 0.126 81 2957.1 8.5554 24 136. 0.041 432 2977.4 9.1015 250 12 064. 0.082 892 2977.1 8.7811 250 8039.9 0.124 38 2976.8 8.5935 24 598. 0.040 654 2997.2 9.1388 260 12 295. 0.081 333 2996.9 8.8185 260 8194.1 0.122 04 2996.6 8.6309 25 060. 0.039 904 3017.0 9.1756 270 12 526. 0.079 832 3016.7 8.8553 270 8348.4 0.119 78 3016.4 8.6678 25 522. 0.039 182 3036.8 9.2118 280 12 757. 0.078 386 3036.6 8.8916 280 8502.6 0.117 61 3036.3 8.7041 25 984. 0.038 486 3056.8 9.2475 290 12 989. 0.076 991 3056.5 8.9273 290 8656.8 0.115 52 3056.2 8.7398 *Values in italics indicate points where the thermodynamic equilibrium state would be a solid; the computed values are for the metastable liquid.
Load more

Recommended publications
  • Advanced Organic Vapor Cycles for Improving Thermal Conversion Efficiency in Renewable Energy Systems by Tony Ho a Dissertation
    Advanced Organic Vapor Cycles for Improving Thermal Conversion Efficiency in Renewable Energy Systems By Tony Ho A dissertation submitted in partial satisfaction of the requirements for the degree of Doctor of Philosophy in Engineering – Mechanical Engineering in the Graduate Division of the University of California, Berkeley Committee in charge: Professor Ralph Greif, Co-Chair Professor Samuel S. Mao, Co-Chair Professor Van P. Carey Professor Per F. Peterson Spring 2012 Abstract Advanced Organic Vapor Cycles for Improving Thermal Conversion Efficiency in Renewable Energy Systems by Tony Ho Doctor of Philosophy in Mechanical Engineering University of California, Berkeley Professor Ralph Greif, Co-Chair Professor Samuel S. Mao, Co-Chair The Organic Flash Cycle (OFC) is proposed as a vapor power cycle that could potentially increase power generation and improve the utilization efficiency of renewable energy and waste heat recovery systems. A brief review of current advanced vapor power cycles including the Organic Rankine Cycle (ORC), the zeotropic Rankine cycle, the Kalina cycle, the transcritical cycle, and the trilateral flash cycle is presented. The premise and motivation for the OFC concept is that essentially by improving temperature matching to the energy reservoir stream during heat addition to the power cycle, less irreversibilities are generated and more power can be produced from a given finite thermal energy reservoir. In this study, modern equations of state explicit in Helmholtz energy such as the BACKONE equations, multi-parameter Span- Wagner equations, and the equations compiled in NIST REFPROP 8.0 were used to accurately determine thermodynamic property data for the working fluids considered. Though these equations of state tend to be significantly more complex than cubic equations both in form and computational schemes, modern Helmholtz equations provide much higher accuracy in the high pressure regions, liquid regions, and two-phase regions and also can be extended to accurately describe complex polar fluids.
    [Show full text]
  • Thermodynamic Data
    Thermodynamic Data It is not possible to know the absolute value of U ˆ or H ˆ for a pure substance, but you can determine the change in U ˆ ( U ˆ ) or Hˆ ( Hˆ ) corresponding to a specified change of state (temperature, pressure, and phase). The change is actually often what we want to know. A common practice is to arbitrarily designate a reference state for a substance at which U ˆ and H ˆ are arbitrarily set to be equal to zero, and then tabulate U ˆ and/or H ˆ for the substance relative to the reference state. For example, ˆ CO (g, 0C, 1 atm) CO (g,100C, 1 atm): HCO 2919 J/mol ˆ ˆ reference state HCO HCO 0 2919 J/mol We say: “The specific enthalpy of CO at 100C and 1 atm relative to CO at 0C and 1 atm is 2919 J/mol”. CHEE 221 1 Reference States and State Properties Most (all?) enthalpy tables report the reference states (T, P and State) on which the values of H ˆ are based; however, it is not necessary to know the reference state to calculate H (change in enthalpy) for the transition from one state to another. ˆ ˆ –H from state 1 to state 2 equals H 2 H 1 regardless of the reference state upon which ˆ and ˆ were based H1 H 2 – Caution: If you use different tables, you must make sure they have the same reference state This result is a consequence of the fact that H ˆ (and U ˆ ) are state properties, that is, their values depend only on the state of the species (temperature, pressure, state) and not on how the species reached its state.
    [Show full text]
  • Backpressure Steam Power Generation in District Energy and CHP - Energy Efficiency Considerations
    Backpressure Steam Power Generation in District Energy and CHP - Energy Efficiency Considerations A 1st Law, 2nd Law and Economic Analysis of the Practical Steam Engine in a District Energy/CHP Application Joshua A. Tolbert, Ph.D. Practical Steam Energy Efficiency Engineering – How is efficiency calculated? • What is the Status Quo? – Engineers currently focus on limiting energy losses as the primary point of focus for district energy and CHP systems – Only local energy losses are typically considered causing energy efficiency opportunities to be wasted • Why? – Conventional wisdom tells us that minimizing local energy losses is ultimate goal • How should we change? – Could a different approach improve global efficiency? Motivation Common Questions: 1. How can installing an imperfect device in parallel to an isenthalpic pressure reducing valve (PRV) improve efficiency? 2. My analysis shows an incremental fuel cost with PRV parallel, how can this be more efficient? Analysis Overview • Consider a Practical Steam Engine (PSE) in a Pressure Reducing Valve (PRV) parallel district energy application • PSE operation is consistent with CHP application • Consider 1st Law, 2nd Law and economic analysis for energy efficiency • Draw conclusions Backpressure Application – Case Study Enwave Seattle - District Energy / CHP Application Assumptions Equipment • 1.5 MW (5.118 MMBtu/hr) • Practical Steam Engine (PSE) heating load is considered o Isentropic efficiency of 80% • Condensate exiting load: o Mechanical efficiency of 80% Saturate liquid at 20 psig o Generator efficiency of 95% • No heat losses in piping or • Isenthalpic PRV equipment* • 150 psig saturated steam boiler • 80% boiler and feedwater pump efficiency *Incorporating actual heat losses does not significantly affect results of analysis.
    [Show full text]
  • Superheated Steam in Locomotive Service
    I LL INO I S UNIVERSITY OF ILLINOIS AT URBANA-CHAMPAIGN PRODUCTION NOTE University of Illinois at Urbana-Champaign Library Large-scale Digitization Project, 2007. 0 ~0' / ~ ( ~ 1~CC~& '~f~LW "0~ "N ~ ~- ~N~TV N Q SC 2"' C' ''~~C'~ C" 4 AA.A..~ Ay ~4.A A A'-' 'A ' ~ ' ,~A~A 1 A' 'A": "I ~' ~A 9 ~AA >' 0 -A.'-- ~ A" Z 'A A' * A -A "* K~ A. A' ~. 'A A, ,~, 'U",' 4 *, A' '~'" 'A * JA A' 'A' A A K 'A 'A / A A A' 'A vas,^esta>bflibea~ ~ by ^f'A A' A ,rt~7B A 'A on, investigations~ve~Wg~on.~. A' ~ 'i* *t~.,to studysti~dy~ prob1~m~problems A sS ~4 IOAWeto eadA manu-m&i~n- 'be industrial interests 'A' of theb8tat;' -'$a te' The control of tho Engineering ExperintSerment• 'titionSl i•is is'vested vested 'A UNIVERSITY OF ILLINOIS ENGINEERING EXPERIMENT STATION BULLETIN No. 57 APRIL 1912 SUPERHEATED STEAM IN LOCOMOTIVE SERVICE (A REVIEW OF PUBLICATION NO. 127 OF THE CARNEGIE INSTITUTION OF WASHINGTON) BY W. F. M. GOSS DEAN OF THE COLLEGE OF ENGINEERING DIRECTOR OF THE ENGINEERING EXPERIMENT STATION DIRECTOR OF THE SCHOOL OF RAILWAY ENGINEERING AND ADMINISTRATION CONTENTS PAGE I. Introduction-A Summary of Conclusions .......... 3 II. Foreign Practice in the Use of Superheated Steam in Locomotive Service.............. ......... 5 III. Tests to Determine the Value of Superheating in Lo- comotive Service................ .. .. .... 14 IV. Performance of Boiler and Superheater.. ........... 20 V. Performance of the Engine and of the Locomotive as a W hole... ............ .. .. ........ 35 VI. Economy Resulting from the Use of Superheated Steam ...........
    [Show full text]
  • Improve Performance and Efficiency of the Steam Power Plant
    First Scientific Conference on Petroleum Resources and Manufacturing 27-28 October 2010 Brega, Libya Improve Performance and Efficiency of the Steam Power Plant Hesham G. Ibrahim1, Aly Y. Okasha2 and Ahmed G. Elkhalidy3 1Chemical Engineering Department, Faculty of Engineering, Misurata University, Al-Khoms City, Libya. Tel.: ++218-338-9965, e-mail: [email protected] 2Environmental Department, Faculty of Science, Misurata University, Al-Khoms City, Libya Tel.:++218-91-344-6102, e-mail: [email protected] 3Life Tech. Company, Manchester City, UK ABSTRACT Power plants generate electrical power by using fuels like coal, oil or natural gas. Fuel burned in the boiler to heats water to generate steam. The steam is then heated to a superheated state in the superheater. This superheated steam is used to rotate the turbine which powers the generator. Electrical energy is generated when the generator windings rotate in a strong magnetic field. After the steam leaves the turbine it is cooled to its liquid state in the condenser. The liquid is pressurized by the pump prior to going back to the boiler. This simple power plant is called (steam power plant). This cycle has a problem represent through a steam leaves the turbine, it is typically wet. The presence of water causes erosion of the turbine blades at high speed, gradually decreasing the life of turbine blades and efficiency of the turbine. That's leading to damage of turbine then shut-off plant. So, a simulation process of steam power plant done using (Hysys v.3.2) to improve the performance of plant also increasing efficiency through prevent erosion occurs and decreasing heat loses by condenser.
    [Show full text]
  • Consider Installing High-Pressure Boilers with Backpressure Turbine-Generators
    Energy Tips – Steam Steam Tip Sheet #22 • September 2004 Industrial Technologies Program Background Consider Installing High-Pressure Boilers with The capital cost of a back- Backpressure Turbine-Generators pressure turbogenerator complete with electrical When specifying a new boiler, consider a high-pressure boiler with a backpressure switchgear varies from steam turbine-generator placed between the boiler and the steam distribution about $700/kW for a small network. A turbine-generator can often produce enough electricity to justify the system (50 kW) to less than capital cost of purchasing the higher-pressure boiler and the turbine-generator. $200/kW for a larger system (>2,000 kW). Installation Since boiler fuel usage per unit of steam production increases with boiler pressure, costs vary depending upon facilities often install boilers that produce steam at the lowest pressure consistent with piping and wiring runs, but end use and distribution requirements. typically average 75% of equipment costs. In the backpressure turbine configuration, the turbine does not consume steam. Instead, it simply reduces the pressure and energy content of steam that is subsequently exhausted into the process header. In essence, the turbo-generator Packaged or “off-the-shelf” serves the same steam function as a pressure-reducing valve (PRV)—it reduces steam backpressure turbogenerators pressure—but uses the pressure drop to produce highly valued electricity in addition are now available in ratings as to the low-pressure steam. Shaft power is produced when a nozzle directs jets of low as 50 kW. Backpressure high-pressure steam against the blades of the turbineʼs rotor. The rotor is attached to a turbogenerators should be shaft that is coupled to an electrical generator.
    [Show full text]
  • An Integrated Study of Flue Gas Flow and Superheating Process in Recovery Boiler Using Computational Fluid Dynamics and 1D-Process Modelling
    An Integrated Study of Flue Gas Flow and Superheating Process in Recovery Boiler using Computational Fluid Dynamics and 1D-Process Modelling Kunal Kumar Andritz Oy, Viljami Maakala Andritz Oy and Ville Vuorinen Aalto University ABSTRACT Superheaters are the last heat exchangers on the steam side in recovery boilers. They are typically made of expensive materials due to the high steam temperature and risks associated with ash-induced corrosion. Therefore, detailed knowledge about the steam properties and material temperature distribution is essential for improving the energy efficiency, cost efficiency and safety of recovery boilers. In this work, for the first time, a comprehensive 1D-process model (1D-PM) for superheated steam cycle is developed and linked with a full-scale 3D CFD (computational fluid dynamics) model of the superheater region flue gas flow. The results indicate that first; the geometries of headers and superheater platens affect platen-wise steam distribution. Second, the CFD solution of the 3D flue gas flow field and platen heat flux distribution coupled with the 1D-PM affect the generated superheated steam properties and material temperature distribution. These new observations clearly demonstrate the value of the present integrated CFD/1D-PM modelling approach. It is advantageous for trouble shooting, optimizing the performance of superheaters and selecting their design margins for the future. The developed integrated modelling approach could also be relevant for other large-scale energy production units such as biomass-fired boilers. 1 INTRODUCTION Recovery boilers are used to combust black liquor for chemical recovery and producing high-pressure superheated steam. The generated steam is utilized for self-sustainable pulp mill operations and electricity generation.
    [Show full text]
  • Thermodynamics
    ME 201 Thermodynamics ME 201 Thermodynamics Old Exam #2 Solutions Directions: Work all three (3) problems. The exam is open notes and open text book. All problems have equal weight. Problem 1 A rigid container holds 3 kg of air initially at 50°C. The air is stirred so that its pressure changes from 500 kPa to 2000 kPa. The heat transfer is 200 kJ. Determine the final temperature, the change in internal energy, and the work. Solution: Using our 1st law template, we carefully read the problem and enter the given information. System Type: Closed (container) Substance Type: Ideal Gas (air) Process Type: Isotropic (rigid) State 1: Fixed State 2: Not fixed Q = 200 kJ Wsh = ??? Wbnd = 0 Conservation of Mass: m1 = m2 Conservation of Energy: m1u2 - u1 = Q - Wsh State 1 State 2 T1 = 50C = 323 K T2 = 1292 K P1 = 500 kPa P2 = 2000 kPa 3 3 v1 = 0.1854 m /kg v2 = 0.1854 m /kg 3 3 V1 = 0.5562 m V2 = 0.5562 m u1 = 230.58 kJ/kg u2 = 1015.6 kJ/kg m1 = 3 kg m2 = 3 kg Bold values are calculated. Italicized values are from tables or ideal gas law. Approach: Use the air tables and ideal gas law to determine the properties for state 1. Use the mass to calculate V1. Use the isotropic condition to fix state 2, then use the tables to determine the properties. Finally, calculate the shaft work from the 1st law. From the air tables we find u1 = 230.58 kJ/kg From the ideal gas law we have RT1 (0.287 )(323) 3 v1 = 0.1854 m /kg P1 (500) 1 ME 201 Thermodynamics Then by definition 3 V1 mv 1 = (3)(0.1854) 0.5562 m Since our process is isotropic 3 V2 = V1 = 0.5562 m and 3 v2 = v1 = 0.1854 m /kg Solving for the state 2 temperature from the ideal gas law P v (2000 )(0.1854 ) T 1 1 = 1292 K 1 R (0.287 ) From the air tables we now find u2 = 1015.6 kJ/kg Solving for the shaft work form the 1st law Wsh = Q - m1 u 2 - u1 200 - (3)(1015.6 - 230.58) - 2155 kJ Problem 2 A desuperheater is an adiabatic mixing tank which produces saturated vapor from a superheated vapor by adding liquid.
    [Show full text]
  • Superheated Steam Temperature and Heat SCIENTIFIC
    Superheated Steam Temperature and Heat SCIENTIFIC Introduction Why is steam a greater skin-burning threat than boiling water? How much energy is contained in steam? This demonstra- tion will dramatically show the energy content of superheated steam. Concepts • Heat energy • Steam • Condensation Materials Water, 150 mL Meker burner Beaker, any size Rubber stopper with hole, #6 Boiling chips, 2 or 3 Sheets of paper, 2 × 2, 2 Crucible tongs Support stand and clamp Copper coil tubing Support ring or adjustable burner support block Erlenmeyer flask, 250-mL Thermometer (optional) Hot plate Towel Match stick Safety Precautions Superheated steam is very hot. Be sure students are not close to the demonstration apparatus and especially not in the “line of fire” of the jet stream. Hot water and steam will spurt out the open end of the copper tubing during the demonstration. Do not point the exhaust end of the copper coil tubing at anybody. Perform this demonstration on a table that is free of any items that should not get wet. Care should be taken when handling the Meker burner while heating the copper coil. Allow the copper tubing to cool completely before touching or disassembling the apparatus. Wear chemical splash goggles, heat-resistant gloves, and a chemical-resistant apron. Please review current Material Safety Data Sheets for additional safety, handling, and disposal information. Preparation (refer to Figure 1) 1. Carefully insert the bent end of the copper tubing into the hole of the #6 rubber stopper so that the end of the tubing is flush with the bottom of the stopper.
    [Show full text]
  • Carbon Dioxide Mixtures As Working Fluid for High-Temperature Heat Recovery: a Thermodynamic Comparison with Transcritical Organic Rankine Cycles
    energies Article Carbon Dioxide Mixtures as Working Fluid for High-Temperature Heat Recovery: A Thermodynamic Comparison with Transcritical Organic Rankine Cycles Abubakr Ayub 1 , Costante M. Invernizzi 1,* , Gioele Di Marcoberardino 1 , Paolo Iora 1 and Giampaolo Manzolini 2 1 Department of Mechanical and Industrial Engineering, University of Brescia, via Branze, 38, 25123 Brescia, Italy; [email protected] (A.A.); [email protected] (G.D.M.); [email protected] (P.I.) 2 Energy Department, Politecnico di Milano, 20156 Milan, Italy; [email protected] * Correspondence: [email protected]; Tel.: +39-030-3715-569 Received: 30 June 2020; Accepted: 24 July 2020; Published: 4 August 2020 Abstract: This study aims to provide a thermodynamic comparison between supercritical CO2 cycles and ORC cycles utilizing flue gases as waste heat source. Moreover, the possibility of using CO2 mixtures as working fluids in transcritical cycles to enhance the performance of the thermodynamic cycle is explored. ORCs operating with pure working fluids show higher cyclic thermal and total efficiencies compared to supercritical CO2 cycles; thus, they represent a better option for high-temperature waste heat recovery provided that the thermal stability at a higher temperature has been assessed. Based on the improved global thermodynamic performance and good thermal stability of R134a, CO2-R134a is investigated as an illustrative, promising working fluid mixture for transcritical power cycles. The results show that a total efficiency of 0.1476 is obtained for the CO2-R134a mixture (0.3 mole fraction of R134a) at a maximum cycle pressure of 200 bars, which is 15.86% higher than the supercritical carbon dioxide cycle efficiency of 0.1274, obtained at the comparatively high maximum pressure of 300 bars.
    [Show full text]
  • Consider Installing High-Pressure Boilers with Backpressure Turbine-Generators, Energy Tips: STEAM, Steam Tip Sheet #22 (Fact Sh
    ADVANCED MANUFACTURING OFFICE Energy Tips: STEAM Steam Tip Sheet #22 Consider Installing High-Pressure Boilers with Backpressure Turbine-Generators Suggested Actions Consider installing a high-pressure When specifying a new boiler, consider a high-pressure boiler with a backpressure boiler with a back-pressure turbine- steam turbine-generator placed between the boiler and the steam distribution network. generator whenever undertaking a A turbine-generator can often produce enough electricity to justify the capital cost of boiler upgrade. When evaluating purchasing the higher-pressure boiler and the turbine-generator. this opportunity, you should: Since boiler fuel usage per unit of steam production increases with boiler pressure, facilities often install boilers that produce steam at the lowest pressure consistent with ■■ Determine how much steam end use and distribution requirements. enthalpy, pressure, and In the backpressure turbine configuration, the turbine does not consume steam. Instead, it temperature are required at the simply reduces the pressure and energy content of steam that is subsequently exhausted header downstream from your into the process header. In essence, the turbogenerator serves the same steam function as boiler. a pressure-reducing valve (PRV)—it reduces steam pressure—but uses the pressure drop to produce highly valued electricity in addition to the low-pressure steam. Shaft power ■■ Calculate the incremental fuel is produced when a nozzle directs jets of high-pressure steam against the blades of the cost between a low-pressure turbine’s rotor. The rotor is attached to a shaft that is coupled to an electrical generator. boiler and a high-pressure boiler. Background ■■ Develop steam flow/duration The capital cost of a back-pressure turbogenerator complete with electrical switchgear curves for your boiler.
    [Show full text]
  • Energy Effective and Green Drying Technologies with Industrial Applications , Chemical Engineering Transactions, 70, 145-150 DOI:10.3303/CET1870025 146
    145 A publication of CHEMICAL ENGINEERING TRANSACTIONS VOL. 70, 2018 The Italian Association of Chemical Engineering Online at www.aidic.it/cet Guest Editors: Timothy G. Walmsley, Petar S. Varbanov, Rongxin Su, Jiří J. Klemeš Copyright © 2018, AIDIC Servizi S.r.l. ISBN 978-88-95608-67-9; ISSN 2283-9216 DOI: 10.3303/CET1870025 Energy Effective and Green Drying Technologies with Industrial Applications Odilio Alves-Filho Norwegian University of Science and Technology, Department of Energy and Process Engineering, Kolbjørn Hejes vei 1b, 7491 Trondheim, Norway [email protected] Heat pump drying is a green technology with zero global warming potential and zero ozone depletion potential when operating with natural fluids. A well designed heat pump dryer can be several times more energy efficient and less costly than conventional dryers. This dryer beneficially contributes to a sustainable society while providing superior products at competitive cost. It is an advanced engineered drying technology ready for implementation by modern industries wishing a return of investment while contributing to a sustainable society. This paper covers the advances in heat pump and superheated steam drying technologies. These drying processes are in the category of green technologies because they are highly effective and advantageous for the environment and climate change. Descriptions and layouts are given covering design of heat pump and steam dryers. Details are provided in their beneficial operation in single and multistage with vapor compression and drying chambers placed in series. The drying modes covered are atmospheric sublimation and evaporation for improved capacity and superior characteristics of dried materials. The future trend is heat pump drying with natural fluids and superheated steam drying complying with proper industrial practice and with regulations reducing damage to sea, soil and water as well as zeroing contribution to global warming and to climate change.
    [Show full text]