R4 Ventures LLC White Paper
|
|
- Brooke Carr
- 5 years ago
- Views:
Transcription
1 R4 Ventures LLC White Paper Preliminary Temperature Performance Evaluation of New Cooling Technologies consisting of the Multistage Evaporative Cooling System (MECS) for Phoenix, AZ; Newark, DE; Houston, TX; and San Jose, CA. Applications included in this evaluation include: Inlet Air Cooling for Nat Gas Turbines/CHP Systems MECS Inlet Air Cooling for Compressed Air Systems MECS By: Darrell Richardson, CEO and Mike Reytblat, Chief Scientist R4 Ventures LLC Please direct questions to Darrell Richardson via phone (602) or or January Page 1
2 Table of Content Executive Summary Technology Summary Section 1 Preliminary Temperature Performance Evaluation for Phoenix AZ Section 2 Preliminary Temperature Performance Evaluation for Wilmington DE Section 3 Preliminary Temperature Performance Evaluation for Houston TX Section 4 Preliminary Temperature Performance Evaluation for San Jose CA Page 2
3 Executive Summary R4V Ventures LLC ( R4V ) is using research, development, innovative technologies and the earth s abundant natural and renewable resources to provide cooling to commercial and industrial buildings throughout the world. R4V s first technology to be commercialized is the Multistage Evaporative Cooling System focused on reducing the energy costs associated with pre-cooling inlet air on Natural Gas Turbines generating electricity (known in the industry as Turbine Inlet Cooling or TIC) and pre-cooling inlet air on Compressed Air Systems worldwide. R4V, through patent pending MECS solution, is providing significant cooling energy cost savings of 40 to 80% when compared to traditional mechanical cooling systems and technologies which also correspondingly significantly reduces green house gas (GHG) emissions. The patented system is the Multistage Evaporative Cooling System (MECS) formally titled Advanced Multi-Purpose, Multi-stage Evaporative Cold Water/Cold Air Generating and Supply System. The US Patent Number 8,899,061 published on December The primary benefit of TIC is that it allows the plant owners to prevent loss of Combustion Turbine (CT) output, compared to the rated capacity, when ambient temperature rises above 59 F or the plant is located in a warm/hot climate region. TIC can even allow plant owners to increase the CT output above the rated capacity by cooling the inlet air to below 59 F. In large industrial air compressors, the air entering the air compressor should be as cool as possible for maximum energy efficiency. This is due to cold air being denser than warm air making it easier to compress thereby using less mechanical energy. The colder the incoming air, the more air molecules there are, resulting in more air being compressed for each revolution of the air compressor. The MECS can also be configured as an Intercooler and Aftercooler. By employing the MECS to pre-cool the inlet air to the compressor would lessen the requirements for intercooling and aftercooling. R4 Ventures LLC has evaluated the cooled water and cooled air temperature performance of our compressor-less refrigerant-less cooling system technologies in this White Paper to provide engineering analysis of what temperatures can be attained in four major markets in the United States. The applications evaluated are: Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Inlet Air Cooling, Inlet Air Cooling/Inter-Cooling/After-Cooling on Compressed Air Systems MECS Process Cooling Water for Industrial & Food Processing Plants - MECS The Multistage Evaporative Cooling System (MECS) (Commercial/Industrial Buildings, Turbine Inlet Air Cooling, Inlet Air Cooling/Inter-Cooling/After-Cooling on Compressed Air Systems and Process Cooling Water for Industrial & Food Processing Markets) for four (4) major cities in the United States, Phoenix, AZ; Newark (Wilmington), DE; Houston, TX; and San Jose, CA. The patent pending technology including the Multistage Evaporative Cooling System (MECS) generates cold water (and cold supply air for the above described markets). This white paper details the cooled water temperature performance of the MECS and the cooled supply air temperature performance of the MECS for the above described markets based on ASHRAE published Summer Design Conditions of.4% for cooling applications, and the monthly Mean Dry Bulb and Wet Bulb Temperatures for each city s closest airport (Phoenix, Wilmington and Houston) and monthly ASHRAE published Summer Design Conditions of.4% for cooling applications (San Jose). The tables and charts below for each of the cities identified show the temperature performance of the MECS. The MECS tables and charts designed to supply cold air for Turbine/Compressor Inlet Air applications show the temperature performance based on, first, the selected and operational components of the MECS based on achieving the maximum energy efficiency in meeting or approaching the desired inlet air temperatures of 59 F (the temperature in which 100% name plate efficiency can be achieved) in natural gas turbine power generation systems and second, the selected and operational components of the MECS based on achieving the lowest possible inlet air temperature entering the turbine or compressor. Please Note: Although we only selected performance temperatures and selected stages in the Multistage Evaporative Cooling System that were closest to the desired ISO data plate temperature of 59 F equating to 100% efficiency of the Combustion Turbine, the MECS is capable of producing much lower air temperatures by utilizing more or all stages of the MECS. Using lower than 59 F as the desired inlet air temperature, efficiencies of > 100% are possible. In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module. Page 3
4 Turbine Inlet Cooling Information on Turbine Inlet Cooling or TIC is sourced from and can be found on the Turbine Inlet Cooling Association website What is TIC? TIC is cooling of the air before it enters the compressor that supplies high-pressure air to the combustion chamber from which hot air at high pressure enters the combustion turbine. TIC is also called by many other names, including combustion turbine inlet air cooling (CTIAC), turbine inlet air cooling (TIAC), combustion turbine air cooling (CTAC), and gas turbine inlet air cooling (GTIAC). Why Cool Turbine Inlet Air? The primary reason TIC is used is to enhance the power output of combustion turbines (CTs) when ambient air temperature is above 59 F. The rated capacities of all CTs are based on the standard ambient conditions of 59 F, 14.7 psia at sea level selected by the International Standards Organization (ISO). One of the common and unattractive characteristics of all CTs is that their power output decreases as the inlet air temperature increases as shown in Figure 1. It shows the effects of inlet air temperature on power output for two types of CTs: Aeroderivative and Industrial/Frame. The data in Figure 1 are typical for the two turbine types for discussion purposes. The actual characteristics of each CT could be different and depend on its actual design. The data in Figure 1 shows that for a typical aeroderivative CT, as inlet air temperature increases from 59 F to 100 F on a hot summer day (in Las Vegas, for example), its power output decreases to about 73 percent of its rated capacity. This could lead to power producers losing opportunity to sell more power just when the increase in ambient temperature increases power demand for operating air conditioners. By cooling the inlet air from 100 F to 59 F, we could prevent the loss of 27 percent of the rated generation capacity. In fact, if we cool the inlet air to about 42 F, we could enhance the power generation capacity of the CT to 110 percent of the rated capacity. Therefore, if we cool the inlet air from 100 F to 42 F, we could increase power output of an aeroderivative CT from 73 percent to 110 percent of the rated capacity or boost the output capacity by about 50 percent of the capacity at 100 F. The primary reason many power plants using CT cool the inlet air is to prevent loss of power output or even increase power output above the rated capacity when the ambient temperature is above 59 F. What are the Benefits of TIC? The primary benefit of TIC is that it allows the plant owners to prevent loss of CT output, compared to the rated capacity, when ambient temperature rises above 59 F or the plant is located in a warm/hot climate region. As discussed in the earlier section, TIC can even allow plant owners to increase the CT output above the rated capacity by cooling the inlet air to below 59 F. Page 4
5 Figure 1. Effect of Inlet Air Temperature on Combustion Turbine Power Output Figure 2. Effect of Ambient Temperature on Combustion Turbine Heat Rate The secondary benefit of TIC is that it also prevents decrease in fuel efficiency of the CT due to increase in ambient temperature above 59 F. Figure 2 shows the effect of inlet air temperature on heat rate (fuel require per unit of electric energy) for the two types of CTs discussed in the earlier section. It shows that for an aeroderivative, CT increase in inlet air temperature from 59 F to 100 F increases heat rate (and thus, decreases fuel efficiency) by 4 percent (from 100 percent at 59 F to 104 per cent at 100 F) and that cooling the inlet air from 59 F to 42 F reduces the heat rate (increases fuel efficiency) Page 5
6 by about 2 percent (from 100 percent to about 98 percent). The other benefits of TIC include increased steam production in cogeneration plants, and increased power output of steam turbines in combined cycle systems. In summary, there are many benefits of TIC when the ambient temperature is above 59 F: Increased output of CT Reduced capital cost for the enhanced power capacity Increased fuel efficiency Increased steam production in cogeneration plants Increased power output of steam turbine in combined cycle plants How does TIC help increase CT output? Power output of a CT is directly proportional to and limited by the mass flow rate of compressed air available to it from the air compressor that provides high-pressure air to the combustion chamber of the CT system. An air compressor has a fixed capacity for handling a volumetric flow rate of air. Even though the volumetric capacity of a compressor is fixed, the mass flow rate of air it delivers to the CT changes with changes in ambient air temperature. This mass flow rate of air decreases with increase in ambient temperature because the air density decreases when air temperature increases. Therefore, the power output of a combustion turbine decreases below its rated capacity at the ISO conditions (59 F, 14.7 psia at sea level) with increases in ambient temperature above 59 F. TIC allows increase in air density by lowering the temperature and thus, helps increase mass flow rate of air to the CT and results in increased output of the CT. Page 6 Compressed Air Systems What is the effect of Air Intake on Compressor performance? The effect of intake air on compressor performance should not be underestimated. Intake air that is contaminated or hot can impair compressor performance and result in excess energy and maintenance costs. If moisture, dust, or other contaminants are present in the intake air, such contaminants can build up on the internal components of the compressor, such as valves, impellers, rotors, and vanes. Such build-up can cause premature wear and reduce compressor capacity. When inlet air is cooler, it is also denser. As a result, mass flow and pressure capability increase with decreasing intake air temperatures, particularly in centrifugal compressors. This mass flow increase effect is less pronounced for lubricant-injected, rotary-screw compressors because the incoming air mixes with the higher temperature lubricant. Conversely, as the temperature of intake air increases, the air density decreases and mass flow and pressure capability decrease. The resulting reduction in capacity is often addressed by operating additional compressors, thus increasing energy consumption. Rules of thumb in designing Compressed Air Systems. 1. Air compressors normally deliver 4 to 5 CFM per horsepower at 100 psig discharge Pressure 2. Power cost for 1 horsepower operating constantly for one year at 10 cents per kwh is about $750 per year 3. Every 7 F rise in temperature of intake air will result in 1% rise in energy consumption. 4. It takes 7 to 8 hp of electricity to produce 1 hp worth of air force 5. Size air receivers for about 1 gallon of capacity for each CFM of compressor capacity 6. Compressor discharge temperatures are a key indicator of compression efficiency. Uncooled compressed air is hot, as much as 250 to 350 deg F! 7. Typical discharge temperature values before aftercooling are: Screw (175 F), Single Stage Reciprocating (350 F), Two Stage reciprocating (250 F) 8. Most water-cooled after coolers will require about 3 GPM per 100 CFM of compressed air at Discharge Air Temperature at 100 psig and will produce about 20 gallons of condensate per day. 9. Locate filters and a dryer in the airline before any pressure-reducing valve (i.e., at the highest pressure) and after air is cooled to 100 F or less (the lowest temperature). 10. Many tools require more CFM at 90 PSI than what is physically possible to get from the power available through a 120 VAC outlet. Beware, that the CFM figure given as the required air power on many tools (e.g., air chisels/hammers, sandblasters) is for an absurdly low duty cycle. You just can't run these constantly on anything but a monster compressor, but the manufacturer still wants you to believe you can, so you will buy the tool. 11. Depending on the size of the system, compressed air costs about 25 to 42 cents per thousand cubic feet of free air ingested by the compressor (including operating and maintenance costs). 12. A 50 horsepower compressor rejects approximately 126,000 BTU per hour for heat recovery.
7 13. The water vapor content at ~100 F of saturated compressed air is about two gallons per hour for each 100 CFM of compressor capacity. 14. Every ~20 F temperature drop in saturated compressed air at constant pressure, 50% of the water vapor condenses to liquid or at 100 psig every ~20 F increase in saturated air temperature doubles the amount of moisture in the air. 15. Every 2-psig change in pressure equals 1% change in horsepower. 16. Most air motors require 30 CFM at 90 psig per horsepower. 17. For every 10 water gauge pressure lost at the inlet, the compressor performance is reduced by 2%. Intake filters should be regularly cleaned well before dirt causes significant pressure restrictions. 18. A device, which will satisfactorily perform its function with 50 psig of air pressure, uses approximately 75% more compressed air when it is operated with compressed air at 100 psig. 19. As a general rule, for every 100 kpa reduction in operating pressure results in about 8% energy and cost savings. Page 7 Summary of Temperature Performance of R4 Ventures LLC s New Cooling Technologies Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Inlet Air on Compressed Air Systems MECS Brief Introduction to Turbine Inlet Cooling (TIC) - The primary reason TIC is used to enhance the power output of combustion turbines (CTs) when ambient air dry bulb temperature if above 59 F. The rated capacities of all CTs are based on the standard ambient conditions of 59 F, 14.7 psia at sea level selected by the International Standards Organization (ISO). Example: for a typical aero derivative CT, as inlet air temperature increases from 59 F to 100 F on a hot summer day, its power output decreases to about 73 percent of its rated capacity. By cooling the inlet air from 100 F to 59 F, the 27% loss of rated generation capacity can be avoided. The engineering analysis provided in this White Paper shows the lowest Inlet Air Temperature available without dehumidification. An additional 5 F to 15 F temperature reduction can be obtained by adding dehumidification to the MU AHU. 1. Phoenix AZ a. ASHRAE published Summer Design Conditions of.4% for cooling applications For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F. No compressors and refrigerants are used in the system. b. Based on the Monthly Mean Dry Bulb and Wet Bulb Temperatures - For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F in the hottest month of August. No compressors and refrigerants are used in the system. Significantly lower cold air supply temperatures of between F and F can be maintained by adding dehumidification to the MU AHU. 2. Newark DE a. ASHRAE published Summer Design Conditions of.4% for cooling applications For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F. No compressors and refrigerants are used in the system. b. Based on the Monthly Mean Dry Bulb and Wet Bulb Temperatures - For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F in the hottest month of August. No compressors and refrigerants are used in the system. Significantly lower cold air supply temperatures of between F and F can be maintained by adding dehumidification to the MU AHU. 3. Houston TX
8 a. ASHRAE published Summer Design Conditions of.4% for cooling applications For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F. No compressors and refrigerants are used in the system. b. Based on the Monthly Mean Dry Bulb and Wet Bulb Temperatures - For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F in the hottest month of August. No compressors and refrigerants are used in the system. Significantly lower cold air supply temperatures of between F and F can be maintained by adding dehumidification to the MU AHU. 4. San Jose CA a. ASHRAE published Summer Design Conditions of.4% for cooling applications For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F. No compressors and refrigerants are used in the system. b. Based on the Monthly Mean Dry Bulb and Wet Bulb Temperatures - For Inlet Air Cooling for Nat Gas Turbines/CHP Systems and Compressed Air Systems, cold supply air temperatures provided to inlet of the combustion turbine can be maintained at an air temperature of F in the hottest month of August. No compressors and refrigerants are used in the system. Significantly lower cold air supply temperatures of between F and F can be maintained by adding dehumidification to the MU AHU. Phoenix, AZ 2001 Monthly Mean Dry Bulb and Wet Bulb Temperatures for Phoenix AZ ( MECS - Turbine Inlet Cooling Outside Air () Dry Bulb F Outside Air () Wet Bulb F Selected Selected MECS MECS Components Components to To Max Energy Max Cool Air Eff. In Temp In Supplying Inlet Supplying Inlet Air to Turbines Air to Turbines & & Compressors Compressors F F January February March April May June July August September October November December Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module Outside Air () Dry Bulb F Outside Air () Wet Bulb F Selected MECS Components To Max Energy Eff. In Supplying Inlet Air to Turbines & Compressors F Selected MECS Components to Max Cool Air Temp In Supplying Inlet Air to Turbines & Compressors F 2001 Monthly Mean Dry Bulb and Wet Bulb Temperatures for Phoenix AZ ( Page 8
9 MECS - Process Cooling Water Temps Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications January February March April May June July August September October November December Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module. Newark (Wilmington), DE 2001 Monthly Mean Dry Bulb and Wet Bulb Temperatures for Wilmington DE ( Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module Monthly Mean Dry Bulb and Wet Bulb Temperatures for Wilmington DE ( Page 9 MECS - Turbine Inlet Cooling Outside Air () Dry Bulb F Outside Air () Wet Bulb F Selected MECS Components To Max Energy Eff. In Supplying Inlet Air to Turbines & Compressors F Selected MECS Components to Max Cool Air Temp In Supplying Inlet Air to Turbines & Compressors F January February March April May June July August September October November December Outside Air () Dry Bulb F Outside Air () Wet Bulb F Selected MECS Components To Max Energy Eff. In Supplying Inlet Air to Turbines & Compressors F Selected MECS Components to Max Cool Air Temp In Supplying Inlet Air to Turbines & Compressors F
10 MECS - Process Cooling Water Temps Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications January February March April May June July August September October November December Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications Houston, TX 2001 Monthly Mean Dry Bulb and Wet Bulb Temperatures for Houston, TX ( MECS - Turbine Inlet Cooling Outside Air () Dry Bulb F Outside Air () Wet Bulb F Selected MECS Components To Max Energy Eff. In Supplying Inlet Air to Turbines & Compressors F Selected MECS Components to Max Cool Air Temp In Supplying Inlet Air to Turbines & Compressors F January February March April May June July August September October November December Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module Outside Air () Bulb F Outside Air () Bulb F Dry Wet Selected MECS Components To Max Energy Eff. In Supplying Inlet Air to Turbines & Compressors F Selected MECS Components to Max Cool Air Temp In Supplying Inlet Air to Turbines & Compressors F 2001 Monthly Mean Dry Bulb and Wet Bulb Temperatures for Houston, TX ( Page 10
11 MECS - Process Cooling Water Temps Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications January February March April May June July August September October November December Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications San Jose, CA 2005 ASHRAE Handbook - ASHRAE published Summer Design Conditions of.4% for cooling applications MECS - Turbine Inlet Cooling Outside Air () Dry Bulb F Outside Air () Wet Bulb F Selected MECS Selected Components MECS To Max Components to Energy Eff. In Max Cool Air Supplying Temp In Inlet Air to Supplying Inlet Turbines & Air to Turbines Compressors & Compressors F F January February March April May June July August September October November December Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module ASHRAE Handbook - ASHRAE published Summer Design Conditions of.4% for cooling applications Outside Air () Dry Bulb F Outside Air () Wet Bulb F Selected MECS Components To Max Energy Eff. In Supplying Inlet Air to Turbines & Compressors F Selected MECS Components to Max Cool Air Temp In Supplying Inlet Air to Turbines & Compressors F Page 11
12 MECS - Process Cooling Water Temps Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications January February March April May June July August September October November December Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module Outside Air () Dry Bulb F Outside Air () Wet Bulb F MECS Cold Water Temperatures for Process Cooling Applications Page 12
13 Technology Summary Background Multistage Evaporative Cooling System Scalable from 10 to over 1000 tons. Based on Phoenix AZ Summer Ambient Air Design Conditions for cooling applications are FDB and 70 FWB, MECS delivers 57 F cool water, 53 F cold air, or both at the same time. Simple... practical design provides ease of monitoring, control, and maintenance. 40 to 80% less power usage / energy savings compared to traditional mechanical refrigeration systems NO Compressors and NO Freon MULTISTAGE EVAPORATIVE COOLING SYSTEM United States 6, Filed September 23, 2011 This was converted to the Non-Provisional Patent Application described below: NEW ADVANCED MULTI-PURPOSE MULTISTAGE EVAPORATIVE COLD WATER/COLD AIR GENERATING AND SUPPLY SYSTEM United States Filed September 22, 2012 under accelerated examination rules of USPTO Converted Provision United States Patent Application 6, to Non Provisional Patent Application. A Utility Patent Application for the Multistage Evaporative Cooling System patent was filed on September 23, The Inventor has developed new methods and systems that provide evaporative cooling by combining multiple direct and indirect evaporative cooling stages into one multistage evaporative cooling system to achieve cooling media (air or water) temperatures that are much lower than the initial wet bulb temperature of the ambient air. The Inventor has named this cooling system the Multistage Evaporative Cooling System (MECS). This new approach and method of the combined multiple direct and indirect evaporative cooling processes fully complies with all laws of thermodynamics by properly sequencing components and actions to achieve maximum cooling at a minimal energy use. The MECS outperforms conventional refrigeration systems by using at least 40-80% less energy to operate. The MECS s resulting output is cold air, cold water, or both. Page 13
14 Preliminary Performance Analysis for Phoenix AZ of the Multistage Evaporative Cooling System (MECS - Patent Pending) Parameters: 1. Phoenix, AZ Summer Ambient Air Design Conditions (ASHRAE.4% for cooling applications Phoenix AZ (PHX) are FDB and 70.0 FWB for the Energy Recovery System (Unit) or ERU, all three CTs and the Makeup Air Handling Unit (MU AHU) 2. is the inlet air at above design parameters to all stages. 3. Entered Air Conditions entering the Fill at each stage: a. CT FDB and 70 FWB b. CT FDB and FWB c. CT FDB and FWB 4. Entered Air Conditions to the MU AHU is FDB and 70.0 FWB 5. Entered Air Conditions to the ERU is FDB and 70.0 FWB Energy Recovery System (Unit) Cooling Tower 3 (CT-3) Cooling Tower 2 (CT-2) Cooling Tower 1 (CT-1) ERU MU AHU Supply Air Temps 59.8 FDB No Adiabatic Cooling (Not using Humidification) 54.8 FDB With Adiabatic Cooling (Using Humidification) water piping exhaust air exhaust air exhaust air MU AHU cooled air supply fan c/coil air washers 3c. 3b. 3a. c/coil air washer c/coil or CT Exhaust Air Munters CELdek pump pump pump CT-3 CT-2 CT-1 Cooled Water Temp F Cooled Water Temp F Cooled Water Temp 73.0 F Process Cooling Supply Water from ERU, CT-1, CT-2 or CT-3 to Plate & Frame Heat Exchangers HX-2A and HX-1B HX 2A HX 1B ERU Legend 330 ERS - Energy Recovery System (UNIT) (ERU) 811 ERU - cooling load 830 ERU - energy recovery system 831 ERU - particulate filter with downstream spray humidifer 835 ERU - fan 836 ERU - exhaust air outlet 860 ERU - pump 865 ERU - cold water outlet pipe 866 ERU - warm water inlet pipe Page 14
15 Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module. Comfort Space and Natural Gas Turbine Inlet Air Cooling "cold supply air" provided by the Multistage Evaporative Cooling System (MECS) serving Commercial and Industrial facilities and plants Temp Performance for Cold Supply Air for Commercial & Industrial Applications in Phoenix AZ ASHRAE Summer Design and Mean Monthly Temperatures in F Phoenix International Airport (PHX) Energy Recovery Unit (ERU) Stage Cold Water Temp Leaving ERU, F Without Outside Air () Humidification and With Humidification MECS Including ERU, Cooling Towers and Makeup Air Handling Unit (MU AHU) Supplying Cold Fresh Air ERU, Cooling Towers (CT-1,CT-2, CT-3) and MU AHU commissioned to provide Cold Supply Air Cooling Towers that are not necessary to meet Mean Monthly Ambient Air Temps to generate cold makeup air Selected Cold Water Temperatures from Energy Recvery Unit or Cooling Towers serving the MU AHU Multistage Evaporative Cooling System (MECS) Cooling Tower Stage Cold Water Temp Leaving Cooling Towers (CT), F Make Up Air Handling Unit (MU AHU) Stage Cold AIR Temp Leaving MU AHU, F Calculated Dew Pt F Calculated Humidity Ratio grains/lb ERU-1A without Humidification ERU-1B with Humidification to 95% RH (Adiabatic Cooling) CT-1 CT-2 CT-3 MU AHU Pre- Cooling Coil Water Temp from ERU or CT- 1, CT-2 or CT-3 (Source shown in RED) MU AHU Cold Supply Air to space without Humidification (No Adiabatic Cooling) includes 2 F for fan heat MU AHU Cold Supply Air to space with Humidification to 95% RH (Adiabatic Cooling) includes 2 F for fan heat TEMPERATURE OF INLET AIR ENTERING NATURAL GAS TURBINES (TARGET TEMP IS 59 F OR Commercial & Industrial Office Space Cold Supply Air Temperature Range DB F WB F LOWER) ASHRAE Coincident Summer Design DB & WB Temps at.4% (Annual) for Cooling Applications (35 hours per year) / CT January / ERU-1B February / ERU-1B March / ERU-1B April / ERU-1B May / CT June / CT July / CT August / CT September / CT October / CT November / ERU-1B December / ERU-1B *** NOTE *** If the negative pressure at the turbine compressor inlet allows for the elimination of the fan in the MU AHU, the temperature can be reduced by an additional 2 F. *** 1. Year round operation of MECS and MU AHU together (Comfort Cooling) can provide the required spacecooling for Commercial & Industrial Office Spaces and Natural Gas and Industrial Compressor Inlet Air Cooling. 2. System is tied into the HVAC system serving the entire building and is providing comfort conditions ("Comfort Cooling"; heating, cooling, humidification, dehumidification) as required. The column on the right in green does not take into consideration any positive or negative affects of the HVAC system. Phoenix International Airport (PHX) Jan Feb Mar Apr May Jun MEAN DRY BULB MEAN WET BULB Jul Aug Sep Oct Nov Dec Yearly Mean MEAN DRY BULB MEAN WET BULB Page 15
16 Phoenix, AZ Preliminary Temperature Performance Evaluation Summer Design Conditions Estimating temperature performance of the MECS to be located in city of Phoenix AZ. Page 16 General Below are calculations for the ASHRAE published Summer Design Conditions of.4% for cooling applications showing the ambient air design dry bulb and wet bulb temperatures for Phoenix AZ (PHX) of FDB and 70.0 FWB. Engineering Analysis Given Data DC site Location: Phoenix AZ (PHX) Site Elevation: 1200 ft. 0.4% design conditions: FDB / 70.0 FWB Assumed the following approach temperatures for: All Cooling Towers & ERUs: 3 F All pre-cooling coils for Cooling Towers: 1 F Fluid-fluid Plate HX: 1 F Design parameters of the are: Relative humidity: 12.61% Dew point temperature, F Humidity ratio: gr/lb Enthalpy: btu/lb Specific volume: ft 3 /lb Calculation Estimated temperature of the cold water leaving the Cooling Tower CT-1 and entering the ambient air pre-cooling coils of the cooling tower CT-2 is: = 73.0 F Estimated dry bulb temperature of the pre-cooled ambient air leaving pre-cooling coils of the Cooling Tower CT-2: = 74.0 F Estimated parameters of the pre-cooled ambient air entering wet media of the cooling tower CT-2A: Dry Bulb temperature: 74.0 F Wet Bulb Temperature: F Relative humidity: 38.94% Dew point temperature, F Humidity ratio: gr/lb Enthalpy: btu/lb Specific volume: ft 3 /lb
17 Estimated temperature of the cold water leaving the Cooling Tower CT-2 and entering the ambient air pre-cooling coils of the cooling tower CT-3 is: = F Estimated dry bulb temperature of the pre-cooled ambient air leaving pre-cooling coils of the Cooling Tower CT-3: = F Estimated parameters of the pre-cooled ambient air entering wet media of the cooling tower CT-3: Dry Bulb temperature: F Wet Bulb Temperature: F Relative humidity: 58.31% Dew point temperature, F Humidity ratio: gr./lb. Enthalpy: btu / lb. Specific volume: ft 3 /lb. Estimated temperature of the cold water leaving the Cooling Tower CT-3 and entering into primary loop of the liquid-liquid plate and frame HX: = F Estimated temperature of the secondary loop supply cooling water leaving plate and frame HX: = F Preliminary Temperature Performance Evaluation Monthly Mean Temperature Conditions Projected Monthly Temperature Performance of the Multistage Evaporative Cooling System The Engineering Analysis shown in the above spreadsheet estimating mean monthly thermal performance of the Multistage Evaporative Cooling System (MECS) generating cold water for use in process cooling of the inlet air on natural gas turbines and compressed air systems. This analysis uses the ASHRAE Design Conditions for Selected Locations table and specifically the Phoenix International Airport (PHX) area and the monthly mean dry bulb and wet bulb temperatures for the Phoenix International Airport (PHX). PHX.html#ixzz2XMUi3IdJ Page 17
18 Site elevation, ft.: 1200 Given conditions Preliminary Assumptions: Preliminary assumption - MECS consists of three cooling towers: CT-1, CT-2 and CT-3. An assumed approach temperature for all cooling tower CT-1, CT-2 and CT-3 is 3.0 F. An assumed approach temperature for ambient air pre-cooling coils for the mentioned cooling towers is 1.0 F. An Executive Summary of the Engineering Analysis The Engineering Analysis conducted below is based on the R4 Ventures LLC - Multi-stage Evaporative Cooling System (MECS) operating in Phoenix, AZ. Depending on the ambient conditions, in the majority of cases, the Energy Recovery Unit (ERU) operating alone would be able to satisfy the all cooling needs. In some ambient conditions, Cooling Tower CT-1, Cooling Tower CT-2, and Cooling Tower CT-3 may be operational. The sequence of operations would be CT-1 alone, CT-1 and CT-2, or CT-1, CT-2 and CT-3. All 3 Cooling Towers can be used to provide redundant back up to the Energy Recovery Units (ERU 1A and ERU 1B). This analysis results in a very economical and cost effective inlet air cooling solution providing significant energy savings as compared to traditional mechanical refrigeration systems. Page 18
19 Preliminary Performance Analysis for Newark DE of the Multistage Evaporative Cooling System (MECS - Patent Pending) Parameters: 1. Newark, Delaware Summer Ambient Air Design Conditions (ASHRAE.4% for cooling applications Wilmington DE (ILG)) are 91.9 FDB and 75.1 FWB for the Energy Recovery System (Unit) or ERU, all three CTs and the Makeup Air Handling Unit (MU AHU) 2. is the inlet air at above design parameters to all stages. 3. Entered Air Conditions entering the Fill at each stage: a. CT FDB and 75.1 FWB b. CT FDB and FWB c. CT FDB and FWB 4. Entered Air Conditions to the MU AHU is 91.9 FDB and FWB 5. Entered Air Conditions to the ERU is 91.9 FDB and 75.1 FWB Energy Recovery System (Unit) Cooling Tower 3 (CT-3) Cooling Tower 2 (CT-2) Cooling Tower 1 (CT-1) ERU MU AHU Supply Air Temps FDB No Adiabatic Cooling (Not using Humidification) 73.2 FDB With Adiabatic Cooling (Using Humidification) water piping exhaust air exhaust air exhaust air MU AHU cooled air supply fan c/coil air washers 3c. 3b. 3a. c/coil air washer c/coil or CT Exhaust Air Munters CELdek pump pump pump CT-3 CT-2 CT-1 Cooled Water Temp F Cooled Water Temp F Cooled Water Temp 78.1 F Process Cooling Supply Water from ERU, CT-1, CT-2 or CT-3 to Plate & Frame Heat Exchangers HX-2A and HX-1B HX 2A HX 1B ERU Legend 330 ERS - Energy Recovery System (UNIT) (ERU) 811 ERU - cooling load 830 ERU - energy recovery system 831 ERU - particulate filter with downstream spray humidifer 835 ERU - fan 836 ERU - exhaust air outlet 860 ERU - pump 865 ERU - cold water outlet pipe 866 ERU - warm water inlet pipe Page 19
20 Note: In locations and months of elevated or high dew point temperatures in the summer months and the need to generate <= 59 F Turbine Inlet Air is desired, the MECS will incorporate a low power consumption dehumidification module. Comfort Space and Natural Gas Turbine Inlet Air Cooling "cold supply air" provided by the Multistage Evaporative Cooling System (MECS) serving Commercial and Industrial facilities and plants Temp Performance for Cold Supply Air for Commercial & Industrial Applications in Wilmington DE ASHRAE Summer Design and Mean Monthly Temperatures in F Wilmington New Castle County Airport (ILG) Energy Recovery Unit (ERU) Stage Cold Water Temp Leaving ERU, F Without Outside Air () Humidification and With Humidification MECS Including ERU, Cooling Towers and Makeup Air Handling Unit (MU AHU) Supplying Cold Fresh Air ERU, Cooling Towers (CT-1,CT-2, CT-3) and MU AHU commissioned to provide Cold Supply Air Cooling Towers that are not necessary to meet Mean Monthly Ambient Air Temps to generate cold makeup air Selected Cold Water Temperatures from Energy Recvery Unit or Cooling Towers serving the MU AHU Multistage Evaporative Cooling System (MECS) Cooling Tower Stage Cold Water Temp Leaving Cooling Towers (CT), F Make Up Air Handling Unit (MU AHU) Stage Cold AIR Temp Leaving MU AHU, F DB F WB F Calculated Dew Pt F Calculated Humidity Ratio grains/lb ERU-1A without Humidification ERU-1B with Humidification to 95% RH (Adiabatic Cooling) CT-1 CT-2 CT-3 MU AHU Pre- Cooling Coil Water Temp from ERU or CT- 1, CT-2 or CT-3 (Source shown in RED) MU AHU Cold Supply Air to space without Humidification (No Adiabatic Cooling) includes 2 F for fan heat MU AHU Cold Supply Air to space with Humidification to 95% RH (Adiabatic Cooling) includes 2 F for fan heat Commercial & Industrial Office Space Cold Supply Air Temperature Range ASHRAE Coincident Summer Design DB & WB Temps at.4% (Annual) for Cooling Applications (35 hours per year) / CT January n/a n/a n/a n/a / ERU-1A n/a February n/a n/a n/a n/a / ERU-1A n/a March n/a n/a n/a / ERU-1A n/a April / CT May / CT June / CT July / CT August / CT September / CT October / CT November n/a n/a / CT December n/a n/a n/a /ERU-1A n/a NOTE: The reason n/a is in some columns is because the system component at this stage would either create ice or is uneconomical. (Example: Wet Bulb temperature in Januaray and February in below freezing and no benefit can be derived) The RTDCCS is designed to maximize cooling at the lowest possible energy usage and cost. TEMPERATURE OF INLET AIR ENTERING NATURAL GAS TURBINES (TARGET TEMP IS 59 F OR *** NOTE *** If the negative pressure at the turbine compressor inlet allows for the elimination of the fan in the MU AHU, the temperature can be reduced by an additional 2 F. *** 1. Year round operation of MECS and MU AHU together (Comfort Cooling) can provide the required spacecooling for Commercial & Industrial Office Spaces and Natural Gas and Industrial Compressor Inlet Air Cooling. 2. System is tied into the HVAC system serving the entire building and is providing comfort conditions ("Comfort Cooling"; heating, cooling, humidification, dehumidification) as required. The column on the right in green does not take into consideration any positive or negative affects of the HVAC system. LOWER) Wilmington New Castle County Airport (ILG) Jan Feb Mar Apr May Jun MEAN DRY BULB MEAN WET BULB Jul Aug Sep Oct Nov Dec Yearly Mean MEAN DRY BULB MEAN WET BULB Page 20
21 Newark, DE Preliminary Temperature Performance Evaluation Summer Design Conditions Estimating temperature performance of the Multistage Evaporative Cooling System (MECS) for Newark, DE General Below are calculations for the ASHRAE published Summer Design Conditions of.4% for cooling applications showing the ambient air design dry bulb and wet bulb temperatures for Newark, DE (Wilmington New Castle County Airport (ILG) of 91.9 FDB and 75.1 FWB. Page 21 Engineering Analysis Given Data DC site Location: Wilmington DE (Near the Newark, DE DC location) Site Elevation: 125 ft. 0.4% design conditions: 91.9 FDB / 75.1 FWB Assumed the following approach temperatures for: All Cooling Towers &ERUs: 3 F All pre-cooling coils for Cooling Towers: 1 F Fluid-fluid Plate HX: 1 F Design parameters of the are: Relative humidity: 46.37% Dew point temperature, F Humidity ratio: gr/lb Enthalpy: btu/lb Specific volume: ft 3 /lb Calculation Estimated temperature of the cold water leaving the Cooling Tower CT-1 and entering the ambient air pre-cooling coils of the cooling tower CT-2 is: = 78.1 F Estimated dry bulb temperature of the pre-cooled ambient air leaving pre-cooling coils of the Cooling Tower CT-2: = 79.1 F Estimated parameters of the pre-cooled ambient air entering wet media of the cooling tower CT-2A: Dry Bulb temperature: 79.1 F Wet Bulb Temperature: F Relative humidity: 69.8% Dew point temperature, F Humidity ratio: gr/lb Enthalpy: btu/lb Specific volume: ft 3 /lb
22 Estimated temperature of the cold water leaving the Cooling Tower CT-2 and entering the ambient air pre-cooling coils of the cooling tower CT-3 is: = F Estimated dry bulb temperature of the pre-cooled ambient air leaving pre-cooling coils of the Cooling Tower CT-3: = F Estimated parameters of the pre-cooled ambient air entering wet media of the cooling tower CT-3: Dry Bulb temperature: F Wet Bulb Temperature: F Relative humidity: 78.45% Dew point temperature, F Humidity ratio: gr./lb. Enthalpy: btu / lb. Specific volume: ft 3 /lb. Estimated temperature of the cold water leaving the Cooling Tower CT-3 and entering into primary loop of the liquid-liquid plate and frame HX: = F Estimated temperature of the secondary loop supply cooling water leaving plate and frame HX: = F Preliminary Temperature Performance Evaluation Monthly Mean Temperature Conditions Projected Monthly Temperature Performance of the Multistage Evaporative Cooling System The Engineering Analysis shown in the above spreadsheet estimating mean monthly thermal performance of the Multistage Evaporative Cooling System (MECS) generating cold water for use in process cooling of the inlet air on natural gas turbines and compressed air systems. This analysis uses the ASHRAE Design Conditions for Selected Locations table and specifically the Wilmington New Castle Airport (ILG) area and the monthly mean dry bulb and wet bulb temperatures for the Wilmington New Castle Airport (ILG). Delaware-ILG.html Site elevation, ft.: 125 Given conditions Page 22
R4 Ventures LLC White Paper. Introduction
R4 Ventures LLC White Paper Preliminary Temperature Performance Evaluation of New Cooling Technologies consisting of the Multistage Evaporative Cooling System (MECS) alone or combined with the Real Time
More informationRedesign of Bennett Hall HVAC System
MEE 488 April 18, 2006 Redesign of Bennett Hall HVAC System Greg Andreasen Michael Chicoine Florent Hohxa Jason Jacobe Mechanical Engineering, University of Maine, Orono ME 04473, USA ABSTRACT Our task
More informationS.A. Klein and G.F. Nellis Cambridge University Press, 2011
12.A-1 A mixture of helium and water vapor is flowing through a pipe at T= 90 C and P = 150 kpa. The mole fraction of helium is y He = 0.80. a.) What is the relative humidity of the mixture? b.) What is
More informationSession: HVAC 101 HVAC 101. Steve Sain Sain Engineering Associates, Inc. August 9, Rhode Island Convention Center Providence, Rhode Island
Session: HVAC 101 HVAC 101 Steve Sain Sain Engineering Associates, Inc. August 9, 2016 Rhode Island Convention Center Providence, Rhode Island Why? 2 Acknowledgements 3 Disclaimer I m gonna shoot down
More informationPRESSURE-ENTHALPY CHARTS AND THEIR USE By: Dr. Ralph C. Downing E.I. du Pont de Nemours & Co., Inc. Freon Products Division
INTRODUCTION PRESSURE-ENTHALPY CHARTS AND THEIR USE The refrigerant in a refrigeration system, regardless of type, is present in two different states. It is present as liquid and as vapor (or gas). During
More informationDehumidification: Energy Efficiency Comparisons
Fourth Annual Energy Management Workshop Cocoa, Florida February 10-11, 2003 Dehumidification: Energy Efficiency Comparisons Michael K. West, Ph.D., P.E. Building Systems Scientist Advantek Consulting,
More informationThomas J Kelly. Fundamentals of Refrigeration. Sr. Engineering Instructor Carrier Corporation. August 20, Page number: 1.
Thomas J Kelly Sr. Engineering Instructor Carrier Corporation August 20, 2003 1 SESSION OBJECTIVES At the conclusion of this session you should be able to: 1. Describe the basics principles of refrigeration
More informationFor an ideal gas mixture, Dalton s law states that the sum of the partial pressures of the individual components is equal to the total pressure.
1 PSYCHROMETICS Psychrometry is the study of the characteristics of moist air. We will see soon that evaporation of moisture from the skin can have a significant impact on thermal comfort. The rate of
More informationA/C Cooling Load calculation and measurement
Testo Inc. 40 White Lake Rd. Sparta NJ 07871 (800) 227-0729 A/C Cooling Load calculation and measurement When we talk about sizing an air conditioning appliance (tons of cooling, BTU/h or KW), we are specifying
More informationMath. The latent heat of fusion for water is 144 BTU s Per Lb. The latent heat of vaporization for water is 970 Btu s per Lb.
HVAC Math The latent heat of fusion for water is 144 BTU s Per Lb. The latent heat of vaporization for water is 970 Btu s per Lb. Math F. to C. Conversion = (f-32)*(5/9) C. to F. Conversion = C * 9/5 +
More informationCopyright 2003 IBACOS, Inc. All rights reserved.
Domestic Hot Water Research Research conducted by Bill Rittelmann Presented by Duncan Prahl Partners for High Performance Homes Meeting Westminster, CO, June 23, 2005 DHW Systems: Current Technologies
More informationME 410 MECHANICAL ENGINEERING SYSTEMS LABORATORY MASS & ENERGY BALANCES IN PSYCHROMETRIC PROCESSES EXPERIMENT 3
ME 410 MECHANICAL ENGINEERING SYSTEMS LABORATORY MASS & ENERGY BALANCES IN PSYCHROMETRIC PROCESSES EXPERIMENT 3 1. OBJECTIVE The objective of this experiment is to observe four basic psychrometric processes
More informationDepartment of Mechanical Engineering ME 322 Mechanical Engineering Thermodynamics
Department of Mechanical Engineering ME 3 Mechanical Engineering Thermodynamics Lecture 34 The Psychrometric Chart Psychrometric Properties in EES Air Conditioning Processes Moist Air Properties Using
More informationCase 13 Food Storage & Processing Center
Case 13 Food Storage & Processing Center Copy Right By: Thomas T.S. Wan ( ) Feb. 2, 2002 All Rights Reserved Case Background: The refrigeration system is for a food processing and storage facility. The
More informationMechanical System Redesign. Dedicated Outdoor Air System. Design Criteria
Mechanical System Redesign Dedicated Outdoor Air System Design Criteria The outdoor air conditions used were for Philadelphia, Pennsylvania IAP at a 0.4% occurrence. The supply air conditions were developed
More informationChapter 14, Problem 27.
Chapter 14, Problem 27. A house contains air at 25 C and 65 percent relative humidity. Will any moisture condense on the inner surfaces of the windows when the temperature of the window drops to 10 C?
More informationME 410 MECHA ICAL E GI EERI G SYSTEMS LABORATORY
ME 410 MECHA ICAL E GI EERI G SYSTEMS LABORATORY MASS & E ERGY BALA CES I PSYCHROMETRIC PROCESSES EXPERIME T 3 1. OBJECTIVE The object of this experiment is to observe four basic psychrometric processes
More informationLife-Cycle Energy Costs and Greenhouse Gas Emissions for Gas Turbine Power
energy center Paper Report Summary 210-1 174-2 Fixed and Floating Head Pressure Comparison for Madison Ice Arena Life-Cycle Energy Costs and Greenhouse Gas Emissions for Gas Turbine Power July 1998 April,
More information3. (a) Explain the working of a rotary screw compressor. [10] (b) How the capacity control is achieved in refrigerant compressor?
Code No: RR410305 Set No. 1 IV B.Tech I Semester Regular Examinations, November 2006 REFRIGERATION & AIR CONDITIONING (Mechanical Engineering) Time: 3 hours Max Marks: 80 Answer any FIVE Questions All
More informationRefrigeration and Boil Off Compression Systems for NGL Export Facilities
Refrigeration and Boil Off Compression Systems for NGL Export Facilities February 2015 2015 Gas/Electric Partnership Conference IHS INTERNATIONAL: US POISED TO LEAD WORLD EXPORTS OF LPG From Oil and Gas
More informationPsychrometrics. Outline. Psychrometrics. What is psychrometrics? Psychrometrics in daily life and food industry Psychrometric chart
Psychrometrics Outline What is psychrometrics? Psychrometrics in daily life and food industry Psychrometric chart Dry bulb temperature, wet bulb temperature, absolute humidity, relative humidity, specific
More informationVARIABLE HEAT RECOVERY IN DOUBLE BUNDLE ELECTRIC CHILLERS. Richard J Liesen 1, Rahul J Chillar 2 1 University of Illinois at Urbana Champaign
VARIABLE HEAT RECOVERY IN DOUBLE BUNDLE ELECTRIC CHILLERS Richard J Liesen 1, Rahul J Chillar 2 1 University of Illinois at Urbana Champaign Dept of Mechanical & Industrial Engineering 1206 WGreen St Urbana,
More informationEnergy Efficient Corn Drying. Kenneth Hellevang, Ph.D., P.E. Professor & Extension Engineer
Energy Efficient Corn Drying Kenneth Hellevang, Ph.D., P.E. Professor & Extension Engineer Estimated Corn Field Drying EMC (%) PET (in) Est. Drying (%pt) Month Week Sep 15 4.0-5.0 18 4.5 Oct 16 2.8-3.5
More informationGRAIN STORAGE AERATION PRESENTED BY: BRENT BLOEMENDAAL AERATION EXPERT
GRAIN STORAGE AERATION PRESENTED BY: BRENT BLOEMENDAAL AERATION EXPERT OUR PART condition store harvest use or market CHOICES field dry & store natural air dry & store dryer store dryer store natural air
More information100% Outdoor Air Dehumidification Methods
Technical Bulletin 16 100% Outdoor Air ehumidification Methods I NTROUCTION As consulting engineers and end users implement the ASHRAE 6 ventilation code, they are faced with selecting an appropriate method
More informationMSP WRAP-AROUND MULTIPLE SMALL PLATE DEHUMIDIFICATION TECHNOLOGY VS. CONVENTIONAL DEHUMIDIFICATION IN DEDICATED OUTDOOR AIR SYSTEMS (DOAS)
MSP WRAP-ARUND MULTIPLE SMALL PLATE DEHUMIDIFICATIN TECHNLGY VS. CNVENTINAL DEHUMIDIFICATIN IN DEDICATED UTDR AIR SYSTEMS (DAS) ++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++++
More informationCTI Sponsored Educational Program
Presented By: Kent Martens SPX Cooling Technologies, Inc. Slide No.: 1 CTI Mission Statement To advocate and promote the use of environmentally responsible Evaporative Heat Transfer Systems (EHTS) for
More informationAppendix A. Glossary of Common Terms
Glossary of Common Terms Glossary of Common Terms Absorption chiller A refrigeration machine using heat as the power input to generate chilled water. Adjustable speed drive A means of changing the speed
More informationOn Balance: Heat Rejection Control a Packaged Solution
On Balance: Heat Rejection Control a Packaged Solution Echelon Americas Channel Partner Conference March 11, 2005 Presented by Doug Scott VaCom Technologies La Verne, California Opportunity An integrated
More informationR07. Answer any FIVE Questions All Questions carry equal marks *****
Set No: 1 III B.Tech. II Semester Supplementary Examinations, April/May 2013 REFRIGERATION AND AIR CONDITIONING (Mechanical Engineering) Time: 3 Hours Max Marks: 80 Answer any FIVE Questions All Questions
More informationSIDDHARTH GROUP OF INSTITUTIONS :: PUTTUR Siddharth Nagar, Narayanavanam Road AUTONOMOUS QUESTION BANK (DESCRIPTIVE) UNIT I
SIDDHARTH GROUP OF INSTITUTIONS :: PUTTUR Siddharth Nagar, Narayanavanam Road 517583 AUTONOMOUS QUESTION BANK (DESCRIPTIVE) Subject with Code : Refrigeration and Air Conditioning (16ME8806) Course & Branch:
More informationUpdate Dedicated Heat Recovery Chiller Technology. Don Frye. Gulf South
3/5/2018 1 Update Dedicated Heat Recovery Chiller Technology Don Frye Gulf South Good design is an intentional act Begin with the end in mind Basic Bldg Tenants IAQ (low VOC & CO 2 ) Controlled Temp &
More informationA Primer for Air Dryer Selection
HYDRAULICS EXTRACTED FROM NOVEMBER 1980 & PNEUMATICS UPDATED JUNE 2015 A Primer for Air Dryer Selection Energy and maintenance costs are key factors in choosing these important components By Charles Henderson,
More informationMECHANICAL ENGINEERING THERMAL AND FLUID SYSTEMS STUDY PROBLEMS
MECHANICAL ENGINEERING THERMAL AND FLUID SYSTEMS STUDY PROBLEMS MASS BALANCES, PSYCHROMETRICS & HVAC 1 Copyright 2018. All rights reserved. How to use this book The exam specifications in effect since
More informationBASE LEVEL AUDIT REQUIREMENTS REFRIGERATION SYSTEMS 1. SITE DATA COLLECTION. Business Name. Site physical address (Street, Suburb, City)
BASE LEVEL AUDIT REQUIREMENTS REFRIGERATION SYSTEMS 1. SITE DATA COLLECTION Business Name Site physical address (Street, Suburb, City) Nature of site / business operation Electricity Supplier Power factor
More informationterminal units only provide sensible cooling, a separate dehumidification system is usually needed.
providing insights for today s hvac system designer Engineers Newsletter volume 44 3 Dual-Temperature Chiller Plants This Engineers Newsletter describes several dual-temperature configurations that can
More informationWeek 4. Gas-vapor mixtures Air conditioning processes. ME 300 Thermodynamics II 1
Week 4 Gas-vapor mixtures Air conditioning processes ME 300 Thermodynamics II 1 Today s Outline Gas-vapor mixtures Key definitions and measures ME 300 Thermodynamics II 2 Gas-vapor Mixtures At temperatures
More informationTHERMAL ICE STORAGE: Application & Design Guide
THERMAL ICE STORAGE: Application & Design Guide Table of Contents: 1. Introduction A. History of Thermal Energy Storage B. Operating and Cost Benefits 2. Applications A Fundamental System B. HVAC Cooling
More informationTHE PSYCHROMETRIC CALCULATOR By: Stanley F. Gallos, The Bastian-Blessing Company INTRODUCTION PROPERTIES OF THE RSES CALCULATOR
Source Application Manual SAM Chapter 620-20 Section 03 THE PSYCHROMETRIC CALCULATOR By: Stanley F. Gallos, The Bastian-Blessing Company INTRODUCTION Problems involving changes in temperature, humidity,
More informationThermodynamic Calculations of Two-Stage Vapor Compression Refrigeration Cycle with Flash Chamber and Separate Vapor Mixing Intercooler
Thermodynamic Calculations of Two-Stage Vapor Compression Refrigeration Cycle with Flash Chamber and Separate Vapor Mixing Intercooler Author: Volodymyr Voloshchuk Vl.volodya@gmail.com Introduction In
More informationD-PAC. Digital Precise Air Control System. Functionality Factory Testing Ease of Installation Ease of Maintenance Energy Efficiency
Digital Precise Air Control System D-PAC Functionality Factory Testing Ease of Installation Ease of Maintenance Energy Efficiency AAON 24 South Yukon Avenue Tulsa, Oklahoma 747 (918) 583-2266 Fax (918)
More informationAuburn University Basketball Arena:
Auburn University Basketball Arena: How Building Data Analytics Achieved Energy and O&M Savings While Improving Comfort and Sustainability Eric Moore, PE, CEM, Auburn University Hadas Webb, CEM, Cimetrics
More informationHVAC Systems What the Rater Needs to Know in the Field CALCS-PLUS
HVAC Systems What the Rater Needs to Know in the Field This presentation used CASE* studies from the following *CASE Copy And Steal Everything HVAC Systems - What the Rater Needs to Know in the Field This
More informationAir Conditioning Clinic. Absorption Water Chillers One of the Equipment Series TRG-TRC011-EN
Air Conditioning Clinic Absorption Water Chillers One of the Equipment Series TRG-TRC011-EN Absorption Water Chillers One of the Equipment Series A publication of The Trane Company Worldwide Applied Systems
More informationME Mechanical Engineering Systems Laboratory. Experiment 3 - Mass and Energy Balances in Psychrometric Processes
ME 410 - Mechanical Engineering Systems Laboratory Experiment 3 - Mass and Energy Balances in Psychrometric Processes Assist.Prof.Dr. Özgür BAYER, A-123 AIR-CONDITIONING (A/C) Goal: Control temperature
More informationTemperature. In the HVAC area, we talk about two kinds of temperatures.
HEATING and COOLING HEATING and COOLING PSYCHROMETRIC CHART Temperature In the HVAC area, we talk about two kinds of temperatures. One is called dry bulb (DB) temperature, a fancy name for the reading
More informationLow GWP Refrigerants for Air Conditioning Applications
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2014 Low GWP Refrigerants for Air Conditioning Applications Samuel F. Yana Motta
More informationFS 231: Final Exam (5-6-05) Part A (Closed Book): 60 points
Name: Start time: End time: FS 231: Final Exam (5-6-05) Part A (Closed Book): 60 points 1. What are the units of the following quantities? (10 points) a. Enthalpy of a refrigerant b. Dryness fraction of
More informationSpecial Topics on Residential HVAC
Special Topics on Residential HVAC by Armin Rudd USDOE Building America Program for EEBA Conference 2002 Phoenix, Arizona 10 October 2002 Page 1 of 25 Two Main Topics: 1. Cyclical trade-offs between building
More informations. Properties for R134a are as follows : Saturated R-134a Superheated R-134a
CHAPTER 9 REFRIGERATION & AIR-CONDITIONING YEAR 2012 ONE MARK Common Data For Q. 1 and Q.2 A refrigerator operates between 120 kpa and 800 kpa in an ideal vapour compression cycle with R-134a as the refrigerant.
More informationSummary Comparison of Simulation Program Features
Summary Comparison of Simulation Program Features FEATURE DOE2.2 equest TRACE 700 HAP Public/Proprietary Public Domain Proprietary Proprietary Proprietary Simulation Method 8760 hours 8760 hours 8760 hours
More informationApplications of Thermodynamics: Heat Pumps and Refrigerators
Applications of Thermodynamics: Heat Pumps and Refrigerators Bởi: OpenStaxCollege Almost every home contains a refrigerator. Most people don t realize they are also sharing their homes with a heat pump.
More informationTechnical Report #3 Mechanical Systems Existing Conditions Evaluation
Mechanical Option Technical Report #3 Technical Report #3 Mechanical Systems Existing Conditions Evaluation Instructor: Dr. Bahnfleth 11.15.04 Building Sponsor: CCG Facilities Integration Table of Contents
More informationTo accomplish this, the refrigerant fi tis pumped throughh aclosed looped pipe system.
Basics Refrigeration is the removal of heat from a material or space, so that it s temperature is lower than that of it s surroundings. When refrigerant absorbs the unwanted heat, this raises the refrigerant
More informationSummary of Comments (Washington Revisions November 7, 2000) Update November 27, 2000
SAE Alternate Refrigerant Cooperative Research Program Summary of Comments (Washington Revisions November 7, 2000) Update November 27, 2000 To: Alternate Refrigerant Task Force Members From: Ward Atkinson
More informationMethod to test HVAC equipment at part load conditions
IPLV Method to test HVAC equipment at part load conditions For water cooled chillers: 100% load ( % hrs) + 75% ( Hrs ) + 50% ( Hrs ) + 25% ( Hrs ) = IPLV value Manufacturer can favor this number by tweaking
More informationDecember 6, 2018 Optimizing Solutions through Superior Dehumidification Technology SM
Humidity Control and Heating and Cooling Applications December 6, 2018 Optimizing Solutions through Superior Dehumidification Technology SM Today s Discussion Discussion of cooling, heating and dehumidification
More informationPharmaceutical Facility Design
PhEn-602 Pharmaceutical Facility Design J. Manfredi Notes 9A PhEn-602 J. Manfredi 1 Primary & Secondary HVAC units Primary Primary air handling unit arrangement: One unit is responsible for all of the
More informationPINNACLE SERIES DEDICATED OUTDOOR AIR SYSTEM ENERGY EFFICIENT DEHUMIDIFICATION
ENERGY EFFICIENT DEHUMIDIFICATION PINNACLE SERIES DEDICATED OUTDOOR AIR SYSTEM Provides a very high degree of latent cooling using only a minimal amount of conventional cooling input Substantial energy
More informationAND AIR-CONDITIONING. Dr Ali Jawarneh Department of Mechanical Engineering Hashemite University
Chapter 14 GAS VAPOR MIXTURES AND AIR-CONDITIONING Dr Ali Jawarneh Department of Mechanical Engineering Hashemite University 2 Objectives Differentiate between dry air and atmospheric air. Define and calculate
More informationannouncements 4/10/08
Psychrometrics & Design Strategies ARCH 331/431 Spring 2008 Lecture 4 announcements 4/10/08 course website: http://courses.washington.edu/arch3431/index.shtml Course materials (readings, assignments, lectures,
More informationHVAC Water chiller selection and optimisation of operation
HVAC Water chiller selection and optimisation of operation Introduction Water-chiller is a broad term describing an overall package that includes an electrical control panel, refrigeration plant, water
More informationIV SEMESTER DIPLOMA EXAMINATION, JANUARY-2013 THERMODYNAMICS
AE401,ME401,DAE19,DME19 IV SEMESTER DIPLOMA EXAMINATION, JANUARY-2013 THERMODYNAMICS Time: 3 Hours Max. Marks: 75 GROUP A : Answer any three questions. (Question No. 1 is compulsory) Q.1 Write a short
More informationCARRIER edesign SUITE NEWS. Modeling 100% OA Constant Volume Air Systems. Volume 6, Issue 1. Page 1 Modeling 100% OA Constant Volume Air Systems
Volume 6, Issue 1 CARRIER edesign SUITE NEWS Modeling 100% OA Constant Volume Air Systems This article provides an overview of how to model a stand-alone constant air volume (CAV) 100% OA system in HAP.
More informationEvaporative Cooling in a Hot-Dry Climate
Evaporative Cooling in a Hot-Dry Climate David Springer Davis Energy Group SWEEP Workshop July 10, 2007 Sponsors: Clarum Homes California Energy Commission U.S.Department of Energy Issues for Discussion
More informationThe Basics - B Practical Psychrometrics. Jerry Cohen President Jacco & Assoc.
The Basics - B Practical Psychrometrics Jerry Cohen President Jacco & Assoc. Who is Jacco Established 1968 Hudson, Ohio Columbus, Ohio Toledo, Ohio Focused on the Engineered Environment Systems Knowledgeable
More informationR10. IV B.Tech I Semester Regular/Supplementary Examinations, Nov/Dec REFRIGERATION & AIR-CONDITIONING (Mechanical Engineering)
Set No. 1 IV B.Tech I Semester Regular/Supplementary Examinations, Nov/Dec - 2014 REFRIGERATION & AIR-CONDITIONING (Mechanical Engineering) Time: 3 hours Max. Marks: 75 Answer any FIVE Questions All Questions
More informationChiller Plant Design. Julian R. de Bullet President debullet Consulting
Chiller Plant Design Julian R. de Bullet President debullet Consulting 703-483-0179 julian@debullet.com This ASHRAE Distinguished Lecturer is brought to you by the Society Chapter Technology Transfer ASHRAE
More informationIntroduction to HVAC. American Standard Inc Air Conditioning Clinic TRG-TRC018-EN
Introduction to HVAC Agenda Psychrometrics Human Comfort Heat Transfer Refrigeration Cycle HVAC Terminology HVAC Systems Introduction to HVAC Psychrometrics 2000 TRG-TRC002-EN Properties of Air Dry-bulb
More informationDesiccant Dehumidification in Air Conditioning for a Large Commercial Building
2333 Desiccant Dehumidification in Air Conditioning for a Large Commercial Building Hyun W Kim, Kamal Abou-Khamis Youngstown State University Abstract A case study was done to investigate the performance
More informationDesigning Energy Efficient Outdoor Air Systems
Designing Energy Efficient Outdoor Air Systems Joseph Thorndal Applied Products Sales Manager Greenheck, Schofield, Wisconsin 1 Joseph Thorndal BS Industrial Engineering North Dakota State University Work
More informationContinuous Commissioning: A Valuable Partner to Retrofit Projects
Continuous Commissioning: A Valuable Partner to Retrofit Projects Yeqiao Zhu Aamer Athar Kenneth Banks Ph.D. PE, CEM PE, CEM Energy Systems Laboratory Sempra Energy Solutions Sempra Energy Solutions Charles
More informationDehumidification for Industrial Coating Applications. By: Jay Kranker Munters MCS
Dehumidification for Industrial Coating Applications By: Jay Kranker Munters MCS Reasons for Using Dehumidification Construction/Coating Schedules New VOC Regulations Paint Specifications Adverse Weather
More informationEVAPORATIVE AIR-COOLING EQUIPMENT
T CHAPTER 41 EVAPORATIVE AIR-COOLING EQUIPMENT Direct Evaporative Air Coolers... 41.1 Indirect Evaporative Air Coolers... 41.3 Indirect/Direct Combinations... 41.5 Air Washers... 41.6 Humidification/Dehumidification...
More informationHeat pump and energy recovery systems
SBS5311 HVACR II http://ibse.hk/sbs5311/ Heat pump and energy recovery systems Ir. Dr. Sam C. M. Hui Faculty of Science and Technology E-mail: cmhui@vtc.edu.hk Oct 2017 Contents Basic concepts Air-to-air
More information6. Within an internal combustion engine, the can-shaped component that moves up and down the cylinder
Student ID: 22133336 Exam: 986052RR - Heat When you have completed your exam and reviewed your answers, click Submit Exam. Answers will not be recorded until you hit Submit Exam. If you need to exit before
More informationEvaluation of HCFC Alternative Refrigerants
Evaluation of HCFC Alternative Refrigerants Shaobo Jia Global Innovation Heatcraft Worldwide Refrigeration shaobo.jia@heatcraftrpd.com Introduction It is well-known that HCFC refrigerants widely used in
More informationEnergy Impacts of Compressed Air
The Overlooked: Water 101/Plug Loads/Process Energy Impacts of Compressed Air Rusty Friend AMEC Foster Wheeler August 14, 2017 Tampa Convention Center Tampa, Florida Energy Impacts of Compressed Air Energy
More informationHello, my name is Sarah Hilden and I am a Marketing Engineer in the C.D.S. group at Trane.
Slide 1 TRACE 700 Waterside Economizers Hello, my name is Sarah Hilden and I am a Marketing Engineer in the C.D.S. group at Trane. Today, we will be going over how to model waterside economizers in TRACE
More informationEnergy-Efficient Makeup Air Units BY HUGH CROWTHER, P.ENG., MEMBER ASHRAE
This article was published in ASHRAE Journal, March 20145 Copyright 2015 ASHRAE. Posted at www.ashrae.org. This article may not be copied and/or distributed electronically or in paper form without permission
More informationArticle Energy Saving Benefits of Adiabatic Humidification in the Air Conditioning Systems of Semiconductor Cleanrooms
Article Energy Saving Benefits of Adiabatic Humidification in the Air Conditioning Systems of Semiconductor Cleanrooms Min Suk Jo, Jang Hoon Shin, Won Jun Kim and Jae Weon Jeong * Department of Architectural
More informationAir-Handling System Cooling Options
Air-Handling System Cooling Options High-Capacity, Economical Evaporative Cooling High-Efficiency, DX & CW Mechanical Cooling Pure and Simple Solutions AbsolutAire Air-Handling System Cooling Options Economical
More information5. ASSESSMENT RECOMMENDATIONS
5. ASSESSMENT RECOMMENDATIONS AR No. 1 Reduce Discharge Pressure Recommended Action Reduce the minimum condensing temperatures on your warehouse refrigeration systems from 110 F to 60 F. In order to reduce
More informationThe Electronic Newsletter of The Industrial Refrigeration Consortium Vol. 11 No. 1, 2011
chan The Electronic Newsletter of The Industrial Refrigeration Consortium Vol. 11 No. 1, 2011 PRESSURE RELIEF CAPACITY DETERMINATION FOR EQUIPMENT Previously in The Cold Front (2006), we provided an introduction
More informationTrilliumSeries. Condenser
TrilliumSeries Condenser TrilliumSeries Condenser The TrilliumSeries Condenser uses a patented Dry-Coil Adiabatic Design that saves energy, reduces refrigerant change, and lowers operating costs. The TrilliumSeries
More informationStandards and Guidelines. Presented by: Aric Murray December 12, 2014
TDSHS Ventilation Standards and Guidelines Presented by: Aric Murray December 12, 2014 Agenda 1. What are the TDSHS ventilation 1. What are the TDSHS ventilation requirements? 2. Pressure relationships.
More informationOptimizing Electric Humidifier Operation with an Air Side Economizer
Optimizing Electric Humidifier Operation with an Air Side Economizer Usama F. Shami, P.E. Senior Project Engineer Savage Engineering, Inc. Foster City, CA Abstract Air side economizer cycle is a control
More informationDES CHAMPS PRODUCTS. Specializing in: -- Air-to-Air Energy Recovery -- Conditioning Outdoor Air -- Controlling IAQ -- Indirect Evaporative Cooling
DES CHAMPS PRODUCTS Specializing in: -- Air-to-Air Energy Recovery -- Conditioning Outdoor Air -- Controlling IAQ -- Indirect Evaporative Cooling DES CHAMPS PRODUCTS Packaged Heat Recovery Systems Micro-Z
More informationCE311 Fall 2016 Mid-Term Exam 1
CE311 Fall 16 Mid-Term Exam 1 Name Instructions 1. Please solve the problems using the specified SI or IP system of units. 2. Please show all of your calculations to get full credit and pay attention to
More informationOPTIMISE VACUUM TO IMPROVE PLANT PERFORMNCE
OPTIMISE VACUUM TO IMPROVE PLANT PERFORMNCE Vacuum Pumps and systems are widely used in the chemical process industry for various applications such as drying, solvent recovery, distillation, short path
More informationDescription of All Alternatives Considered-
Description of All Alternatives Considered- Energy efficiency is an area where the Tubman design can be improved. The design heating load is 1807.8 MBH and the design cooling load is 1702.2 MBH or 142
More informationCompressed Air. Energy Efficiency Reference Guide
Compressed Air Energy Efficiency Reference Guide DISCLAIMER: Neither CEA Technologies Inc. (CEATI), the authors, nor any of the organizations providing funding support for this work (including any persons
More information2013 Guideline for Specifying the Thermal Performance of Cool Storage Equipment. AHRI Guideline T (I-P)
2013 Guideline for Specifying the Thermal Performance of Cool Storage Equipment AHRI Guideline T (I-P) IMPORTANT SAFETY DISCLAIMER AHRI does not set safety standards and does not certify or guarantee the
More informationLaboratory Evaluation of Hybrid and Advanced Water Heaters: Performance Overview in Hot Humid Climate
Laboratory Evaluation of Hybrid and Advanced Water Heaters: Performance Overview in Hot Humid Climate American Council for an Energy Efficient Economy ACEE Hot Water Forum Nov. 4-5, 2013 Carlos J. Colon
More informationENERGY RECOVERY HEAT PIPE HEAT EXCHANGERS
WAHX (WRAP-AROUND) AAHX (AIR-TO-AIR) ENERGY RECOVERY HEAT PIPE HEAT EXCHANGERS HVAC PRODUCT GUIDE THERMAL MANAGEMENT EXPERTS ADVANCED COOLING TECHNOLOGIES, INC. IS A PREMIER THERMAL MANAGEMENT SOLUTIONS
More informationThe Ed Roberts Campus
The Ed Roberts Campus Technical Report 3 Anderson Clemenceau Mechanical Option Advisor: Donghyun Rim November 11, 2014 2 Contents Technical Report 3... 1 Executive Summary... 3 Building Overview... 4 Design
More informationSECTION 5 COMMERCIAL REFRIGERATION UNIT 22 CONDENSERS UNIT OBJECTIVES UNIT OBJECTIVES 3/22/2012
SECTION 5 COMMERCIAL REFRIGERATION UNIT 22 CONDENSERS UNIT OBJECTIVES After studying this unit, the reader should be able to explain the purpose of the condenser in a refrigeration system. describe differences
More informationChillers, air and water cooled, featuring centrifugal compressors with magnetic levitation, from 200 to kw
Chillers, air and water cooled, featuring centrifugal compressors with magnetic levitation, from 200 to 1.99 kw Centrifugal compressor with magnetic levitation This is a miniaturized, highly innovative
More informationASHRAE Region VI CRC Track III: Session 3 Ventilation Energy Recovery. Steven T. Taylor, PE Principal Taylor Engineering
ASHRAE Region VI CRC Track III: Session 3 Ventilation Energy Recovery Steven T. Taylor, PE Principal Taylor Engineering This program is registered with the AIA/CES for continuing professional education.
More informationFundamentals of Psychrometrics. By James L. Murphy, Colorado Building Environments Sales Engineer
Fundamentals of Psychrometrics By James L. Murphy, Colorado Building Environments Sales Engineer Let s s Start with Air Air is Made up of Two Main Gases Nitrogen (77%) Oxygen (23%) If that is all there
More information