Sco2 Recuperators Application Notes and Testing Issues

Total Page:16

File Type:pdf, Size:1020Kb

Sco2 Recuperators Application Notes and Testing Issues sCO2 Recuperators Application Notes and Testing Issues Echogen Power Systems Timothy J. Held, CTO sCO2 Power Cycles . Competitor to steam cycles . Offer advantages in efficiency, footprint, simplicity and water- free operation . Flexible power cycle . Nuclear, CSP, primary power applications . Waste heat recovery / combined cycle applications . Echogen’s strategy: Start with WHR/CC for near-term market availability, branch to other areas from there Echogen Power Systems 2 Echogen Background 2007 Echogen founded 2011 Partnership with Dresser-Rand (now Siemens) for oil & gas market; development of EPS100 7.5 MW engine begins 2013 Partnership with GE Marine; development of Akron, OH EPS30 1.35 MW engine begins 2014 EPS100 completes factory testing Echogen Power Systems is the 2016 EPS30 testing commences with high-speed industry leader in development alternator subsystem test of supercritical CO heat recovery 2 2018 Started energy storage project with ARPA-E systems. DAYS funding, developing 10MW primary Founded in 2007, EPS has power project progressed from small multi-kW 2019 First EPS100 commercial announcement demonstration units to the recent multi-MW heat recovery package, the EPS100. Echogen Power Systems Echogen EPS100 EPS100 process skid EPS100 power skid • 7.5 MWe net power output • Gas turbine combined cycle application (22 MWe target application) • Successfully completed factory testing • First commercial sale to TransCanada (through Siemens licensee) Echogen Power Systems Foreshadowing… . Recuperators have a significant impact on sCO2 power cycle performance and cost . Understanding the sCO2 application… counterflow, high effectiveness, Cr=1 . Materials issues: Strength at temperature, creep-rupture life, cyclic operation impacts on life, CO2 corrosion compatibility, non-CO2 corrosion compatibility . Importance of developing cost models (and our preferred form) . Testing of high-temperature recuperators Echogen Power Systems 5 100 Recompression Cycle recuperators 100 Recycled Heat source PHX 10 Low-temp recuperator High-temp recuperator Primary heat exchanger HTT HTR 10 HTC Cooler Low-temp High-temp LTR recuperator recuperator 1 100 300 500 700 900 1100 1300 LTC Recuperator inlet temperature ~ 150°C lower than turbine inlet temperature QRX Turbine inlet temperature limited by primary heat exchanger materials to ~700-730°C 1 Echogen Power Systems 6 100 300 500 700 900 1100 1300 Waste Heat Recovery architecture example PHX2 PHX1 100 Once-through Heat source Primary heat exchanger Recuperator Turbine 10 Recuperator Recuperator Pressure(MPa) Compr 1 100 200 300 400 500 600 700 800 900 1000 Enthalpy (kJ/kg) ACC WHR applications tend to be lower temperature (< 550°C) due to nature of heat sources Cycle design emphasizes wide temperature range for heat extraction Echogen Power Systems 7 Glide-matching Recompression cycle . Cycle design always trends towards glide-matched heat exchangers (Cr=1) to minimize exergy destruction / maximize cycle efficiency . Drives design flow mismatch in low- temperature recuperator 3 P=8.5 MPa 2.5 P=30 MPa 2 1.5 [kJ/(kg·K)] p c 1 0.5 0 0 100 200 300 400 500 600 700 800 Temperature (°C) Echogen Power Systems 8 Allam cycle recuperator Fuel + O2 100 Burner Turbine Recuperator Combustor H2O Recuperator Cooler CO2 10 Compr Pump Pressure(MPa) Intercooler Recuperator Compr 1 0 250 500 750 1000 1250 1500 1750 2000 Enthalpy (kJ/kg) Intercooler Turbine inlet temperature limited by recuperator inlet temp (750°C today) Echogen Power Systems 9 Extra challenges with the Allam cycle • Composition is more complex than pure CO2 • Water ~ 7% (molar) • Inert carryover from gas (primarily N2) • Trace materials, like sulfur, minor issue with natural gas, huge issue with coal-derived syngas • Composition changes rapidly between oxidizing and reducing over a very narrow equivalence ratio range • Not sure whether NetPower is biasing their control system on the rich or lean side Echogen Power Systems 10 Balancing cost and performance . Techno-Economic Optimization major part of Echogen’s focus . Requires coupled models of component performance and cost . Mostly means heat exchangers! . Turbomachinery efficiency is critical, but largely insensitive to investment cost Echogen Power Systems 11 Cycle implications on recuperator design . Design pressure is toward high effectiveness with Cr → 1.0 푈퐴 휀 휀 = or 푈퐴 = 퐶푚푛 퐶푚푖푛+푈퐴 1−휀 . Cycle performance is strongly influenced by recuperator performance . System cost is strongly influenced by heat exchanger cost . Recuperators typically 10-30% of equipment cost . Other heat exchangers comparable Echogen Power Systems 12 Representing heat exchanger cost . Until someone tells us otherwise, we represent heat exchanger cost as: Design study on WHR cycle Baseline: RC effectiveness = 95% 퐶 = 푓 푈퐴, ∆푝ℎ, ∆푝푐 ΔPh= ΔPl=0.1 MPa or in a slightly more detailed form UA-10% 퐶 = 퐴 + 퐵 푈퐴α · 푔 ∆푝 , ∆푝 ℎ 푐 UA+10% ΔPh x 2 Baseline High dP ΔPh / 2 Low dP ΔPl x 2 Cost ΔPl / 2 -1.0% -0.5% 0.0% 0.5% 1.0% 1.5% Impact on output power UA Echogen Power Systems 13 Other design issues . Don’t go nuts on passage size! . PCHEs have diameters ~ 1-3 mm . Less than that and we will have a serious plugging / filtration issue. CO2 systems are not that clean . Some applications are by nature cyclic (e.g. CSP) . Thought needs to be given to managing / designing / analyzing impact of thermal ramp rates . Less concerned about the core. Headers and connections usually the weak points . Non-counterflow features need to be evaluated for impact on limiting effectiveness (e.g. cross-flow in entry/exit regions) Echogen Power Systems 14 Testing high-temperature recuperators . Echogen is providing testing services for multiple HITEMMP awardees – open to others . Facility capable of 700°C, 20 MPa, 0.28 kg/s CO2 flow rate (demonstrated) . Inconel 740H heater . By moving heater to low-pressure side of system, can reach 800°C at 8 MPa Echogen Power Systems 15 Test facility for 800°C / 8 MPa Heater Heat input ~ 16 kW 674°C Designed for 60 kW 8.1 MPa Fixed 800°C orifice 8.0 MPa 680°C 24.5 MPa Recuperator design: 50 kWth 800°C / 8 MPa Test recuperator 300°C / 25 MPa Flow rate ε=80% 0.104 kg/s 300°C 408°C 25.1 MPa 7.8 MPa Recuperator ACC53°C (existing) 7.75 MPa 25°C 49°C 7.7 MPa 25.2 MPa Pump Echogen Power Systems 16 1100°C plan . No materials code-qualified to full pressure at > 800°C . Will need to encase final-stage heater and unit under test inside insulated pressure vessel Echogen Power Systems 17 1100°C / 8 MPa test conditions Heater 676°C . Lower effectiveness Heat input ~ 56 kW 8.1 MPa Designed for > 100 kW Fixed target increases Orifice 1100°C Recuperator design: heater duty 8.0 MPa 682°C 50 kWth 24.6 MPa requirements and 1100°C / 8 MPa 726°C 300°C / 25 MPa Test recuperator 7.8 MPa flow rate ε=50% . Dashed line = internal Test flow rate 300°C 0.104 kg/s 25.1 MPa to pressure vessel 324°C 7.8 MPa Low-T 53°C recuperator 7.75 MPa FCV 25°C 49°C 7.7 MPa Pump 25.2 MPa Echogen Power Systems 18 Other test issues . Test planning . Performance testing – steady-state evaluation of UA by inlet/outlet temperatures and pressures, CO2 flow rate at multiple operating conditions . Cyclic testing – Define min/max, number of cycles, duration . Practical issues . Fittings . Instrumentation Echogen Power Systems 19 How not to do fittings (and a potential better way) 1” fitting, 700°C, 25 MPa Inconel 740H Grayloc hubs Silver-plated Inconel 718 seal ring 347 clamp with HA230 studs/nuts $11.5K per connection 1” fitting Inconel 625 ~$1.5K Need to complete thermal and stress analysis at intended design conditions Preliminary scaling from room temperature design conditions to operating conditions favorable Echogen Power Systems 20 Instrumentation . External to heat exchanger – inlet/outlet pressures and temperatures, total flow rate . Pressure: Rosemount 3051 (±0.04% of span, ~ 0.1 bar) . Temperature: Type R special limit TC’s (±greater of 0.6°C or 0.1% of reading) . Flow: Micromotion CMF Coriolis mass flow meter (±0.25% of reading) . Can accommodate internal instrumentation, will be provider’s responsibility to provide Echogen Power Systems 21 Summary . Recuperators (and heat exchangers in general) are critical components of sCO2 power cycles . High temperatures mostly driven by Allam cycle today, but other applications may follow once limitations are moved . Cost vs. performance trades need good cost models . Test facility available for 800°C testing . 1100°C facility design and execution in very preliminary stages Echogen Power Systems 22 Thank you! Echogen Power Systems 23.
Recommended publications
  • Air Treatment and Residential HRV Technical Solutions for Integration Into Radiant Systems Rapid Selection of Heat Recuperators
    Radiant Systems Catalog • Price List GIACOMINI.COM 05/2019 ITALY ER0008 JUN2019 AIR TREATMENT AND HRV RESIDENTIAL AIR TREATMENT GIACOMINI S.P.A. VIA PER ALZO, 39 28017 SAN MAURIZIO D’OPAGLIO NOVARA ITALY Air Treatment and Residential HRV Technical solutions for integration into radiant systems Rapid selection of heat recuperators EXCHANGE AIR HOUSE TYPE OF HEAT RECUPERATOR FLOW RATE HEAT RECUPERATOR SURFACE LODGING WITH AIR TREATMENT CALCULATED* 2 3 Nominal Catalog Nominal Catalog m m /h Type flow rate Page Type flow rate Page KHRD-V 300/150 m3/h page 67 KHR-V 200 m3/h page 45 Studio flat, KHRD-H 300/150 m3/h page 73 up to 50 two-roomed flat, max 70 KHR-H 200 m3/h page 50 3 1 bathroom KHRW-V 300/150 m /h page 93 KHRA-H 80 m3/h page 113 KHRW-H 300/150 m3/h page 99 KHRD-V 300/150 m3/h page 67 50÷60 75 KHRD-H 300/150 m3/h page 73 KHR-V 200 m3/h page 45 60÷70 Living room, kitchen 90 KHRW-V 300/150 m3/h page 93 1-2-3 bedrooms KHR-H 200 m3/h page 50 3 70÷80 1-2 bathrooms 105 KHRW-H 300/150 m /h page 99 KHRA-H 140 m3/h page 113 80÷90 115 KHRW-H 600/150 m3/h page 99 KDV water cond 300/160 m3/h page 79 KHRD-V 500/250 m3/h page 67 90÷100 130 KHR-V 200 m3/h page 45 KHRD-H 500/250 m3/h page 73 100÷110 Living room, kitchen 145 2-3 bedrooms KHR-H 200 m3/h page 50 KHRW-V 500/250 m3/h page 93 110÷120 2 bathrooms 160 KHRA-H 200 m3/h page 113 KHRW-H 500/250 m3/h page 99 120÷130 170 KDV air cond 360/220 m3/h page 79 KHRD-V 500/250 m3/h page 67 120÷130 170 KHR-V 300 m3/h page 45 KHRD-H 500/250 m3/h page 73 130÷140 Living room, kitchen 185 2-3-4 bedrooms
    [Show full text]
  • A Lightweight, High-Effectiveness Recuperator for Next-Generation Airborne Cryocoolers
    A Lightweight, High-Effectiveness Recuperator for Next-Generation Airborne Cryocoolers A. Niblick, J. Cox, M. Zagarola Creare LLC, Hanover, NH, 03755 USA ABSTRACT Next-generation turboelectric aircraft aim to decouple power generation from propulsion by using gas turbines driving electric generators connected to electric propulsion motors. The power density requirements for these electric machines can only be achieved with superconductors, which in turn require lightweight, high-capacity cryocoolers. However, current cryocooler technologies offer cooling capacities that are too low and masses that are too high to meet projected aircraft needs. For turbo-Brayton cryocoolers, the recuperative heat exchanger historically has been the largest and most massive component, and offers the most potential for size and weight reduction. Improvements PD\EHDFKLHYHGWKURXJKWKHXVHRIVPDOOHUÀRZSDVVDJHVRUWKRWURSLFFRUHWKHUPDOUHVLVWDQFHWR GHFUHDVHUHVLVWDQFHEHWZHHQÀRZVWUHDPVZKLOHLQFUHDVLQJD[LDOUHVLVWDQFHIURPZDUPWRFROGHQGV and lighter-weight materials. To this end, a recuperator that implements all such improvements has been developed. The recuperator core consists of a stack of copper-polyimide plates. Miniature ÀRZIHDWXUHVDUHHWFKHGLQWRWKHFRSSHUWRSURYLGHWKHÀRZSDWKIRUWKHUHFXSHUDWHGJDVVWUHDP 7KHVPDOOÀRZIHDWXUHVHWFKHGLQWRWKHFRQGXFWLYHFRSSHUVXEVWUDWHSURPRWHKHDWWUDQVIHUUDGLDOO\ EHWZHHQÀRZVWUHDPVZKLOHWKHSRO\LPLGHDFWVDVDWKHUPDOUHVLVWRULQWKHD[LDOGLUHFWLRQ7KH ODPLQDWHVDUHERQGHGWRJHWKHU7KHUHVXOWLVDFRPSDFWPRQROLWKLFFRUHWKDWDFKLHYHVKLJKVSHFL¿F FRQGXFWDQFH7KLVQHZUHFXSHUDWRUWHFKQRORJ\¿OOVDYRLGEHWZHHQKLJKSHUIRUPDQFHOLJKWZHLJKW
    [Show full text]
  • Evaluation of Heat Transfer on Air Recuperator
    © 2018 JETIR September 2018, Volume 5, Issue 9 www.jetir.org (ISSN-2349-5162) EVALUATION OF HEAT TRANSFER ON AIR RECUPERATOR M. Padma1, P. S. Kishore2, K. Sudhakar3 G.Prasad4 M. E Student1, Professor (Ph. D)2, 푘. 푠푢푑ℎ푎푘푎푟3 퐷푒푝푎푟푡푚푒푛푡 표푓 푀푒푐ℎ푎푛푐푎푙 퐸푛푔푛푒푒푟푛푔12 퐴푛푑ℎ푟푎 푈푛푣푒푟푠푡푦12, Visakhapatnam - 530003, India 퐷푒푝푢푡푦 퐺푒푛푒푟푎푙 푀푎푛푎푔푒푟 (퐸푀퐷)3, 푅푎푠ℎ푡푟푦푎 퐼푠푝푎푡 푁푔푎푚 퐿푚푡푒푑3 Assisitant professor©, JNTU KAKINADA ABSTRACT-Industrial waste heat refers to energy that is flow rates of air and flue gas are consolidated as table and put in generated in industrial process without being put to practical use. appendix. It is estimated that somewhere between 20 to 50% industrial Key words: recuperator, volume flow rate, heat transfer energy input is lost as waste heat in the form of hot exhaust gases, cooling water, heat lost from hot equipment surface and heated coefficient , friction factor, pressure drop. products. While some waste heat losses from industrial processes I INTRODUCTION are inevitable. Facilities can reduce these losses by improving Air Recuperator: equipment efficiency or installing waste heat recovery technologies. The flue gases coming out of the furnace are sent through the air recuperator so that the excess heat energy from the flue In the steel making process, Rolling mills play a vital gases can be absorbed by the incoming air. The recuperator is role in transforming the steel to finished Products. Rolling mills at shell and tube type cross-flow heat exchanger. Waste gases which are to be circulated in the furnace in a direction opposite to that of Visakhapatnam Steel Plant consists of Light and medium bloom movement will be exhausted through the openings merchant mill (LMMM), Wire Rod Mills (WRM) and Medium provided at the charging end, after passing through the Merchant Structural Mills (MMSM).
    [Show full text]
  • Waste Heat Recovery Technology Assessment
    Quadrennial Technology Review 2015 Chapter 6: Innovating Clean Energy Technologies in Advanced Manufacturing Technology Assessments Additive Manufacturing Advanced Materials Manufacturing Advanced Sensors, Controls, Platforms and Modeling for Manufacturing Combined Heat and Power Systems Composite Materials Critical Materials Direct Thermal Energy Conversion Materials, Devices, and Systems Materials for Harsh Service Conditions Process Heating Process Intensification Roll-to-Roll Processing Sustainable Manufacturing - Flow of Materials through Industry Waste Heat Recovery Systems Wide Bandgap Semiconductors for Power Electronics U.S. DEPARTMENT OF ENERGY Quadrennial Technology Review 2015 Waste Heat Recovery Systems Chapter 6: Technology Assessments NOTE: This technology assessment is available as an appendix to the 2015 Quadrennial Technology Review (QTR). Waste Heat Recovery Systems is one of fourteen manufacturing-focused technology assessments prepared in support of Chapter 6: Innovating Clean Energy Technologies in Advanced Manufacturing. For context within the 2015 QTR, key connections between this technology assessment, other QTR technology chapters, and other Chapter 6 technology assessments are illustrated below. Representative Intra-Chapter Connections Representative Extra-Chapter Connections CHP: heat recovery in CHP systems Sustainable Manufacturing: optimization of heat flows to maximize production intensity and minimize waste heat losses Electric Power: waste heat recovery Direct Thermal Energy Conversion: novel energy
    [Show full text]
  • Diesel Engine Waste Heat Recovery System Comprehensive Optimization Based on System and Heat Exchanger Simulation
    Open Physics 2021; 19: 331–340 Research Article Da Li, Qiang Sun, Ke Sun*, Guodong Zhang, Shuzhan Bai*, and Guoxiang Li* Diesel engine waste heat recovery system comprehensive optimization based on system and heat exchanger simulation https://doi.org/10.1515/phys-2021-0039 received February 04, 2021; accepted May 11, 2021 Nomenclature Abstract: To further improve the thermal efficiency of E power output, kW diesel engines, a waste heat recovery system model uti- m mass flow rate, kg/s lizing organic Rankine cycle (ORC) is constructed and Q heat flux, kW verified through system bench test and heat exchanger h enthalpy, kJ/kg bench test. To recover waste heat from diesel engine η efficiency exhaust, ethanol, cyclopentane, cyclohexane, R1233zd out outlet (E), and R245fa were selected for comparison. The quality s heat source of heat source, the quality of evaporator, the system r working fluid output, and the system complicity were taken as vari- re recuperated ables for comparison. Analysis shows that for ORC sys- tems without recuperator, ethanol system has the best system output of the five in a wide operation temper range, with the highest exergy efficiency of 24.1%, yet the exergy Subscripts and superscripts efficiency increase after the application of recuperator, 9.0%, is limited. For low temperature exhaust, cyclopen- eva evaporator tane system has the best performance with or without exp expander recuperator, and the cyclopentane system with recup- in inlet erator has the best performance in terms of exergy effi- ciency, 27.6%, though complex heat exchangers are also required for high power output.
    [Show full text]
  • Compact Heat Exchangers for Microturbines
    Compact Heat Exchangers for Microturbines R.K. Shah Rochester Institute of Technology Dept. of Mechanical Engineering 76 Lomb Memorial Drive Rochester NY 14623-5604 USA [email protected] ABSTRACT With distributed power generation market, the most economical solution today is to generate power through small gas turbine systems, arbitrarily categorized as microturbines (5 – 200 kW) and miniturbines (200 – 500 kW). The thermal efficiency of such microturbines is about 20% or less if no recuperator is used in the system. Using a recuperator (regenerator can also be considered but has a number of problems) operating at 87% effectiveness, the efficiency of the gas turbine system increases to about 30%, a substantial performance improvement. However, cost of the recuperator is about 25 – 30% of the total power plant. This means that the heat exchanger (recuperator) must be designed to get high performance with minimum cost. While the offset strip fin geometry is one of the highest performing surface it is also quite expensive to manufacture. This necessitates the use of all prime surface heat exchangers with no brazing. In this paper, after providing the necessary concise information on microturbines, the discussion is presented on various types of heat exchanger surfaces and novel designs considered for the cost effective heat exchangers and packaging in the system. For hot fluid inlet temperature of less than about 675°C, stainless steel material can be used for the heat exchanger, which has reasonable cost. However, for higher inlet temperatures in heat exchangers associated with higher turbine inlet temperatures, superalloys are essential which increases the material cost of the exchanger alone by a factor of 4 to 5.
    [Show full text]
  • Design Point Performance and Optimization of Humid Air Turbine Power Plants
    applied sciences Article Design Point Performance and Optimization of Humid Air Turbine Power Plants Giovanni D. Brighenti *, Pau Lluis Orts-Gonzalez, Luis Sanchez-de-Leon and Pavlos K. Zachos Propulsion Engineering Centre, School of Aerospace, Transport and Manufacturing, Cranfield University, Cranfield, Bedfordshire MK43 0AL, UK; p.ortsgonzalez@cranfield.ac.uk (P.L.O.-G.); [email protected] (L.S.-d.-L.); p.zachos@cranfield.ac.uk (P.K.Z.) * Correspondence: g.d.brighenti@cranfield.ac.uk; Tel.: +44-0-1234-75-4633 Academic Editor: Antonio Ficarella Received: 30 January 2017; Accepted: 13 April 2017; Published: 20 April 2017 Abstract: With the recent drive towards higher thermal efficiencies and lower emission levels in the power generation market, advanced cycle power plants have become an increasingly appealing option. Among these systems, humid air turbines have been previously identified as promising candidates to deliver high efficiency and power output with notably low overall system volume, weight and emissions footprint. This paper investigates the performance of an advanced humid air turbine power cycle and aims to identify the dependencies between key cycle design variables, thermal performance, weight and cost by means of a parametric design optimization approach. Designs of the main heat exchangers are generated, aiming to ascertain the relationship between their technology level and the total weight and acquisition cost of them. The research outcomes show that the recuperator and the intercooler are the two components with the largest influence on the thermal efficiency and the total cost. The total weight of the power system is driven by the technology level of the recuperator and the economizer.
    [Show full text]
  • RECUPERATOR RGS with HMI Control Panel
    Szymański, Nowakowski General Partnership 31 Lubelska Str., 08-500 Ryki phone +48 81 883 56 00, fax +48 81 883 56 09 POLAND RECUPERATOR RGS with HMI control panel I. CONTACTS II. ORIGINAL INSTRUCTION MANUAL III. LIST OF COMPONENTS INSTALLED IN THE DEVICE IV. SAMPLE EC DECLARATION OF CONFORMITY V. WARRANTY TERMS VI. DEVICE COMMISSIONING REPORT VII. INSPECTION AND MAINTENANCE CHART VIII. SERVICE REQUEST IX. ADDITIONAL DOCUMENTS » Technical Data Sheet » Declaration of Conformity » List of Components Installed in the Device; » Specification of Automation Components; » List of Elements Attached to the Unit; Please read this instruction manual carefully before beginning any work. RYKI 2017 ISSUE 1 EN I. CONTACTS Szymański, Nowakowski General Partnership 31 Lubelska Str., 08-500 Ryki phone +48 81 883 56 00, fax +48 81 883 56 09 POLAND Export department mob.+48 502 087 841 mob.+48 664 465 243 [email protected] 2 www.juwent.com.pl II. ORIGINAL INSTRUCTION MANUAL RECUPERATOR RGS-1, -2, -3, -4, -5, -6, -7 www.juwent.com.pl 3 TABLE OF CONTENTS 1. INTRODUCTION 5 2. DEVICE DESIGNATION 5 3. INTENDED USE AND DESIGN 6 3.1. UNITS DIMENSIONS 6 3.2. SERVICE SIDES 9 4. HANDLING AND STORAGE 10 5. SITTING, MOUNTING AND CONNECTIONS 10 5.1. SITTING 10 5.2. SITTING LOCATION 11 5.3. CONNECTING VENTILATION DUCTS 11 5.4. CONNECTING HEATERS AND COOLERS 11 5.5. CONDENSATE DRAINAGE 11 5.6. ELECTRICAL CONNECTION 12 5.7. ELECTRIC HEATER 12 5.8. FAN MOTOR 12 5.9. AUTOMATIC EQUIPMENT 13 5.9.1. AUTOMATIC EQUIPMENT ELEMENTS 14 6.
    [Show full text]
  • Numerical Analysis of an Organic Rankine Cycle with Adjustable Working Fluid Composition, a Volumetric Expander and a Recuperator
    Article Numerical Analysis of an Organic Rankine Cycle with Adjustable Working Fluid Composition, a Volumetric Expander and a Recuperator Peter Collings and Zhibin Yu * School of Engineering, University of Glasgow, Glasgow G12 8QQ, UK; [email protected] * Correspondence: [email protected]; Tel.: +44-141-330-2530 Academic Editor: Andrew J. Haslam Received: 31 January 2017; Accepted: 22 March 2017; Published: 27 March 2017 Abstract: Conventional Organic Rankine Cycles (ORCs) using ambient air as their coolant cannot fully utilize the greater temperature differential available to them during the colder months. However, changing the working fluid composition so its boiling temperature matches the ambient temperature as it changes has been shown to have potential to increase year-round electricity generation. Previous research has assumed that the cycle pressure ratio is able to vary without a major loss in the isentropic efficiency of the turbine. This paper investigates if small scale ORC systems that normally use positive-displacement expanders with fixed expansion ratios could also benefit from this new concept. A numerical model was firstly established, based on which a comprehensive analysis was then conducted. The results showed that it can be applied to systems with positive-displacement expanders and improve their year-round electricity generation. However, such an improvement is less than that of the systems using turbine expanders with variable expansion ratios. Furthermore, such an improvement relies on heat recovery via the recuperator. This is because expanders with a fixed expansion ratio have a relatively constant pressure ratio between their inlet and outlet. The increase of pressure ratio between the evaporator and condenser by tuning the condensing temperature to match colder ambient condition in winter cannot be utilised by such expanders.
    [Show full text]
  • Evaporators for High Temperature Lift Vapor Compression Loop for Space Applications
    ProceedingsProceedings ofof thethe ASME2009 ASME 2009 HeatSummer Transfer Heat SummerTransfer ConferenceConference July 17-23, 2009, San Francisco, California,HT2009 USA July 19-23, 2009, San Francisco, California USA HT2009-88205 HT2009-88205 EVAPORATORS FOR HIGH TEMPERATURE LIFT VAPOR COMPRESSION LOOP FOR SPACE APPLICATIONS Tadej Semenic Xudong Tang Advanced Cooling Technologies, Inc. Advanced Cooling Technologies, Inc. Lancaster, Pennsylvania, USA Lancaster, Pennsylvania, USA ABSTRACT lunar surface with Altair Lunar Lander previously known as An Advanced Vapor Compression Loop (AVCL) for high Lunar Surface Access Module (LSAM). temperature lift for heat rejection to hot lunar surface during The objective of the thermal control systems (TCS) of the lunar daytime was developed. The loop consists of an Altair Lunar Lander is to maintain the cabin and electronics evaporator, a compressor, a condenser, and an electronic temperatures within acceptable levels anywhere on the lunar expansion valve. Different types of evaporators were evaluated surface during the hot lunar daytime. This is challenging in this study: a circular tube evaporator, a circular tube because the lunar surface temperature at the equator can range evaporator with a twisted tape, a circular tube evaporator with a from -173°C to 121°C [1-5]. wick, and a circular tube evaporator with a wick and a twisted The most effective heat rejection method is to radiate the tape. The evaporators were tested with two different heat to space. The temperature difference between the radiator compressors. The first was a 0.5hp oil-less compressor and the surface and the heat sink needs to be sufficiently large to ensure second was a 5.3hp compressor that used oil as lubricant.
    [Show full text]
  • Plate Heat Exchangers Introduction
    Plate heat exchangers Introduction Energy Saving. Condensation. Recuperator heat recovery units offer Plate-type exchangers do not allow for various possibilities for energy saving the passage of humidity from one flow and an alternative for reducing energy to another, but can transfer part of the costs and atmospheric pollution. latent heat contained in the wet exhaust air-flow; this happens Characteristics. especially when external temperatures Heat-exchangers are exchangers that are very low, so that the supply air enable heat to be transferred between cools the wet exhaust below its dew the input and the output air-flows based point and condensation is formed. on the difference in temperature. Recuperator offer two series of static plate exchangers (Series B and F) and a rotary exchanger series (Series T), whose characteristics meet the require- ments of both the industrial and the non-industrial markets. Reliability and High Performance. The plate type are air-to-air heat- exchangers that have no moving parts, offering very high reliability and performance; in addition, they make for low energy consumption in associated boiler equipment. The heat is transmitted directly from the higher to the lower temperature-flow; the air-flow pattern is of cross-flow design, and the exchanger's efficiency is between 40 and 75%. Sealing. This type of heat-exchanger consists of flat plates with swirl control, whose spacing depends on the type of application. The exhaust and supply air-flows are completely separated by means of special seals. Materials. The plates are usually made of aluminium, due to the latter's corrosion- resistance, ease of manufacture, non- inflammability, and durability.
    [Show full text]
  • Heat Exchangers for Industrial Heat Recovery
    ··--·----- --------------- A GUIDE TO HEAT EXCHANGERS FOR INDUSTRIAL HEAT RECOVERY NEW YORK STATE ENERGY RESEARCH AND DEVELOPMENT AUTHORITY Photographs and illustrations courtesy of American Schack, Corning Glass Works, Condensing Heat Exchanger Corporation, and National Bureau of Standards. HEAT EXCHANGER PROFITS CONTENTS N~~s 0 ENG\NES RECOVERY POTENTIAL ........................................................... 1 1 tvc~, TECHNOLOGY ...........................................................................3 'IV~~~4 .,.0 /is ECONOMICS ............................................................................ 15 ENVIRONMENT ........................................................................ 17 "'f.\l~f3\~f;.S FURNACES SYSTEM APPLICATION ........................................................... 19 ADDITIONAL INFORMATION ...................................................20 How much energy can be recovered by different industries? Stack gas heat recovery systems for different applications and their corresponding recovery potential are listed in Table 1. High-temperature industries {those having minimum processing temperatures between 1500- 2800'F) normally have adequate heat sinks to recover 40-70% ol their waste heat. Heat exchangers employed to effect this recovery are ceramic and metallic radiation recuperators, ceramic heat wheels, regenerators, waste heat boilers and fluidized beds. Medium-temperature industries {600-1500'F) can normally recover 35-60% of stack waste heat. Heat exchangers used for these applications are
    [Show full text]