R4 Ventures LLC White Paper

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