SAN MATEO JAIL GEOTHERMAL FEASIBILITY...Geothermal Heat Pump systems have a number of potential...

PG&E’s Emerging Technologies Program ET Project # ET12PGE1501

SAN MATEO JAIL GEOTHERMAL FEASIBILITY

ET Project Number: ET12PGE1501

Project Mgr: Agatha Vaaler Pacific Gas & Electric Company Prepared By: Ryan Nelson, P.E. Dave Troup, P.E. Meline Engineering Corporation HOK 9343 Tech Center Drive #135 One Bush Street Sacramento, CA 95826 Suite 200

San Francisco, California

Issued: July 3, 2013

Copyright, 2013, Pacific Gas and Electric Company. All rights reserved.

i


ACKNOWLEDGEMENTS Pacific Gas and Electric Company’s Emerging Technologies Program is responsible for this project. It was developed as part of Pacific Gas and Electric Company’s Emerging Technology – Technology Assessment program under internal project number ET12PGE1501. HOK conducted this technology evaluation for Pacific Gas and Electric Company with overall guidance and management from Agatha Vaaler. For more information on this project, contact [email protected].

LEGAL NOTICE This report was prepared for Pacific Gas and Electric Company for use by its employees and agents. Neither Pacific Gas and Electric Company nor any of its employees and agents:

(1) makes any written or oral warranty, expressed or implied, including, but not limited to those concerning merchantability or fitness for a particular purpose;

(2) assumes any legal liability or responsibility for the accuracy, completeness, or usefulness of any information, apparatus, product, process, method, or policy contained herein; or

(3) represents that its use would not infringe any privately owned rights, including, but not limited to, patents, trademarks, or copyrights.

ii


ABBREVIATIONS AND ACRONYMS IPLV Integrated Part Load Value

NPLV Non Standard Part Load Value

GSHP Ground Source (Geothermal) Heat Pump

GHX Ground Heat Exchanger

DHW Domestic Hot Water

CUP Central Utility Plant

iii


CONTENTS EXECUTIVE SUMMARY ___________________________________________ 1 INTRODUCTION ________________________________________________ 3 TECHNOLOGY/PROJECT EVALUATION _______________________________ 4 TECHNICAL APPROACH/TEST METHODOLOGY ________________________ 5 RESULTS ______________________________________________________7 EVALUATIONS ________________________________________________ 8 RECOMMENDATIONS FOR FURTHER STUDY ____________________________ 9

APPENDICES:

1. Geothermal Site Plan Layout

2. System Sizing Results using GSHPCalc Software

3. System Cost Comparison

4. Multistack Water-to-Water Heat Pump Catalog (R410A)

5. Multistack Dedicated Heat Recovery Chiller Catalog (R134A)

6. Conventional Central Plant Energy Cost Calculations

7. Geothermal Central Plant Energy Cost Calculations

8. Building Heating and Cooling Loads

9. Formation Thermal Conductivity Test and Data Analysis

1


EXECUTIVE SUMMARY PROJECT GOAL The goal of this project was to compare a Geothermal Central Utility Plant (CUP) to a Conventional CUP, estimate the energy cost savings, and determine the simple payback for a correctional facility new construction project in San Mateo County, California.

Two different CUP systems for heating, cooling and domestic hot water were considered to serve the building, based on the architect/engineer HOK’s “100% Design Development” drawings and specifications dated February 14, 2013.

• The baseline system was a Conventional CUP as designed by HOK, utilizing water-cooled chillers with magnetic levitation (or MagLev) variable speed compressors, cooling towers, and natural gas condensing-type boilers to provide chilled water and heating water for space conditioning, and gas-fired storage-type domestic water heaters.

• The system compared to the baseline was a Centralized Geothermal Heat Pump system, utilizing large water-to-water heat pumps (ground source heat pumps) connected to a vertical Geothermal Ground Heat Exchanger (GHX), to provide chilled water and heating water for space conditioning and for domestic hot water. The Geothermal system uses the same chilled water, heating water, and domestic hot water distribution water piping external to the CUP as the baseline system. Note that the geothermal heat pump option is an all-electric solution. Even though domestic water heaters would be provided for auxiliary domestic hot water production, for the purposes of this study the domestic hot water is produced with no assistance from the natural gas supply available at the site.

• A potential third system is a Decentralized Geothermal Heat Pump system, utilizing many relatively small water-to-air heat pumps distributed throughout the building, each of which includes a small refrigerant compressor. A decentralized geothermal system was not part of this study, as discussed later in this report.

This study was conducted to estimate the installed costs and energy costs of natural gas and electricity for the two CUP systems, and to determine the simple payback of the Geothermal Heat Pump system for this facility and the applicability in general to similar facilities.

GEOTHERMAL SYSTEM BENEFITS Geothermal Heat Pump systems have a number of potential benefits:

• Potential strategy to achieve low-energy or net-zero-energy buildings in California due to the efficiency of the equipment in extended range operation of ground loop temperatures and the reduction of electricity use during peak demand periods.

• Lower operating costs from energy usage and peak demand reduction for building’s heating and cooling.

• Using energy recovery from the heat pump during cooling mode can significantly reduce the cost of domestic hot water heating.

2


• Reduces or eliminates outdoor equipment, such as cooling towers or condensing units, with a corresponding reduction in first cost and maintenance.

• Reduces or eliminates the need for on-site natural gas or fuel oil where there are concerns by the building owner. For projects on which natural gas is not needed for other purposes (such as cooking), this can reduce the infrastructure costs by eliminating the need for natural gas piping and utility connection.

PROJECT FINDINGS/RESULTS Comparison of the two systems showed a yearly operating savings of $35,579 for the Geothermal CUP compared to the Conventional CUP. The Geothermal CUP’s first cost was estimated to be $2.0 million more than the Conventional CUP. Most of this higher first cost is attributed to the geothermal ground bore field and mechanical equipment; however a significant portion is due to the challenges of permitting and installing the ground bore field at this particular project site. These costs include the drilling permit costs, prevailing wage/union contractor costs, and the cost of containment, removal and disposal of drilling fluid and spoils of the project site.

The result is a simple payback of 56 years, which is quite long. The client’s criterion for acceptance was a simple payback of approximately 15 years. It is anticipated that utility or government incentives may be able to lower the installed cost somewhat, but not sufficiently to make the central geothermal system economically feasible for this particular project.

PROJECT RECOMMENDATIONS The results of the study indicate that the project should utilize a conventional CUP, consisting of high efficiency chillers and boilers, in lieu of a central geothermal system.

A decentralized geothermal system was not part of the study, but it is believed that it could be more economically feasible for the project than a central system. This is discussed further in the Recommended Study section at the end of this report.

An additional recommendation stemming from this study is that the decision to review the feasibility of a geothermal system needs to be made very early in the design process, ideally at the Concept Design stage of an integrated design process.

3


INTRODUCTION BACKGROUND A geothermal heat pump, also known as a ground source heat pump or geo-exchange, taps into the thermal energy stored in the earth to provide energy-efficient heating, cooling, and domestic hot water for buildings. The technology uses the relatively constant temperature of the earth as the medium of heat exchange instead of outside air temperature.

Less than 10 feet beneath the surface of the earth, the ground remains at a relatively constant temperature. In winter this ground temperature is warmer than the outside air, and in summer the ground temperature is cooler than the outside air. A geothermal heat pump takes advantage of this temperature difference by exchanging heat with the earth through a ground heat exchanger. Ground heat exchangers may include closed loop, open loop, or open water/lake applications. A closed loop heat exchanger was considered for this project.

The technology has been in use since the 1940s, and is endorsed by the U.S. Department of Energy and the Environmental Protection Agency. Geothermal systems can be cost-effective for both new construction and retrofits. Lowered operating costs and longer service life make geothermal heat pump equipment a potentially more attractive choice than conventional heating and cooling equipment for many applications, including schools and institutional and government buildings.

A geothermal heat pump system includes three main components:

• Earth connection: Using the earth as a heat source/sink, a series of pipes, commonly called a ground heat exchanger or “loop,” is buried in the ground near the building to be conditioned. The loop can be installed either vertically or horizontally. It circulates a fluid (water, or a mixture of water and antifreeze) that absorbs heat from, or releases heat to, the surrounding soil depending on whether the fluid is colder or warmer than the soil.

• Heat pump subsystem: For heating, a geothermal heat pump removes the heat from the fluid in the earth connection, concentrates it, and then transfers it to the building. For cooling, the process is reversed.

• Heat distribution subsystem: o In a geothermal CUP system, water-to-water heat pumps produce chilled

water for cooling, hot water for heating, and preheat for domestic hot water. The cooling and heating water would be delivered through chilled water and heating water piping, similar to a conventional CUP arrangement.

o A more traditional application of the technology is the decentralized arrangement, in which individual water-to-air heat pumps are provided at the zone or room level, with the central utility plant simply consisting of a pair of ground loop pumps circulating the ground loop water between the ground heat exchanger and the heat pumps in a one-pipe or two-pipe configuration.

4


TECHNOLOGY/PROJECT EVALUATION Two different system technologies were evaluated and compared for overall energy and operational cost savings for a new prison construction project in San Mateo County, California. The project is approximately 260,000 GSF in size and includes 832 beds, support areas, kitchen, and laundry.

The baseline system is a conventional central utility plant (CUP), utilizing two water-cooled chillers with magnetic levitation (or MagLev) variable speed compressors, cooling towers, and two natural gas condensing-type boilers to provide chilled water and heating water for space conditioning, and gas-fired domestic water heaters. With the mass introduction of MagLev compressor technology, water-cooled chillers have drastically increased their operational efficiency, especially at part load. MagLev compressors are operated by variable speed drives and are capable of reducing capacity to 25% or less of their total capacity. At operating conditions below full capacity they can achieve efficiencies approaching twice that of full load efficiency. Due to the various part-load efficiencies of Maglev Chillers and the simultaneous heating and cooling operation of Geothermal Heat Pumps, a simple caparison of published equipment efficiencies was not sufficient and a more detailed analysis of the building systems integration and operation was required to compare the two systems.

As noted previously, the study compared only the equipment within the CUP for cost and efficiency. Everything outside the CUP was assumed to be the same. The chilled water design temperature for both systems was set to 44 deg F. For the baseline system the boilers and domestic water heaters were set to 140 deg F design temperature.

The system compared to the baseline is a Geothermal CUP that utilizes a ground heat exchanger for both heat rejection and heat extraction, as required by the demands of the connected heat pump equipment. The use of the ground as the heat source and heat sink for the building’s CUP results in a more constant temperature for the heat exchange, compared to either the condenser water provided by cooling towers, or the ambient air temperature used by air-cooled chillers or air-cooled condensers.

During the thermal conductivity testing (see report in Appendix 9) it was discovered that very competent sandstone rock resided between 222 and 242 feet below finished grade. Rather than slowing down the future drilling to work through these layers, a design decision was made to keep the ground loop depths to 225 feet. The result was good soil conductivity for the heat exchanger and a more reasonable drilling cost, than if an all in-ground solution was proposed to the client with deeper loops. The disadvantage is that a fluid cooler is required to meet the heat rejection requirements of the system during long periods of cooling. The schematic design provided for analysis was a “hybrid” with both ground heat exchanger and fluid cooler. Even for the moderate climate of San Mateo County, the overall system as designed is cooling-dominated. This is due to the solar gains, large occupant population, lighting, and heat-producing equipment such as computers.

As noted previously, since HOK’s design direction was to include a CUP, modular heat recovery pumps were selected to create chilled water and hot water. This allowed the building load to be transferred between the different heating and cooling systems. As heat is removed from the building during cooling operation it can be transferred to the heating hot water or domestic hot water systems. The water-to-water heat pumps also utilize the compressor heat in the water stream, using the heat that would have been otherwise wasted.

5


TECHNICAL APPROACH/TEST METHODOLOGY This study was conducted to determine the feasibility of a Geothermal CUP (geothermal heat pump system) versus the baseline design of a Conventional CUP (chillers and boilers), as described previously. To compare the two systems, the ground-source heat exchange portion of the Geothermal CUP had to be schematically designed and the energy consumption of the two systems calculated based on the annual building energy load profile developed by HOK.

The building design (as of design-development phase) was modeled into a building energy simulation software package. There are several energy modeling software packages available, and for this project HOK used the Virtual Environment software by Integrated Environmental Solutions Limited (IES-VE), which is a comprehensive building simulation software package that estimates the building energy use due to envelope loads, internal loads (due to lights, people, and equipment), and ventilation air loads. HOK used the output of the IES-VE energy modeling software to provide heating and cooling load profiles on an hourly basis (8,760 hours/year).

The domestic hot water (DHW) load was estimated at 30 gallons per day (GPD) per inmate on average. This includes the hot water for showers and sinks, but not for the kitchen or laundry, which are served by separate gas-fired water heaters. The estimate of the DHW usage was a topic of significant discussion by the project team. Reliable usage data is not available, and data varies from source to source; however, the 30 GPD per inmate value for DHW was utilized, and the energy required to produce the DHW was determined to be an important variable in the overall results of the project cost effectiveness.

Two geothermal test bore holes were drilled on the project site to determine the soil properties and to ascertain the drilling conditions. The results are included in Appendix 9.

While most building simulation software packages can model the conventional heating and cooling systems, it is the geothermal engineering subcontractor Meline Engineering’s experience that most of them do not efficiently or accurately model the relationship between the ground heat exchanger and the efficiency of the geothermal heat pumps. Geothermal water-cooled equipment experiences different operating temperatures at different times than conventional air cooled equipment. Most software programs mistakenly apply equipment efficiency algorithms and temperature data sets developed for air-cooled equipment to geothermal water-cooled equipment, resulting in lower simulated energy savings than in realized in actual real world operation. Therefore the building heating, cooling and DHW loads from HOK were used by Meline Engineering in the sizing of the GHX and in manually calculating the energy consumption of the two systems being analyzed. Once the building heating, cooling, and DHW loads were determined, they were entered into GSHPCalc, by Energy Information Services, a software package for designing GHX systems.

GSHPCalc is a software package that uses heating loads, cooling loads, DHW loads, Equivalent Full Load Hours, and soil properties and temperature to size a GHX. Meline Engineering used GSHPCalc to determine a preliminary geothermal heat exchanger (GHX) size. For this project, there is limited site area available for a GHX. Due to the project site constraints, a traditional all “in-ground” geothermal heat pump system that utilizes only the GHX for heating and cooling was not possible. The GHX was designed for the heating demand as it was smaller than the cooling demand. This resulted in a GHX that can provide the heating and DHW energy for the building but not all of the cooling. To supplement the heat rejection required for cooling, a fluid cooler is recommended to reject the surplus heat that cannot be absorbed by the GHX. (See Appendix 2 for the GSHPCalc results.) The

6


resulting arrangement is referred to as a Hybrid Geothermal System. Once the preliminary design for the Hybrid Geothermal System was complete, the building loads were used and manual spreadsheet calculations were performed by Meline to determine the energy consumption of the two systems.

The energy consumption for each system was calculated by using average monthly heating and cooling loads and applying the published equipment efficiency. The Conventional CUP operates as required to meet the loads. The MagLev Chillers experience a condenser water temperature from the cooling tower operation that varies with the ambient wet bulb temperature. The Geothermal CUP efficiency varies over the year due to the heat rejected to and extracted from the GHX and the supplemental operation of the fluid cooler. The equipment efficiencies were applied at the anticipated condenser water temperatures throughout the year. A large portion of the energy savings was due to using waste heat to preheat the DHW system. It is anticipated that up to 45% of the DHW preheat load would be done simultaneously with cooling and be a byproduct of the cooling operation. Once the energy consumption was calculated, the PG&E natural gas and electric rates for the project were then applied to the energy consumption of both systems to determine the operating cost in dollars.

The following PG&E utility rates were used:

• Electricity

o Summer Off Peak $0.08 per kWh

o Summer Partial Peak $0.10 per kWh

o Summer Peak $0.14 per kWh

o Winter Off Peak $0.07 per kWh

o Winter Partial Peak $0.08 per kWh

• Natural Gas

o $0.82 per therm

The estimated energy costs for the Conventional System are given in Appendix 6, and for the Geothermal System in Appendix 7. The first costs of the two systems were estimated by Contractors. Appendix 3 shows a summary of the estimated energy costs for each system, the difference in first costs between the two systems, and the estimated simple payback.

7


RESULTS Conventional Central Utility Plant: 2 Smardt chillers @ 260 tons

1 cooling tower with 2 cells @ 780 GPM each

2 condensing boilers @ 1,500,000 Btu/hr each

Geothermal Central Utility Plant: 11 Modular Heat Pumps @ 50 tons

1 fluid cooler @ 235 tons

Geothermal Bore Field:

250 bores, 225 feet deep, 15 feet on center spacing.

System Comparison As stated in Appendix 3, the geothermal system is estimated to save approximately $35,579 in energy costs annually, but has a higher first cost of about $2.0 million. This results in a simple payback of approximately 56 years.

8


EVALUATIONS

Comparison of the two systems showed a yearly operating savings of $35,579 for the Geothermal central utility plant (CUP) compared to the Conventional CUP. The Geothermal CUP’s first cost was estimated to be $2.0 million more than the Conventional CUP. Most of this higher first cost is attributed to the geothermal ground bore field and mechanical equipment; however a significant portion is due to the challenges of permitting and installing the ground bore field at this particular project site. These costs include the drilling permit costs, prevailing wage/union contractor costs, and the cost of containment, removal and disposal of drilling fluid and spoils of the project site.

The ideal geothermal design would have balanced heating and cooling loads so that the size of the ground loop is balanced for heating and cooling. However, in this climactic region it is common that a building has a higher annual cooling demand than heating demand. This unbalanced load results in a ground heat exchanger sized for the cooling requirements that would be larger than that sized for the heating requirements. For this project the geothermal heat exchanger (GHX) would require approximately 450 to 500 boreholes at 15 feet on center spacing for cooling, and 250 to 300 boreholes at 15 feet on center for heating, based on a 225-foot depth. 450 boreholes at 15 feet on center would require a site area over 100,000 square feet, which is larger than that available at the site. Additionally, test bores drilled on site indicated competent rock was encountered at depths of 222 and 242 feet, which limited the borehole depth to approximately 225 feet to avoid the added cost of drilling through substantial amounts of sandstone. Therefore for this project it is recommended that the GHX be sized for the heating demand, and a fluid cooler be provided to handle the balance of the building cooling needs, resulting in a "Hybrid" system. Due to the anticipated heating and cooling demands and the GHX size constraints on site, the recommended GHX size is 250 boreholes, 225 feet deep, at 15 feet on center (requiring approximately 56,250 sq. ft.) with a 235-ton fluid cooler to supplement the cooling operation. The required site area is shown in the site plan in Appendix 1.

The result is a simple payback of 56 years, which is quite long. The client’s criterion for acceptance was in the range of 15 years. It is anticipated that utility or government incentives may be able to lower the installed cost somewhat, but not sufficiently to make the central geothermal system economically feasible for this particular project.

9


RECOMMENDATIONS FOR FURTHER STUDY

The following items were beyond the scope of this feasibility study, and could be explored in the future:

• Study the possibility of using a decentralized geothermal heat pump system, consisting of many relatively small water-to-air heat pumps distributed throughout the building. The installed cost and energy cost of a decentralized system could be less than a centralized system, although a decentralized system has different maintenance requirements. The heat pumps of a decentralized system are small higher-efficiency “packaged” equipment, with simple thermostatic controls at each zone or room, reducing the cost associated with building system controls. The piping distribution system would consist of one pair of pipes (2-pipe system), instead of a pair of chilled water pipes and a pair of heating water pipes (4-pipe system). Pump energy would be reduced.

A decentralized system was not studied in this report for the following reasons. First, the County had requested that the main HVAC equipment be centralized in a CUP for operational and maintenance reasons. The second reason has to do with the project’s design schedule. Due to several factors, the decision to study a geothermal system in depth was not made until the project was near the end of design development phase, and the project design was based on a central HVAC system. A decentralized system would have required a complete mechanical redesign, which was not feasible given the stage of the project design.

• Monitor and evaluate recent applications of geothermal heat pump systems in the region to gather system performance data and compare it to simulated data. This could include several community college projects such as Ohlone College in Fremont, San Francisco City College, and College of Marin. One of the challenges with the geothermal technology is documenting the true operating efficiency of the installed systems.

• Study the impacts of the regional location of the project. There are factors that may make a geothermal system less economically feasible in California compared to other regions of the country.

o Electric rates: A geothermal system, by its nature, uses more electricity and less natural gas than does a conventional system. In general this would make its use less economically attractive in a region like California where electricity rates are more expensive.

o Natural gas rates: Currently natural gas rates are somewhat low, and are generally projected to remain that way for some time in the future. In general this makes the use of high-efficiency gas-fired boilers economically attractive. Geothermal heat pump systems are much more practically applied in areas where natural gas is not readily available.

o Climate: An advantage of using a geothermal system is that the ground temperature is relatively stable for heat rejection during the cooling season, and energy efficiency is achieved if the water temperature produced by the geothermal field is cooler than the condenser water produced by conventional cooling towers. This would more likely be the case in geographical regions with hot, humid summers like the central and eastern US. However the Bay Area and the western US are comparatively cooler and less humid, resulting

10


in cooler condenser water produced by the cooling towers, which reduces the advantage of a geothermal system.

o Local permitting and regulatory requirements: Educate regulators and the general public on the “cost of doing business” in California. Include topics such as ground water protection, storm water, brownfields, and education on the differences between a ground loop system and water well.

• Study the technology as an approach to meeting California’s Net Zero Energy goals for non-residential buildings by year 2030.

• Study the impact of a possible preferential electric rate structure for geothermal heat pumps.

PG&E’s Emerging Technologies Program


Appendix 1

Geothermal Site Plan Layout

250 wells at 15-feet spacing requiresapproximately 56,250 sq.ft. of site area.



Appendix 2

GSHPCalc GHX Sizing Results Data Sheet



Appendix 3

System Cost Comparison

Appendix 3

System Cost Comparison Annual Energy Costs

1. Conventional Plant (from Appendix 6)

a. Domestic hot water $40,327/year b. Chillers and boilers 67,903 c. Condenser water pump 1,843 d. Cooling Towers 2,806

Total Conventional Plant energy cost $112,879/year

2. Geothermal Plant (from Appendix 7)

a. Domestic hot water $11,401/year b. Heat pumps 61,477 c. Condenser water pump 2,387 d. Cooling tower 2,035

Total Geothermal Plant energy cost $77,300/year Total Difference in Energy Costs $35,579/year

First Costs

The difference in first costs between the conventional system and geothermal central plant system is estimated as follows:

1. Cost of drilling boreholes, installing loops, and grouting $1,354,000

(estimated by Pitcher Drilling) 2. Cost of loop header piping extended to the CUP 510,000 (estimated by Air Connection) 3. Cost difference of mechanical work within the CUP 193,000

(estimated by mechanical contractor) a. Delete chillers (389,000) b. Delete boilers (141,000) c. Delete open cooling towers (145,000) d. Delete labor and misc. trim (72,000) e. Add heat pumps 765,000 f. Add closer fluid cooler 175,000

4. Electrical and controls credit within the CUP (32,000)

Total Difference in First Costs $2,025,000

$2,025,000

Simple payback = $35,579/year = 57 Years



Appendix 4

Multistack Water-To-Water Heat Pump Catalogue (410A)

Water Cooled ChillerProduct Data Catalog

For chillers with R-410A refrigerant

sm

For Modules:MS010XC_W-410A, MS015XC_W-410A, MS020XC_W-410A, MS030XC_W-410A, MS050XC_W-410A, MS070XC_W-410A, MS085XC_W-410A

Water Cooled Chiller Catalog

2

TAble oF ConTenTs

Made in the USA

Product Introduction .................................................................................................................................................. 3

Performance Data ...................................................................................................................................................... 4

Pressure Drop Tables................................................................................................................................................... 6

Selection Data ............................................................................................................................................................ 7

Electrical Data ............................................................................................................................................................ 8

Chiller Drawing........................................................................................................................................................... 9

Sample Piping Schematics ......................................................................................................................................... 10

General Data Table ................................................................................................................................................... 12

Controller Schematics ............................................................................................................................................... 13

Mechanical Specifications ......................................................................................................................................... 14

MoDEl NuMbEr NoMENClATurEExisting MS 50 X 1 H 1 W 0 R-410A

New MS 050 X N 1 H 1 A 0 A A -410A

Module Nominal Capacity (10 - 160 tons)

AHRI Certified (C - certified, N - Not certified)

Voltage3

Application4

Evaporator5

Series

Compressor Type1

Configuration2

Module Number (1 - single, 2 - multiple)

AHRI Version - if applicable

Condenser6Refrigerant

1 B: Bristol, C: Trane Cornerstone, R: Bitzer Screw, S: Trane Scroll, T: Danfoss Turbocor, Z: Copeland scroll (old elec), X: Copeland Scroll (ZP), A: Copeland Scroll (ZR)2 1- Standard, 2- Total access, 3 - Evap extended headers, 4 - Cond extended headers, 5 - Both extended headers, V - others3 A - 208/3/60, L - 230/3/60, H - 460/3/60, C - 575/3/60, D - 200/3/50, E - 400/3/50, F - 380/3/60, S - 220/230/1/60, V - other4 C - Single module temp controller, A-Air Cooled split, D - Cond unit, F - Fluid cooler (high temp),H - Heat recovery, R - Heat pump, W - Water cooled5 A - Brazed SS, B - Brazed SMO, C- S&T copper, D - S&T cu-Ni, V - Other6 A - Brazed SS, B - Brazed SMO, C- S&T copper, D - S&T cu-Ni, E - Double wall brazed, V - Other


33

HIGHlY DePenDAble• Multiple independent systems for redundancy• Comprehensive computer monitoring of operations• Automatic diagnostic recording of fault conditions• Rotates lead compressor every 24 hours

sIMPle To oPeRATe• Large LCD screen displays information in plain English• Simple keypad provides control of unit operations

eAsY To InsTAll• Compact modules fit through standard doorways and into elevators• Modules interconnect easily and quickly• All refrigeration systems are factory charged and run tested

PRoGRAMMAble loGIC ConTRolleR (PlC) sYsTeM

• Manual switch allows redundancy control as each module has a processor allowing it to run even if master controller fails

• Optional Fail-To-Run software• Display at each module• Remote display option

DesIGn FleXIbIlITY• Wide array of module combinations• Install only the capacity required at the time

sIMPle To seRVICe• Service can often be performed on a convenient,

non-emergency basis• Most components are standard, off the shelf design

BackFront Side View

Chilled Water

Busbar Duct

Control Box

Compressors

Condenser Water

PRoDUCT InTRoDUCTIon


44

All performance data is based on a 10°F chilled water temperature drop through the evaporator and condenser. For total chiller performance multiply above output (TONS) and input (KW) by the number of modules. For selection procedures see selection software at www.multistack.com.

SINGLE MODULE ENTERING CONDENSER WATER TEMPERATURE

MS010X_W 75°F 80°F 85°F 90°F 95°FLeaving Chilled

Water °FOutput

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW KW/Ton EER

40°F 10.3 7.8 0.757 15.8 10.1 8.3 0.822 14.6 9.8 8.7 0.888 13.5 9.5 9.2 0.986 12.4 9.2 9.7 1.054 11.342°F 10.8 7.8 0.722 16.5 10.5 8.2 0.781 15.3 10.2 8.7 0.853 14.1 9.9 9.2 0.929 12.9 9.6 9.7 1.010 11.944°F 11.2 7.8 0.696 17.3 10.9 8.2 0.752 16.0 10.6 8.7 0.821 14.7 10.3 9.1 0.883 13.5 10.0 9.6 0.960 12.445°F 11.4 7.8 0.684 17.6 11.1 8.2 0.739 16.3 10.8 8.6 0.796 15.0 10.5 9.1 0.867 13.8 10.2 9.6 0.941 12.746°F 11.6 7.7 0.664 18.0 11.3 8.2 0.726 16.7 11.0 8.6 0.782 15.4 10.7 9.1 0.850 14.1 10.4 9.6 0.923 13.048°F 12.1 7.7 0.636 18.8 11.8 8.1 0.686 17.4 11.5 8.6 0.748 16.1 11.2 9.1 0.813 14.8 10.8 9.6 0.889 13.650°F 12.6 7.7 0.611 19.6 12.3 8.1 0.659 18.1 11.9 8.5 0.714 11.9 11.6 9.0 0.776 15.4 11.2 9.5 0.848 14.2


Water °FOutput

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output


40°F 17.4 12.1 0.695 17.2 17.0 12.9 0.759 15.8 16.5 13.6 0.824 14.5 16.0 14.4 0.900 13.3 15.6 15.3 0.981 12.242°F 18.1 12.1 0.669 17.9 17.6 12.9 0.733 16.4 17.2 13.6 0.791 15.1 16.7 14.4 0.862 13.9 16.2 15.3 0.944 12.744°F 18.8 12.2 0.649 18.5 18.3 12.9 0.705 17.1 17.8 13.7 0.770 15.7 17.3 14.5 0.838 14.5 16.8 15.3 0.911 13.245°F 19.2 12.2 0.635 18.9 18.7 12.9 0.690 17.4 18.2 13.7 0.753 16.0 17.7 14.5 0.819 14.7 17.2 15.3 0.890 13.446°F 19.6 12.2 0.622 19.2 19.0 12.9 0.679 17.7 18.5 13.7 0.741 16.3 18.0 14.5 0.806 14.9 17.5 15.3 0.874 13.748°F 20.3 12.2 0.601 19.9 19.8 12.9 0.652 18.3 19.3 13.7 0.710 16.9 18.7 14.5 0.775 14.5 18.2 15.3 0.841 15.350°F 21.1 12.3 0.583 20.6 20.5 13.0 0.634 19.0 20.0 13.7 0.685 17.5 19.4 14.5 0.747 16.1 18.9 15.4 0.815 14.7


Water °FOutput

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output


40°F 20.9 14.4 0.689 17.4 20.3 15.0 0.739 16.3 19.8 15.8 0.798 15.0 19.1 16.6 0.869 13.8 18.5 17.6 0.951 12.642°F 21.6 14.4 0.667 18.0 21.1 15.0 0.711 16.8 20.5 15.8 0.771 15.6 19.9 16.6 0.834 14.4 19.3 17.6 0.912 13.144°F 22.4 14.4 0.643 18.6 21.9 15.1 0.689 17.4 21.3 15.8 0.742 16.2 20.7 16.7 0.807 14.9 20.0 17.6 0.880 13.645°F 22.8 14.4 0.632 19.0 22.3 15.1 0.677 17.7 21.7 15.8 0.728 16.5 21.1 16.7 0.791 15.2 20.4 17.6 0.863 13.946°F 23.2 14.5 0.625 19.3 22.7 15.1 0.665 18.0 22.1 15.8 0.715 16.7 21.5 16.7 0.777 15.5 20.8 17.6 0.846 14.248°F 24.0 14.5 0.604 19.9 23.5 15.1 0.643 18.6 22.9 15.9 0.694 17.3 22.3 16.7 0.749 16.0 21.6 17.7 0.819 14.750°F 24.9 14.5 0.582 20.6 24.3 15.2 0.626 19.3 23.8 15.9 0.668 17.9 23.1 16.7 0.723 16.6 22.5 17.7 0.787 15.2


Water °FOutput

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output


40°F 31.0 21.6 0.697 17.2 30.3 22.6 0.746 16.1 29.5 23.7 0.803 14.9 28.7 24.9 0.868 13.8 27.8 26.2 0.942 12.742°F 32.2 21.8 0.677 17.8 31.5 22.8 0.724 16.6 30.7 23.8 0.775 15.4 29.8 25.0 0.839 14.3 28.9 26.3 0.910 13.244°F 33.4 21.9 0.656 18.3 32.7 22.9 0.700 17.1 31.8 24.0 0.755 15.9 31.0 25.1 0.810 14.8 30.1 26.4 0.877 13.745°F 34.1 22.0 0.645 18.6 33.3 23.0 0.691 17.4 32.4 24.0 0.741 16.2 31.6 25.2 0.797 15.0 30.6 26.5 0.866 13.946°F 34.7 22.1 0.637 18.9 33.9 23.0 0.678 17.6 33.0 24.1 0.730 16.5 32.2 25.3 0.786 15.3 31.2 26.5 0.849 14.148°F 36.0 22.3 0.619 19.4 35.2 23.2 0.659 18.2 34.3 24.3 0.708 17.0 33.4 25.4 0.760 15.8 32.4 26.6 0.821 14.650°F 37.3 22.5 0.603 19.9 36.4 23.4 0.643 18.7 35.5 24.4 0.687 17.5 34.6 25.5 0.737 16.3 33.6 26.8 0.798 15.1

PeRFoRMAnCe DATA


55

All performance data is based on a 10°F chilled water temperature drop through the evaporator and condenser. For total chiller performance multiply above output (TONS) and input (KW) by the number of modules. For selection procedures see selection software at www.multistack.com.

SINGLE MODULE ENTERING CONDENSER WATER TEMPERATURE


Water °FOutput

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output


40°F 50.3 34.7 0.690 17.4 49.0 36.4 0.743 16.2 47.6 38.2 0.803 15.0 46.2 40.2 0.870 13.8 44.8 42.4 0.946 12.742°F 52.3 34.8 0.665 18.0 50.9 36.5 0.717 16.7 49.5 38.4 0.776 15.5 48.1 40.3 0.838 14.3 46.6 42.5 0.912 13.244°F 54.4 35.0 0.643 18.6 52.9 36.7 0.694 17.3 51.5 38.5 0.748 16.0 50.0 40.5 0.810 14.8 48.4 42.6 0.880 13.645°F 55.4 35.1 0.634 18.9 54.0 36.8 0.681 17.6 52.5 38.6 0.735 16.3 51.0 40.5 0.794 15.1 49.4 42.7 0.864 13.946°F 56.5 35.2 0.623 19.3 55.0 36.8 0.669 17.9 53.5 38.6 0.721 16.6 52.0 40.6 0.781 15.4 50.4 42.7 0.847 14.148°F 58.6 35.4 0.604 19.9 57.1 37.0 0.648 18.5 55.6 38.8 0.698 17.2 54.0 40.7 0.754 15.9 52.3 42.9 0.820 14.750°F 60.9 35.6 0.585 20.6 59.3 37.2 0.627 19.2 57.7 38.9 0.674 17.8 56.1 40.9 0.729 16.5 54.4 43.0 0.790 15.2


Water °FOutput

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output


40°F 65.8 44.9 0.682 17.6 64.1 47.1 0.735 16.3 62.4 49.5 0.793 15.1 60.6 52.1 0.860 14.0 58.8 54.8 0.932 12.942°F 68.4 45.1 0.659 18.2 66.6 47.3 0.710 16.9 64.8 49.7 0.767 15.7 63.0 52.3 0.830 14.5 61.1 55.0 0.900 13.344°F 71.0 45.4 0.639 18.8 69.2 47.6 0.688 17.5 67.4 49.9 0.740 16.2 65.5 52.5 0.802 15.0 63.5 55.3 0.871 13.845°F 72.4 45.6 0.630 19.1 70.6 47.7 0.676 17.7 68.7 50.1 0.729 16.5 66.7 52.6 0.789 15.2 64.7 55.4 0.856 14.046°F 73.8 45.7 0.619 19.4 71.9 47.9 0.666 18.0 70.0 50.2 0.717 16.7 68.0 52.7 0.775 15.5 66.0 55.5 0.841 14.348°F 76.6 46.0 0.601 20.0 74.6 48.1 0.645 18.6 72.6 50.5 0.696 17.3 70.6 53.0 0.751 16.0 68.5 55.7 0.813 14.750°F 79.5 46.4 0.584 20.6 77.4 48.5 0.627 19.2 75.4 50.7 0.672 17.8 73.2 53.3 0.728 16.5 71.1 56.0 0.788 15.2


Water °FOutput

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output

TonsInput KW

KW/Ton EER Output


40°F 81.0 56.8 0.701 17.1 79.2 59.2 0.747 16.1 77.2 61.9 0.802 15.0 75.1 65.0 0.866 13.9 73.0 68.3 0.936 12.842°F 84.2 56.9 0.676 17.7 82.3 59.3 0.721 16.7 80.3 62.0 0.772 15.5 78.2 65.0 0.831 14.4 76.0 68.3 0.899 13.344°F 87.5 57.1 0.653 18.4 85.6 59.4 0.694 17.3 83.5 62.1 0.744 16.1 81.4 65.1 0.800 15.0 79.1 68.4 0.865 13.945°F 89.2 57.3 0.642 18.7 87.3 59.5 0.682 17.6 85.2 62.2 0.730 16.4 83.0 65.1 0.784 15.3 80.7 68.4 0.848 14.246°F 90.9 57.4 0.631 19.0 88.9 59.6 0.670 17.9 86.8 62.2 0.717 16.7 84.6 65.2 0.771 15.6 82.3 68.4 0.831 14.448°F 94.5 57.6 0.610 19.7 92.4 59.8 0.647 18.5 90.2 62.4 0.692 17.4 88.0 65.3 0.742 16.2 85.6 68.5 0.800 15.050°F 98.1 57.9 0.590 20.3 96.0 60.0 0.625 19.2 93.7 62.5 0.667 18.0 91.4 65.4 0.716 16.8 88.9 68.6 0.772 15.6

PeRFoRMAnCe DATA


66

Figure 2. Water Cooled Units

WATEr FloW - GPM PEr MoDulE

PrES

SurE

Dro

P - F

T oF W

ATEr

use Curve ForA: MS010X_W, MS015X_W, MS020X_W Evaporatorb: MS010X_W, MS015X_W, MS020X_W CondenserC: MS030X_W EvaporatorD: MS030X_W Condenser

E: MS050X_W EvaporatorF: MS050X_W CondenserG: MS070X_W EvaporatorH: MS070X_W CondenserCall Factory for MS085X_W

20 30 40 50 60 70 80 90 100

200

300

400

500

600

50

40

30

20

10987

6

5

4

3

2

PRessURe DRoP TAbles


77

selectionTo select a MULTISTACK Water Cooled chiller, the following information is required:1. Load in tons of refrigeration. 2. Chilled water temperature drop. 3. Leaving chilled water temperature. 4. Entering condenser water temperature.

Capacity Tables (contact factory)Capacity tables are based on a 10° F temperature drop through the evaporator. For other than 10 °F temperature drop, apply the respective performance adjustment factors from.

Water Flow RatesEvaporator water flow can be determined as follows: GPM = (24) (TONS)/TEMPERATURE DROP (°F)Condenser water flow should always be determined using a 10 °F temperature rise as follows: GPM = 2.4 [TONS + (0.285)(Compressor KW)]

Waterside Pressure DropEvaporator and condenser waterside pressure drops are provided in chart on the previous page. To use this chart, divide the total chilled water GPM by the number of modules in the chiller.

Chilled Water selection example (Assumes MS050X Modules)System load = 290 TONS. Chilled water drop of 12°F. Leaving chilled water temperature of 45°F. Entering condenser water temperature of 85°F

1. Use the adjustment factor for tons to convert tons to 10°F at equivalent for use with capacity tables.

TONS = 290/1.008 = 287.7 TONS2. Select the appropriate performance table based on module to be used.

Read the CAPACITY and KW of a single module at the water temperature specified.

CAPACITY = 52.5 TONS, KW = 38.63. To find the number of modules required, divide equivalent tons required at

10°F temperature drop by single module capacity from table:MODULES REQUIRED = 287.7/52.5 = 6 modulesCHILLER CAPACITY = (52.5)(6) = 315 TONSPOWER INPUT = (38.6)(6) = 231.6KW

4. At 12°F evaporator temperature drop, applying the performance adjustment factors result in:

TONS = (315)(1.008) = 317.52 tons vs. system load5. To determine evaporator and condenser water pressure drops,

first determine GPMEvaporator GPM = (24)(317.52)/12 = 635.04Condenser GPM = 2.4[317.52 + (.285)(231.6)] = 920.5 GPM

6. With a 6 module chiller, evaporator and condenser pressure drops are read for as follows:

Evaporator = GPM/modules = 636/6 = 106Pressure Drop = 12 feetCondenser = GPM/modules = 921/6 = 154Pressure Drop = 13 feet

low Temperature operation with GlycolEthylene Glycol adjustment factors should be used to adjust performance depending on the percent of glycol used in the evaporator circuit. The factors in Table 3 are based on a 10°F change in fluid temperature through the evaporators.Capacity and KW should be obtained by extrapolating no more than 10°F from the lowest leaving chilled water temperature shown in the capacity tables.MULTISTACK should be contacted if leaving glycol temperatures below 32°F are required.Adjustment factors for Propylene Glycol are used in the same way given in the following example.

ethylene Glycol selection example (Assumes MS030X Modules)Determine CAPACITY, GPM, Pressure Drop and KW for a MS-30X6 module cooling 30% Ethylene Glycol from 45°F to 35°F, with an entering condensing temperature of 85°F and 100% water. 1. By extrapolating from the Performance Tables:

CAPACITY: 26.5 tons; KW: 23.22. Evaporator water flow and pressure drops are determined for water as in

the previous example. Evaporator GPM = (24)(26.5)/10 = 63.6 Evaporator Pressure Drop = 8.2 feet

3. To convert performance for water to performance with Ethylene Glycol read adjustment factors at 30% Glycol. CAPACITY Adjustment: 0.94 KW Adjustment: 0.99 Evaporator GPM Adjustment: 1.10 Pressure Drop Adjustment: 1.22

4. Calculate performance with 30% Ethylene Glycol by multiplying performance for water by adjustment factors. CAPACITY: (26.5)(0.94) = 24.91 TONS KW: (23.2)(0.99) = 22.97KW GPM: (63.6)(1.10) = 69.96 GPM Pressure Drop: (8.2)(1.22) = 10.01 ft of water

5. To determine condenser water pressure drops, first determine GPM. Condenser GPM = 2.4[24.91+(0.285)(22.97)] = 75.5 GPM

6. Condenser pressure drops are read as follows: Condenser Pressure Drop = 7.5 feet

For adjustment factors, contact Multistack.

seleCTIon DATA


88

1.Compressor Rated Load Amps (RLA) and Locked Rotor Amps (LRA) Data: RLA/LRA

external Input/output Connections system Wire & Fuse sizing specifications(Applicable codes may require different wire sizing)

VolTAGE 208 230 460 575MS010X 15/123 14/123 6.8/62 5.5/50MS015X 25.3/225 22.8/225 11.4/114 8.8/80MS020X 29.8/239 27/239 13.5/125 10.8/80MS030X 49.8/340 45/340 22.5/173 18/132MS050X 67/605 60/605 30/272 24/215MS070X 89/599 80/599 40/310 32/239MS085X N/A N/A 51/368 N/A

2. Wiring Sizing: Minimum Circuit Ampacity (MCA) MCA = (1.25 x RLA1*) + RLA2 + RLA3

MCA 3 CoNDuCTorS1 CoNDuIT

6 CoNDuCTorS2 CoNDuIT

50 8 —65 6 —85 4 —

100 3 —115 2 —130 1 —150 1/0 —175 2/0 —200 3/0 —230 4/0 —255 250 MCM —285 300 MCM 1/0300 — 2/0350 — 3/0400 — 4/0460 — 4/0500 — 250 MCM

3. Fuse Sizing: Maximum Fuse (MF), Type RK5 FuseMF= (2.25 x RLA1*) + RLA2 + RLA3 Where the MF does not equal a standard size fuse, the next larger size should be used.

4. NoTES:A.*RLA1 = RLA of the largest compressor in the system. RLA2 & RLA3 = RLA of the other compressors in the system.B. The total system Minimum Circuit Ampacity (aMCA) shall not exceed 500A.C. Wire sizing is based on the Nat. Electr. Code (NEC) rating for 75°C copper wire, with 3 wires per conduit.D. Wiring Distance from branch circuit shall not exceed 100ft.

eleCTRICAl DATA


99

end View

CHIlleR DRAWInG


1010

Condenser schematic with Head Pressure Control

TOCOOLINGTOWER

FROM COOLING TOWER

FLOW SWITCHSUPPLIED AND INSTALLED BY OTHERS

3-WAY CONDENSER BY-PASS VALVESUPPLIED AND INSTALLED IN BUILDING BY OTHERS

CONDENSER ISOLATION VALVESSUPPLIED AND INSTALLED BY OTHERS

1/2” SENSOR POCKETS SUPPLIED BY MULTISTACKInstallation of sensor pocket (weld-a-let) is recommended at 30” from end of chiller, supplied and installed by others

PRESSURE TAPSSUPPLIED AND INSTALLED BY MULTISTACK

MULTISTACKCHILLER

STANDARD “Y” STRAINERSUPPLIED AND INSTALLED BY OTHERS.

NOTE: SELECT STRAINER MESH BASED ON WATER QUALITY

STRAINER ISOLATION VALVESUPPLIED AND INSTALLED

BY OTHERS

CONDENSER WATER PUMPSUPPLIED AND INSTALLED BY OTHERS

SP

SP

FS

Required Chilled Water Piping


1/2” SENSOR POCKETS SUPPLIED BY MULTISTACKInstallation of sensor pocket (weld-a let) is recommended at 30” from end of chiller, supplied and installed by others

SP

SP

STANDARD “Y” STRAINERSUPPLIED AND INSTALLED BY OTHERS.*NOTE: SELECT STRAINER BASED ON WATER QUALITY

STRAINER ISOLATION VALVESUPPLIED AND INSTALLED BY OTHERS

CHILLED WATER PUMPSUPPLIED AND INSTALLED BY OTHERS

TOBUILDING LOAD

FROM BUILDING LOAD


CHILLER ISOLATION VALVESSUPPLIED AND INSTALLED BY OTHERS

MULTISTACKCHILLER

FS

sCHeMATICs


1111

Chiller Installation Dimensions

Plan View

Front elevation View – Chiller length

42”REQUIRED

42” RECOMMENDED

28”12” MIN

32”

RECO

MM

ENDE

D

NoTE: THE MAIN PoWEr CoNNECTIoN For A SINGlE MoDulE CHIllEr IS loCATED INSIDE MoDulE.

sCHeMATICs


1212

MS010X MS015X MS020X MS030X MS050X MS070X MS085XCompressor Type Scroll Scroll Scroll Scroll Scroll Scroll ScrollDry Weight (lbs. each) 89 135 135 146 353 390 441

Normal Capacity (tons each) 5 7.5 10 15 25 30 40Quantity 2 2 2 2 2 2 2Oil Charge (pints per compressor) 3.5 6.9 6.9 6.9 14.4 13.3 13.3

Evaporator (Brazed Plate) Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed PlateWeight (lbs. each) 80 80 80 105 180 243 292Water Storage (gallons each) 1.9 1.9 1.9 2.9 4.8 7.3 10.1Circuit Configuration Dual Dual Dual Dual Dual Dual DualQuantity 1 1 1 1 1 1 1Header System (gallons) 7 7 7 7 7 7 14

Condenser Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed PlateWeight (lbs. each) 90 90 90 135 220 313 340Water Storage (gal. each) 2.4 2.4 2.4 4.1 6.6 10.1 12.3Circuit Configuration Dual Dual Dual Dual Dual Dual DualQuantity 1 1 1 1 1 1 1Header System (gallons) 7 7 7 7 7 7 14

refrigerant Type R410A R410A R410A R410A R410A R410A R410ACharge (lbs./circuit) 8 8 8 12 18 24 28Number of Circuits 2 2 2 2 2 2 2

operating Weight (lbs.) 1155 1200 1200 1625 2000 2200 2550Shipping Weight (lbs.) 995 1040 1040 1450 1730 1900 2100

GeneRAl TAble


1313

ENT. CHILLED WATER TEMP.

LVG. CHILLED WATER TEMP

VERIFY CHILLED WATER FLOW

ENT. COND. WATER TEMP

LVG. COND. WATER TEMP

VERIFY COND. WATER FLOW

CUSTOMER INTERLOCKS

CHILLED WATER RESET INPUT/ LOAD LIMIT RESET INPUT

CHILLED WATER PUMP OPERATION

CONDENSER WATER PUMP OPERATION

FAULT NOTIFICATION

FULL LOAD RELAY

MULTIFLUSH OUTPUT

Chiller Data

MoDUle ConTRol PAnel

Module Data

DATA FroM rEFrIGErATIoN SYSTEM “b”

HP TRANSDUCER

HIGH PRESSURE SWITCH

LP TRANSDUCER

COMP. MOTOR PROTECTION

SUCTION TEMPERATURE


CIRCUIT FAULT CONDITION

HIGH VolTAGE CoNTrol PANElCIRCUIT “A” COMPRESSOR CONTACTOR

CIRCUIT “B” COMPRESSOR CONTACTOR

bUIlDInG AUToMATIon solUTIons

InTeRoPeRAbIlITY PoRTAls

MASTEr CoNTrolCan stage a maximum of 15 modules

(30 compressors)

REMOTE DISPLAY (optional)

bACneT™

• MSTP • ETHERNET• TCP/IP

MoDbUs™ (RTU)

snMP PRoToCol

lonMARK™

rS485 Serial Card

PCo Net rS485 Interface board

PCo Web Ethernet Interface board

DATA FroM rEFrIGErATIoN SYSTEM “A”

HP TRANSDUCER


LP TRANSDUCER


SUCTION TEMPERATURE



ConTRolleR sCHeMATICs


1414

GeneralModules are ETL listed in accordance with UL standard 1995 and are CSA certified per standard C22.2 #236 on all heat exchangers.

Modules ship wired and charged with refrigerant and oil, ready for installation. All modules are factory run tested prior to shipment.

Compressors, heat exchangers, piping and controls are mounted on a heavy gauge steel frame. Electrical controls, contactors, and relays for each module, are mounted within that module.

Chilled and Condensed Water MainsEach module includes supply and return mains for both chilled and condensed water. Grooved end connections are provided for interconnection to 6” US standard (6.625 outside diameter) customer piping with victaulic type couplings. Standard units include 30 mesh in-line strainers in the condenser and evaporator supply headers. Also standard is the Multiflush™ automatic debris removal system.

evaporators and CondensersEach evaporator and condenser is a brazed plate heat exchanger constructed of 316 stainless steel; designed, tested and stamped for a 650 psig working pressure.

CompressorsEach module contains two separate refrigeration systems. The hermetic compressor in each system is mounted to the frame with rubber-in-shear isolators. Each system also includes high discharge pressure and low suction pressure cutouts.

Central Control systemScheduling of the various compressors is performed by the microprocessor control. Compressors operating schedules are sequenced every 24 hours to assure distribution of run time. This microprocessor monitors the following on each refrigeration system:

• Discharge pressure cut-out• Suction pressure cut-out• Compressor motor protector• Suction temperature• Evaporator entering and leaving chilled water temperature

A fault condition from these controls or sensors will cause a shutdown of that compressor with the transfer of load requirements to another available compressor. When a fault occurs, the microprocessor records the reading of conditions at the time and stores the data for recall by operating personnel. This information can be recalled using the keys and displayed on the LCD screen. A running history of the fault occurrence conditions is maintained (up to the last 20 occurrences) should it be required for trouble shooting.

Individual monitoring of leaving chilled water temperature from each refrigeration system is designed to protect against freeze-up.

The control system monitors entering and leaving chilled water temperatures to determine system load and selects the number of compressors required. Response time and set points are adjustable.

options• Variable Flow• Inside Out/Total Access Design• Pump Options• Lifting Frame Options• Dry Cooler Options

MeCHAnICAl sPeCIFICATIons

F148PC0911

1065 Maple Avenue P.O. Box 510 Sparta, WI 54656Phone 608-366-2400 • Fax 608-366-2450

www.multistack.com

Made in the USA

Originators…Multistack invented the modular water chiller. It started with a radically simple idea: chiller modules that could be brought into the equipment room one at a time, through standard doorways and down elevators, to form a fully integrated chiller system. The idea launched a revolution and transformed Multistack into a leader in the commercial water-chiller industry.

Innovators…Multistack perfected the modular chiller and leads the industry in innovative and environmentally friendly modular solutions. Since founding in the late 1980s, Multistack has engineered, manufactured, and distributed an impressive array of modular air conditioning firsts: the first on-board strainer, the first modular automatic blow-down device, the first modular chiller for variable flow, the first modular chiller-heater (heat pump), the first modular heat-recovery chiller, the first modular air-to-water heat pump, the first modular chiller to utilize MagLev™ compressor technology, and the first modular chiller to utilize R-410A.

Never the Imitators…Multistack sets the standard in the industry for superior customer service, fast and on time shipment, superior product quality, and new product development. Our pioneering leadership in environmental issues is well documented. If you want the best, be sure to specify the original – Multistack®.

Environmentally Friendly Refrigerantsr-410A refrigerantRefrigerant, R-410A, is widely available, safe, and environmentally friendly refrigerants. R-410A is available in virtually all Multistack systems making hot water up to 140°F, a good environmental choice!

Environmental FocusIn addition to providing products to deliver reliable comfort and low operating cost, Multistack’s products can also reduce your environmental footprint. We are committed to developing and manufacturing cooling and heating products that can reduce fossil fuel consumption and operate on the refrigerants designed to protect the environment. Multistack Water-Cooled chillers and efficiency improvements across our product line are the result of this focus.



Appendix 5

Multistack Dedicated Heat Recovery Chiller Catalogue (R134A)

Dedicated Heat Recovery Chiller™ (DHRC)Product Data Catalog for R410A and R134a Refrigerants

sm

MS010XC-410A MS010AN-134a






Table of Contents

Product Introduction ............................................................................................. 4

Chiller Options ...................................................................................................... 6

General Data ....................................................................................................... 11

Performance Data for R410A Refrigerant ............................................................ 12

Performance Data for R134a Refrigerant ............................................................ 18

Electrical Data ..................................................................................................... 24

Controller Schematics ......................................................................................... 25

Schematics .......................................................................................................... 26

Sample Piping Schematics .................................................................................. 27

Mechanical Specifications ................................................................................... 29

Model Number NomenclatureExisting MS 50 X 1 H 1 W 0 R410A

New MS 050 X C or N 1 H 1 W 0 A A -410A

SeriesModule Nominal Capacity (10 - 160 tons)

Compressor Type1AHRI Certified (C - certified, N - Not certified)

Configuration2

Voltage3Module Number ( 1 - single, 2 - multiple)

Application4AHRI Version - if applicable

Evaporator5Condenser6

Refrigerant

1 B: Bristol, C: Trane Cornerstone, R: Bitzer Screw, S: Trane Scroll, T: Danfoss Turbocor, Z: Copeland scroll (old elec), X: Copeland Scroll (ZP), A: Copeland Scroll (ZR)2 1- Standard, 2- Total access, 3 - Evap extended headers, 4 - Cond extended headers, 5 - Both extended headers, V - others3 A - 208/3/60, L - 230/3/60, H - 460/3/60, C - 575/3/60, D - 200/3/50, E - 400/3/50, F - 380/3/60, S - 220/230/1/60, V - other4 A - Air Cooled split, C - Single module temp controller, D - Cond unit, F - Fluid cooler (high temp),H - Heat recovery, R - Heat pump, W - Water cooled5 A - Brazed SS, B - Brazed SMO, C- S&T copper, D - S&T cu-Ni, V - Other6 A - Brazed SS, B - Brazed SMO, C- S&T copper, D - S&T cu-Ni, E - Double wall brazed, R - Remote, V - Other

Dedicated Heat Recovery Chiller™ (DHRC)PRODUCT INTRODUCTION

Multistack® is the recognized world leader in the design and implementation of modular chillers. Through 20-plus years of product development we have learned how to best capture and control the heat that is typically rejected by the chiller. With that in mind we set out to build the industry’s best, most efficient, Dedicated Heat Recovery Chiller™ (DHRC).

During the process of cooling, heat is generated, and, more often than not, discarded to the atmosphere. This process has been around for as long as there have been heating and cooling systems. There are many negative effects with the disposal of heat as waste. Buildings can use two times more energy to do the cooling and dispose of the heat, as if they just took possession of the heat and using that heat where it is needed. Even in the middle of summer, most buildings require a certain amount of heat to be made for proper humidity control, potable hot water, and many other hot water applications. Heat recovery addresses this waste and turns it into a way to lower energy bills, reduce the carbon footprint of a building and will provide tremendous improvement for overall building efficiency. Currently, the requirement for LEED is to improve upon ASHRAE 90.1 by up to 30%. A DHRC can help you get there.

Heat recovery is not a new concept, it has been around since the early 1970s, however it was not easy to implement based on the size of chillers then — and the very limited hot water temperatures achieveable. The Multistack DHRC, by the very nature of a modular chiller, changes the application from difficult to simple because it gives you control of hot and cold water simultaneously, and most buildings have a constant heating and cooling requirement. By identifying the maximum and minimum loads of both, it becomes fairly easy to size a DHRC from 10 – 900-tons per array. This allows the DHRC to be a part of the buildings chiller and boiler system –especially since it can produce water up to 180°F.

When a DHRC is applied as a supplement to a building system, it can contribute to the cooling process during the spring, summer and fall, while supplying the hot water for the building for free. During the winter, by directing the DHRC to focus on the constant cooling demands of the building core, a data center or phone room, it will continue to supply hot water—still for basically free and eliminating the use of natural gas for creating the heat.

Anytime a building has a concurrent demand identified, it makes sense to look to the DHRC for a first stage economizer, rather than bringing in cold outside air and exhausting building heat. This application makes even more sense when you have an array of Multistack chillers that are the primary source of cooling for the building, allowing all the heat generated during that first stage to be used—for free!

To associate some dollars saved to this concept, the 45-ton DHRC installed upstream of the condensing boilers at Evansville State Hospital in Evansville, Indiana. Designed to satisfy all the VAV reheating and the domestic hot water—while supplementing the cooling load-- the DHRC is having a significant impact on the utility costs at the hospital by saving $36,000 - $54,000 per year, depending on the costs of natural gas. See this case study, and others, at www.multistack.com

These are just some of the reasons a DHRC can be a great addition to almost any building.

5

Dedicated Heat Recovery Chiller™ (DHRC)

Applications for a Multistack DHRC•Laundry Water Heating•Swimming Pool Heating•Process Heating and Cooling•Domestic Hot Water•Building Heat•Reheat Coils•Ice Hockey Rink•VAV Reheat

Typical Buildings for DHRC Applications•Hotels and Motels•Resorts•Recreational Facilities•Schools•Hospitals•Nursing Homes•Process Cooling and Heating•Data Centers•Call Centers•Campus Cooling and Heating Plants

Benefits•Reduced CO2 emissions•Easy retrofit for any mechanical room•Double Wall Vented Heat Exchanger allows for potable water (optional)•Payback in less than three years typically•More efficient than a gas boiler

− COP can exceed 7.0•Low load efficiency•Apply for Leed points•ASHRAE 15 / B-52 compliant without monitoring or ventilation

equipment.

Features•Independent refrigerant circuits•No reversing valves•Auto mode controls•Control the mode dynamically without input from the BAS

Highly Dependable•Multiple independent systems for redundancy•Comprehensive computer monitoring of operations (optional)•Automatic diagnostic recording of fault conditions•Rotates lead compressor every 24 hours

Simple To Operate•Large LCD screen displays information in plain English•Simple keypad provides control of unit operations

Easy To Install•Compact modules fit through standard doorways and into elevators•Modules interconnect easily and quickly•All refrigeration systems are factory charged and run tested•Single point power up to 500 MCA

Programmable Logic Controller (PLC) System

•Manual switch allows redundancy control as each module has a processor allowing it to run even if master controller fails•Optional Fail-To-Run software•Display at each module•Remote display option•Automatic controls for both chilled and hot water•Optional BAS Interface

Design Flexibility•Wide array of module combinations•Install only the capacity required at the time•Variable or constant flow options

Simple To Service•Service can often be performed on a convenient, non-emergency basis•Most components are standard, off the shelf design•Able to service one module while system is in operation

PRODUCT INTRODUCTION

Side View

Lockable High Voltage Circuit Breaker

Chilled Water

Bussbar DuctLow Voltage Controls Compressors

Condenser Water

6

Dedicated Heat Recovery Chiller™ (DHRC)CHILLER OPTIONS

Rail = Num

ber of Modules x W

idth + 8

Standard Modules (Constant Flow

Design)

Dim

ensions (No Panels)

Width (A)

Depth (B)Height (C)

Standard28”

47 5/8”64”

Total Access (MS010--050)

32”56”

67”

Total Access (MS070)

34”56”

67”

Extended Headers (1)28”

62 1/8”64”


76 5/8”64”

*Standardized drawing of sample custom

er installation

7

Dedicated Heat Recovery Chiller™ (DHRC)CHILLER OPTIONS, Cont’d

Rail = Num

ber of Modules x W

idth + 8

Variable Flow

Design for Chilled and H

ot Water–

Extended Headers on Evaporators and Condensers

Dim

ensions (No Panels)

Width (A)

Depth (B)Height (C)

Standard28”

47 5/8”64”


32”56”

67”


34”56”

67”


62 1/8”64”


76 5/8”64”


er installation

8

Dedicated Heat Recovery Chiller™ (DHRC)CHILLER OPTIONS, Cont’d

Rail = Num

ber of Modules x W

idth + 8

Variable Flow

Design for H

ot Water

Constant Flow for Chilled W

aterExtended H

eaders on Condensers

Dim

ensions (No Panels)

Width (A)

Depth (B)Height (C)

Standard28”

47 5/8”64”


32”56”

67”


34”56”

67”


62 1/8”64”


76 5/8”64”


er installation

9


Rail = Num

ber of Modules x W

idth + 8

CHILLER OPTIONS, Cont’dV

ariable Flow D

esign for Chilled Water

Constant Flow for Condenser W

aterExtended H

eaders on EvaporatorsDim

ensions (No Panels)

Width (A)

Depth (B)Height (C)

Standard28”

47 5/8”64”


32”56”

67”


34”56”

67”


62 1/8”64”


76 5/8”64”


er installation

10


Rail = Num

ber of Modules x W

idth + 8

CHILLER OPTIONS, Cont’d

Total Access D

esign with or w

ithout Variable Flow

Dim

ensions (No Panels)

Width (A)

Depth (B)Height (C)

Standard28”

47 5/8”64”


32”56”

67”


34”56”

67”


62 1/8”64”


76 5/8”64”


er installation

11

Dedicated Heat Recovery Chiller™ (DHRC)GENERAL DATA

General Data TableMS010XC-410A/ MS010AN-134a

MS015XC-410A/ MS015AN-134a

MS020XC-410A/ MS020AN-134a

MS030XC-410A/ MS030AN-134a

MS050XC-410A/ MS050AN-134a

MS070XC-410A/ MS070AN-134a

Compressor Type Scroll Scroll Scroll Scroll Scroll ScrollDry Weight (lbs. each) 89 135 135 146 353 390Normal Capacity (tons each) 5 8.5 10 15 25 32Quantity 2 2 2 2 2 2Oil Charge (pints) 3.5 6.9 6.9 6.9 14.4 13.3

Evaporator (Brazed Plate) Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed PlateWeight (lbs. each) 80 80 80 105 180 243Water Storage (gallons each) 1.9 1.9 1.9 2.9 4.8 7.3Circuit Configuration Dual Dual Dual Dual Dual DualQuantity 1 1 1 1 1 1Header System (gallons) 7 7 7 7 7 7

Condenser Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed Plate Brazed PlateWeight (lbs. each) 90 90 90 135 220 313Water Storage (gal. each) 2.4 2.4 2.4 4.1 6.6 10.1Circuit Configuration Dual Dual Dual Dual Dual DualQuantity 1 1 1 1 1 1Header System (gallons) 7 7 7 7 7 7

Refrigerant Type R410A/R134a R410A/R134a R410A/R134a R410A/R134a R410A/R134a R410A/R134aCharge (lbs./circuit) 6.5 6.5 8 12 18 24Number of Circuits 2 2 2 2 2 2

Operating Weight (lbs.) 1110 1200 1200 1625 2000 2200Shipping Weight (lbs.) 950 1040 1040 1450 1730 1900

Multistack Glycol Solution InformationLow Temperature Operation with Glycol

In chilled water systems where water temperatures of less than 40°F and ambient temperatures of 32° F are likely to occur, it is necessary to add a glycol-based heat transfer fluid to the system. Both Ethylene and Propylene are available and they offer the same basic freeze and corrosion protection although there are performance differences in the solutions.

*Note: Ethylene and propylene glycol ratings are outside the scope of AHRI Standard 550/590 Certifications.*Note: The effect of glycol in the condenser is negligible as it tends to mirror the properties of water as its temperature increases. No emphasis on derate on condenser capacity with glycol is necessary in the selection process.

ETHYLENE GLYCOL

Ethylene %Freeze Point

Capacity Power Flow Pressure Drop°F °C

10 26 -3.3 0.996 0.999 1.035 1.09620 18 -7.8 0.986 0.998 1.06 1.21930 7 -13.9 0.978 0.996 1.092 1.35240 -7 -21.7 0.966 0.993 1.131 1.5350 -28 -33.3 0.955 0.991 1.182 1.751

PROPYLENE GLYCOL

Propylene %Freeze Point

Capacity Power Flow Pressure Drop°F °C

10 26 -3 0.987 0.992 1.01 1.06820 19 -7 0.975 0.985 1.028 1.14730 9 -13 0.962 0.978 1.05 1.24840 -5 -21 0.946 0.971 1.078 1.36650 -27 -33 0.929 0.965 1.116 1.481

12


MS010XC-410A LEAVING HOT WATER TEMPERATURE105°F

Leaving Chilled Water °F Power (kW) Cooling (Tons) Heat (MBH) Cooling EER Heat COP H & C COP50°F 9.5 11.2 167.3 14.2 5.2 9.348°F 9.6 10.8 162.3 13.6 5.0 9.046°F 9.6 10.4 157.3 13.0 4.8 8.645°F 9.6 10.2 154.9 12.7 4.7 8.444°F 9.6 10.0 152.5 12.4 4.6 8.342°F 9.7 9.6 147.8 11.9 4.5 8.040°F 9.7 9.2 143.3 11.3 4.3 7.7

115°FLeaving Chilled Water °F Power (kW) Cooling (Tons) Heat (MBH) Cooling EER Heat COP H & C COP

50°F 10.6 10.5 161.9 11.9 4.5 7.948°F 10.7 10.1 157.1 11.3 4.3 7.746°F 10.7 9.7 152.3 10.8 4.2 7.345°F 10.7 9.5 150.0 10.6 4.1 7.244°F 10.8 9.3 147.7 10.3 4.0 7.142°F 10.8 8.9 143.3 9.9 3.9 6.840°F 10.8 8.5 138.9 9.4 3.8 6.5


50°F 11.9 9.6 156.2 9.8 3.9 6.748°F 11.9 9.2 151.6 9.3 3.7 6.546°F 12.0 8.9 147.0 8.9 3.6 6.245°F 12.0 8.7 144.8 8.7 3.5 6.144°F 12.0 8.5 142.6 8.5 3.5 6.042°F 12.1 8.1 138.3 8.0 3.4 5.740°F 12.1 7.7 134.2 7.7 3.2 5.5


50°F 12.6 9.2 153.2 8.8 3.6 6.248°F 12.6 8.8 148.7 8.4 3.5 5.946°F 12.7 8.4 144.3 8.0 3.3 5.745°F 12.7 8.2 142.1 7.8 3.3 5.644°F 12.7 8.0 140.0 7.6 3.2 5.542°F 12.8 7.7 135.8 7.2 3.1 5.240°F 12.8 7.3 131.7 6.9 3.0 5.0


50°F 13.3 8.7 150.2 7.9 3.3 5.648°F 13.4 8.4 145.8 7.5 3.2 5.446°F 13.4 8.0 141.5 7.1 3.1 5.245°F 13.5 7.8 139.4 6.9 3.0 5.144°F 13.5 7.6 137.3 6.8 3.0 5.042°F 13.5 7.3 133.2 6.4 2.9 4.840°F 13.6 6.9 129.2 6.1 2.8 4.6


50°F 14.1 8.3 147.2 7.0 3.1 5.148°F 14.2 7.9 142.9 6.7 3.0 4.946°F 14.2 7.5 138.7 6.3 2.9 4.745°F 14.3 7.3 136.6 6.2 2.8 4.644°F 14.3 7.2 134.6 6.0 2.8 4.542°F 14.4 6.8 130.6 5.7 2.7 4.340°F 14.4 6.5 126.7 5.4 2.6 4.2

PERFORMANCE DATA-R410A REFRIGERANT

For non-published performance ranges, please contact Multistack.

13





50°F 17.3 17.7 271.3 12.3 4.6 8.248°F 17.2 17.0 263.2 11.9 4.5 8.046°F 17.2 16.4 255.4 11.4 4.3 7.745°F 17.2 16.1 251.6 11.2 4.3 7.644°F 17.2 15.8 247.9 11.0 4.2 7.442°F 17.3 15.1 240.6 10.5 4.1 7.240°F 17.3 14.6 233.4 10.1 4.0 6.9


50°F 19.5 14.4 239.0 8.8 3.6 6.248°F 19.5 15.8 256.2 9.8 3.9 6.746°F 19.5 15.2 249.9 9.4 3.7 6.545°F 19.5 14.9 245.3 9.2 3.7 6.444°F 19.5 14.6 241.8 9.0 3.6 6.342°F 19.5 14.0 234.8 8.6 3.5 6.140°F 19.5 13.5 228.1 8.3 3.4 5.9


50°F 20.7 15.8 260.0 9.2 3.7 6.448°F 20.7 15.2 252.7 8.8 3.6 6.246°F 20.7 14.6 245.6 8.4 3.5 6.045°F 20.7 14.3 242.1 8.3 3.4 5.944°F 20.7 14.0 238.7 8.1 3.4 5.842°F 20.8 13.4 232.0 7.8 3.3 5.640°F 20.8 12.9 225.5 7.4 3.2 5.4


50°F 22.0 15.1 256.2 8.2 3.4 5.848°F 22.0 14.5 249.2 7.9 3.3 5.646°F 22.1 13.9 242.3 7.6 3.2 5.445°F 22.1 13.6 238.9 7.4 3.2 5.444°F 22.1 13.4 235.6 7.3 3.1 5.342°F 22.1 12.8 229.2 6.9 3.0 5.140°F 22.2 12.3 222.8 6.6 2.9 4.9


50°F 23.4 14.4 252.5 7.4 3.2 5.348°F 23.5 13.8 245.6 7.1 3.1 5.146°F 23.5 13.2 239.0 6.8 3.0 5.045°F 23.5 13.0 235.8 6.6 2.9 4.944°F 23.5 12.7 232.6 6.5 2.9 4.842°F 23.6 12.2 226.3 6.2 2.8 4.640°F 23.6 11.6 220.2 5.9 2.7 4.5



14


14





50°F 19.9 21.0 319.3 12.7 4.7 8.448°F 19.9 20.2 309.6 12.2 4.6 8.146°F 19.9 19.4 300.1 11.7 4.4 7.945°F 19.9 19.0 295.5 11.5 4.4 7.744°F 19.9 18.6 290.9 11.2 4.3 7.642°F 19.9 17.8 281.9 10.8 4.2 7.340°F 19.9 17.1 273.1 10.3 4.0 7.1


50°F 22.5 19.3 308.3 10.3 4.0 7.048°F 22.5 18.5 299.1 9.9 3.9 6.846°F 22.5 17.8 290.1 9.5 3.8 6.645°F 22.5 17.4 285.7 9.3 3.7 6.444°F 22.5 17.0 281.3 9.1 3.7 6.342°F 22.5 16.3 272.8 8.7 3.5 6.140°F 22.6 15.6 264.6 8.3 3.4 5.9


50°F 23.9 18.4 302.8 9.2 3.7 6.448°F 24.0 17.7 293.8 8.9 3.6 6.246°F 24.0 16.9 285.1 8.5 3.5 6.045°F 24.0 16.6 280.9 8.3 3.4 5.944°F 24.0 16.2 276.7 8.1 3.4 5.842°F 24.1 15.5 268.5 7.8 3.3 5.540°F 24.1 14.9 260.5 7.4 3.2 5.3


50°F 25.5 17.5 297.2 8.2 3.4 5.848°F 25.5 16.8 288.6 7.9 3.3 5.646°F 25.6 16.1 280.2 7.5 3.2 5.445°F 25.6 15.7 276.1 7.4 3.2 5.344°F 25.6 15.4 272.1 7.2 3.1 5.242°F 25.7 14.7 264.3 6.9 3.0 5.040°F 25.7 14.1 256.7 6.6 2.9 4.8


50°F 27.2 16.6 291.7 7.3 3.1 5.348°F 27.2 15.9 283.5 7.0 3.1 5.146°F 27.3 15.2 275.5 6.7 3.0 4.945°F 27.3 14.9 271.6 6.5 2.9 4.844°F 27.3 14.5 267.8 6.4 2.9 4.742°F 27.4 13.9 260.3 6.1 2.8 4.640°F 27.5 13.3 253.1 5.8 2.7 4.4


15


15





50°F 29.6 31.5 478.9 12.8 4.8 8.548°F 29.5 30.4 464.7 12.4 4.6 8.246°F 29.4 29.2 450.8 11.9 4.5 8.045°F 29.3 28.7 444.0 11.7 4.4 7.944°F 29.3 28.1 437.3 11.5 4.4 7.842°F 29.2 27.0 424.1 11.1 4.3 7.540°F 29.1 26.0 411.3 10.7 4.1 7.3


50°F 32.9 29.2 462.6 10.7 4.1 7.348°F 32.8 28.1 449.1 10.3 4.0 7.046°F 32.7 27.1 436.1 9.9 3.9 6.845°F 32.6 26.5 429.7 9.8 3.9 6.744°F 32.6 26.0 423.3 9.6 3.8 6.642°F 32.5 25.0 411.0 9.2 3.7 6.440°F 32.5 24.0 398.9 8.9 3.6 6.2


50°F 34.7 28.0 454.2 9.7 3.8 6.748°F 34.6 26.9 441.2 9.3 3.7 6.546°F 34.5 25.9 428.6 9.0 3.6 6.345°F 34.5 25.4 422.4 8.8 3.6 6.244°F 34.5 24.9 416.3 8.7 3.5 6.142°F 34.4 23.9 404.4 8.3 3.4 5.940°F 34.3 23 392.7 8.0 3.4 5.7


50°F 36.6 26.7 445.8 8.8 3.6 6.148°F 36.6 25.7 433.3 8.4 3.5 5.946°F 36.5 24.7 421.1 8.1 3.4 5.845°F 36.5 24.2 415.1 8.0 3.3 5.744°F 36.4 23.8 409.2 7.8 3.3 5.642°F 36.4 22.8 397.7 7.5 3.2 5.440°F 36.3 21.9 386.5 7.2 3.1 5.2


50°F 38.7 25.4 437.4 7.9 3.3 5.648°F 38.7 24.5 425.3 7.6 3.2 5.546°F 38.6 23.5 413.6 7.3 3.1 5.345°F 38.6 23.0 407.8 7.2 3.1 5.244°F 38.6 22.6 402.2 7.0 3.1 5.142°F 38.5 21.7 391.1 6.7 3.0 5.040°F 38.5 20.8 380.4 6.5 2.9 4.8


16


16




50°F 47.7 50.8 772.7 12.8 4.8 8.548°F 47.6 48.9 749.3 12.3 4.6 8.246°F 47.5 47.1 726.6 11.9 4.5 8.045°F 47.4 46.1 715.4 11.7 4.4 7.944°F 47.4 45.3 704.5 11.5 4.4 7.742°F 47.2 43.5 683.1 11.0 4.2 7.540°F 47.1 41.8 662.3 10.6 4.1 7.2


50°F 53.1 47.1 746.8 10.7 4.1 7.248°F 53.0 45.3 724.9 10.3 4.0 7.046°F 52.9 43.6 703.5 9.9 3.9 6.845°F 52.9 42.7 693.1 9.7 3.8 6.744°F 52.8 41.9 682.9 9.5 3.8 6.642°F 52.7 40.3 662.8 9.2 3.7 6.440°F 52.6 38.7 643.3 8.8 3.6 6.2


50°F 56.1 45.2 734.1 9.7 3.8 6.748°F 56.0 43.5 712.9 9.3 3.7 6.546°F 55.9 41.8 692.3 9.0 3.6 6.345°F 55.8 41.0 682.2 8.8 3.6 6.244°F 55.8 40.2 672.3 8.6 3.5 6.142°F 55.7 38.6 652.9 8.3 3.4 5.940°F 55.6 37.1 634.1 8.0 3.3 5.7


50°F 59.3 43.3 721.5 8.8 3.6 6.148°F 59.2 41.6 701.1 8.4 3.5 5.946°F 59.1 40.0 681.2 8.1 3.4 5.845°F 59.0 39.2 671.5 8.0 3.3 5.744°F 59.0 38.4 661.9 7.8 3.3 5.642°F 58.8 36.9 643.2 7.5 3.2 5.440°F 58.7 35.4 625.1 7.2 3.1 5.2


50°F 62.7 41.3 709.2 7.9 3.3 5.648°F 62.6 39.7 689.5 7.6 3.2 5.546°F 62.4 38.1 670.3 7.3 3.1 5.345°F 62.4 37.4 661.0 7.2 3.1 5.244°F 62.3 36.6 651.8 7.0 3.1 5.142°F 62.2 35.1 633.8 6.8 3.0 5.040°F 62.1 33.7 616.3 6.5 2.9 4.8



17


17




50°F 62.1 66.5 1010.0 12.9 4.8 8.548°F 61.9 64.1 980.0 12.4 4.6 8.346°F 61.6 61.7 950.7 12.0 4.5 8.045°F 61.5 60.5 936.3 11.8 4.5 7.944°F 61.4 59.4 922.1 11.6 4.4 7.842°F 61.2 57.1 894.3 11.2 4.3 7.640°F 61.1 54.9 867.2 10.8 4.2 7.3


50°F 69.1 61.7 976.6 10.7 4.1 7.348°F 68.9 59.5 948.4 10.4 4.0 7.146°F 68.7 57.2 921.0 10.0 3.9 6.945°F 68.6 56.1 907.5 9.8 3.9 6.844°F 68.5 55.0 894.2 9.6 3.8 6.742°F 68.4 52.9 868.1 9.3 3.7 6.540°F 68.2 50.8 842.6 8.9 3.6 6.2


50°F 73.0 59.3 960.0 9.7 3.9 6.748°F 72.8 57.0 932.8 9.4 3.8 6.546°F 72.6 54.9 906.2 9.1 3.7 6.345°F 72.5 53.8 893.2 8.9 3.6 6.244°F 72.4 52.8 880.3 8.7 3.6 6.142°F 72.3 50.7 855.0 8.4 3.5 5.940°F 72.1 48.7 830.3 8.1 3.4 5.8


50°F 77.2 56.7 943.4 8.8 3.6 6.248°F 76.9 54.6 917.1 8.5 3.5 6.046°F 76.8 52.5 891.5 8.2 3.4 5.845°F 76.7 51.5 878.9 8.1 3.4 5.744°F 76.6 50.4 866.4 7.9 3.3 5.642°F 76.4 48.5 842.0 7.6 3.2 5.540°F 76.3 46.5 818.1 7.3 3.1 5.3


50°F 81.5 54.1 926.9 8.0 3.3 5.748°F 81.3 52.0 901.5 7.7 3.3 5.546°F 81.2 50.0 876.7 7.4 3.2 5.345°F 81.1 49.0 864.6 7.3 3.1 5.344°F 81.0 48.0 852.6 7.1 3.1 5.242°F 80.8 46.1 829.0 6.8 3.0 5.040°F 80.7 44.2 805.9 6.6 2.9 4.9



18

Dedicated Heat Recovery Chiller™ (DHRC)PERFORMANCE DATA-R134a REFRIGERANT

MS010AN-134a LEAVING HOT WATER TEMPERATURE150°F



50°F 11.2 5.0 97.8 5.3 2.6 4.148°F 11.2 4.7 95.0 5.0 2.5 4.046°F 11.2 4.5 92.4 4.8 2.4 3.845°F 11.2 4.4 91.1 4.7 2.4 3.844°F 11.2 4.3 89.8 4.6 2.3 3.742°F 11.3 4.1 87.4 4.4 2.3 3.640°F 11.3 3.9 85.1 4.1 2.2 3.4


50°F 12.7 4.4 96.3 4.2 2.2 3.548°F 12.7 4.2 93.8 4.0 2.2 3.346°F 12.7 4.0 91.4 3.8 2.1 3.245°F 12.7 3.9 90.3 3.7 2.1 3.244°F 12.7 3.8 89.1 3.6 2.1 3.142°F 12.8 3.6 87.0 3.4 2.0 3.040°F


50°F 14.3 3.9 95.0 3.2 2.0 2.948°F 14.3 3.7 92.8 3.1 1.9 2.846°F 14.4 3.5 90.7 2.9 1.8 2.745°F 14.4 3.4 89.7 2.8 1.8 2.644°F 14.5 3.3 88.8 2.7 1.8 2.642°F40°F


19

Dedicated Heat Recovery Chiller™ (DHRC)PERFORMANCE DATA-R134a REFRIGERANT




50°F 21.3 7.1 157.9 4.0 2.2 3.448°F 21.2 6.8 153.7 3.8 2.1 3.246°F 21.2 6.4 149.5 3.7 2.1 3.145°F 21.1 6.3 147.5 3.6 2.0 3.144°F 21.1 6.1 145.5 3.5 2.0 3.042°F 21.0 5.8 141.6 3.3 2.0 2.940°F 21.0 5.5 137.8 3.2 1.9 2.9


50°F 23.5 6.1 153.7 3.1 1.9 2.848°F 23.4 5.8 149.9 3.0 1.9 2.846°F 23.4 5.5 146.1 2.8 1.8 2.745°F 23.3 5.5 144.3 2.8 1.8 2.644°F 23.3 5.3 142.5 2.7 1.8 2.642°F 23.2 5.0 139.0 2.6 1.8 2.540°F


50°F 25.9 5.2 150.0 2.4 1.7 2.448°F 25.8 4.9 146.6 2.3 1.7 2.346°F 25.7 4.6 143.2 2.2 1.6 2.345°F 25.7 4.5 141.6 2.1 1.6 2.244°F 25.6 4.4 140.0 2.1 1.6 2.242°F40°F


20


2020

PERFORMANCE DATA-R134a REFRIGERANT




50°F 22.5 8.4 177.3 4.5 2.3 3.648°F 22.4 8.0 172.5 4.3 2.3 3.546°F 22.4 7.6 167.7 4.1 2.2 3.445°F 22.3 7.4 165.4 4.0 2.2 3.344°F 22.3 7.3 163.1 3.9 2.1 3.342°F 22.2 6.9 158.6 3.7 2.1 3.240°F 22.2 6.6 154.2 3.6 2.0 3.1


50°F 24.8 7.4 173.1 3.6 2.0 3.148°F 24.8 7.0 168.6 3.4 2.0 3.046°F 24.7 6.7 164.2 3.2 2.0 2.945°F 24.7 6.5 162.1 3.2 1.9 2.944°F 24.6 6.3 159.9 3.1 1.9 2.842°F 24.5 6.0 155.8 2.9 1.9 2.740°F


50°F 27.4 6.3 169.0 2.8 1.8 2.648°F 27.3 6.0 164.9 2.6 1.8 2.546°F 27.2 5.7 160.9 2.5 1.7 2.545°F 27.2 5.5 159.0 2.4 1.7 2.444°F 27.1 5.4 157.0 2.4 1.7 2.442°F40°F


21


2121





50°F 28.8 12.1 243.3 5.0 2.5 4.048°F 28.7 11.5 235.9 4.8 2.4 3.846°F 28.7 10.9 228.5 4.5 2.3 3.745°F 28.7 10.6 224.9 4.4 2.3 3.644°F 28.7 10.3 221.3 4.3 2.3 3.542°F 28.7 9.7 214.1 4.1 2.2 3.440°F 28.7 9.1 207.1 3.8 2.1 3.2


50°F 32.3 10.5 235.6 3.9 2.1 3.348°F 32.3 9.9 228.2 3.7 2.1 3.146°F 32.2 9.3 221.0 3.4 2.0 3.045°F 32.2 9.0 217.4 3.3 2.0 3.044°F 32.2 8.7 213.8 3.2 1.9 2.942°F 32.2 8.1 206.7 3.0 1.9 2.840°F


50°F 36.2 8.7 227.4 2.9 1.8 2.748°F 36.2 8.1 220.1 2.7 1.8 2.646°F45°F44°F42°F40°F


22


22




50°F 52.0 24.4 469.6 5.6 2.6 4.348°F 52.0 23.3 456.7 5.4 2.6 4.146°F 52.1 22.3 444.5 5.1 2.5 4.045°F 25.1 21.7 438.5 5.0 2.5 3.944°F 52.1 21.3 432.7 4.9 2.4 3.942°F 52.2 20.3 421.4 4.7 2.4 3.740°F 52.3 19.4 410.7 4.4 2.3 3.6


50°F 59.3 22.3 470.0 4.5 2.3 3.648°F 59.5 21.3 458.4 4.3 2.3 3.546°F 59.7 20.3 447.4 4.1 2.2 3.445°F 59.8 19.9 442.1 4.0 2.2 3.344°F 59.9 19.4 437.0 3.9 2.1 3.342°F 60.1 18.5 427.0 3.7 2.1 3.240°F


50°F 68.3 20.2 475.1 3.5 2.0 3.148°F 68.7 19.2 465.0 3.4 2.0 3.046°F45°F44°F42°F40°F



23


23




50°F 66.3 31.7 607.0 5.7 2.7 4.448°F 66.3 30.3 590.3 5.5 2.6 4.246°F 66.4 29.0 574.2 5.2 2.5 4.145°F 66.4 28.3 566.5 5.1 2.5 4.044°F 66.4 27.7 558.9 5.0 2.5 3.942°F 66.5 26.4 544.2 4.8 2.4 3.840°F 66.7 25.2 530.2 4.5 2.3 3.7


50°F 75.7 29.1 606.9 4.6 2.4 3.748°F 75.9 27.8 591.8 4.4 2.3 3.646°F 76.1 26.5 577.5 4.2 2.2 3.545°F 76.3 25.9 570.6 4.1 2.2 3.444°F 76.4 25.3 563.8 4.0 2.2 3.342°F 76.7 24.1 550.8 3.8 2.1 3.240°F


50°F 87.2 26.3 612.9 3.6 2.1 3.148°F 87.7 25.1 599.6 3.4 2.0 3.046°F45°F44°F42°F40°F




2424

1. Compressor Rated Load Amps (RLA) and Locked Rotor Amps (LRA) Data: RLA/LRA

External Input/Output Connections System Wire & Fuse Sizing Specifications(Applicable codes may require different wire sizing)

R410A VOLTAGE 208 230 460 575

MS010XC 22.8/123 20.6/123 10.3/62 8.4/50

MS015XC 36.5/225 33/225 16.5/114 13/80

MS020XC 44/239 40/239 20/125 16/80

MS030XC 68/340 61/340 31/173 25/132

MS050XC 101/605 91/605 46/272 37/215

MS070XC 133/599 120/599 60/310 48/239

R134a VOLTAGE 208 230 460 575

MS010AN 23.5/128 21/128 10.2/63 8.2/49

MS015AN 38.7/225 35/225 17.5/114 14/80

MS020AN 44/239 40/239 20/125 16/80

MS030AN 61/300 55/300 27/150 22/109

MS050AN 100/500 90/500 46/250 37/198

MS070AN 127/599 114/599 58/310 47/239

2. Wiring Sizing: Minimum Circuit Ampacity (MCA) MCA = (1.25 x RLA1*) + RLA2 + RLA3

MCA 3 CONDUCTORS1 CONDUIT

6 CONDUCTORS

2 CONDUIT

50 8 —65 6 —85 4 —

100 3 —115 2 —130 1 —150 1/0 —175 2/0 —200 3/0 —230 4/0 —255 250 MCM —285 300 MCM 1/0300 — 2/0350 — 3/0400 — 4/0460 — 4/0500 — 250 MCM

3. Fuse Sizing: Maximum Fuse (MF), Type RK5 FuseMF= (2.25 x RLA1*) + RLA2 + RLA3 Where the MF does not equal a standard size fuse, the next larger size should be used.

NOTES:A.*RLA1 = RLA of the largest compressor in the system. RLA2 & RLA3 = RLA of the other compressors in the system.B. The total system Minimum Circuit Ampacity (aMCA) shall not exceed 500A.C. Wire sizing is based on the Nat. Electr. Code (NEC) rating for 75°C copper wire, with 3 wires per conduit.D. Wiring Distance from branch circuit shall not exceed 100ft.

Note: RLA and LRA is per compressor. Two compressors per module.

ELECTRICAL DATA


25

ENT. CHILLED WATER TEMP.


VERIFY CHILLED WATER FLOW

ENT. HOT WATER TEMP

LVG. HOT WATER TEMP

VERIFY HOT WATER FLOW

CUSTOMER INTERLOCKS

CHILLED WATER , HOT WATER ORLOAD LIMIT RESET INPUT

CHILLED WATER PUMP OPERATION

HOT WATER PUMP OPERATION

FAULT NOTIFICATION

FULL LOAD RELAY

CHILLED WATER CONTROLS

HOT WATER CONTROLS

AUTO CONTROLS FOR SIMULTANEOUS HOTAND CHILLED WATER

Chiller Data

MODULE CONTROL PANEL

Module Data

DATA FROM REFRIGERATION SYSTEM “B”

HP TRANSDUCER


LP TRANSDUCER


SUCTION TEMPERATURE



HIGH VOLTAGE CONTROL PANEL

CIRCUIT “A” COMPRESSOR CONTACTOR

CIRCUIT “B” COMPRESSOR CONTACTOR

BUILDING AUTOMATION SOLUTIONS

INTEROPERABILITY PORTALS

MASTER CONTROLCan stage a maximum of 15 modules

(30 compressors)

REMOTE DISPLAY (optional)

BACNET™

• MSTP • ETHERNET• TCP/IP

MODBUS™ (RTU)

SNMP PROTOCOL

LONMARK™

RS485 Serial Card

PCO Net RS485 Interface Board

PCO Web Ethernet Interface Board

DATA FROM REFRIGERATION SYSTEM “A”

HP TRANSDUCER


LP TRANSDUCER


SUCTION TEMPERATURE



CONTROLLER SCHEMATICS


26

Required Chilled Water Piping (Evaporator)


1/2” SENSOR POCKETS SUPPLIED BY MULTISTACKINSTALLATION OF SENSOR POCKET (WELD-A LET) IS RECOMMENDED AT 30” FROM END OF CHILLER, INSTALLED BY OTHERS.

SP

SP

STANDARD “Y” STRAINERSUPPLIED AND INSTALLED BY OTHERS.

NOTE: SELECT STRAINER BASED ON WATER QUALITY

STRAINER ISOLATION VALVESUPPLIED AND INSTALLED BY OTHERS

EVAPORATOR WATER PUMPSUPPLIED AND INSTALLED BY OTHERS

TO BUILDING LOAD

FROM BUILDING LOAD


EVAPORATOR ISOLATION VALVESSUPPLIED AND INSTALLED BY OTHERS

MULTISTACK CHILLERFS

SCHEMATICS

Required Hot Water Piping (Condenser)

TO HEATLING LOAD

FROM HEATING LOAD


3-WAY CONDENSER BY-PASS VALVESUPPLIED AND INSTALLED IN BUILDING BY OTHERS * May be required if tying into additional heat rejection equipment like a ground source, cooling tower or dry cooler.

CONDENSER ISOLATION VALVESSUPPLIED AND INSTALLED BY OTHERS

1/2” SENSOR POCKETS SUPPLIED BY MULTISTACKINSTALLATION OF SENSOR POCKET (WELD-A-LET) IS RECOMMENDED AT 30” FROM END OF CHILLER, INSTALLED BY OTHERS.


MULTISTACK CHILLERSTANDARD “Y” STRAINER

SUPPLIED AND INSTALLED BY OTHERS.NOTE: SELECT STRAINER MESH BASED ON

WATER QUALITY

STRAINER ISOLATION VALVESUPPLIED AND INSTALLED BY

OTHERS

CONDENSER WATER PUMPSUPPLIED AND INSTALLED BY OTHERS

SP

SP

FS

27

Dedicated Heat Recovery Chiller™ (DHRC)SAMPLE PIPING SCHEMATICS

Figure 1: Domestic Water Heating

Figure 2: Space Hot Water Heating

If using double wall heat exchangers, intermediate heat exhanger is not required.*HX=Intermediate heat exchanger.

28


28

SAMPLE PIPING SCHEMATICS, Cont’d

Figure 3: Chiller Cooling Load

Figure 4: Combination System

29


29

1.01 OPERATING CONDITIONSA. Provide Dedicated Heat Recovery Chiller with the capacity as scheduled on drawings

at job site elevation listed in Section 15050.B. DHRC shall be designed to operate using R-410A or R-134a Refrigerant.C. DHRC shall be designed for parallel evaporator water flow.D. The liquid to be chilled will be water containing corrosion inhibitors.E. DHRC shall be designed to operate using ____ volt, 3 phase, 60 Hz electrical power

supply.

1.02 DEDICATED HEAT RECOVERY CHILLERA. Approved manufacturer is MULTISTACK.B. System Description: Chiller shall incorporate Scroll-type compressors and consist

of multiple ___-ton refrigerant circuits. Each refrigerant circuit shall consist of an individual compressor, condenser, evaporator, thermal expansion valve, and control system. Each circuit shall be constructed to be independent of other circuits from a refrigeration and electrical stand-point. The multi-circuit chiller must be able to produce chilled water even in the event of a failure of one or more refrigerant circuits. Circuits shall not contain more than ___ lb. of R-410A or R-134a refrigerant.

C. General1. Chiller Modules shall be ETL listed in accordance with UL Standard 995, CSA

certified per Standard C22.236.2. Dedicated Heat Recovery Chiller modules shall be based on AHRI certified

platforms.3. Modules shall ship wired and charged with refrigerant. All modules shall be

factory run tested prior to shipment on an AHRI certified or 3rd party verified test stand.

4. Compressors, heat exchangers, piping and controls shall be mounted on a heavy gauge steel frame. Electrical controls, contactors, and relays for each module shall be mounted within that module.

D. Chilled and Condenser Water Mains: Each module shall include supply and return mains for both chilled and condenser water. Grooved end connections are provided for interconnection to six inch standard (6.625” outside diameter) piping with Victaulic type couplings. All headers to be factory insulated. When modules are joined together mains shall create a single point of connection for hot and cold water.

E. Evaporators and condensers: Each evaporator and condenser shall be brazed plate heat exchangers constructed of 316 stainless steel, designed and tested for 650 psig working pressure on the evaporator and 650 psig working pressure on the condenser. Both the condenser and evaporator heat exchanger shall be mounted below the compressor, to eliminate the effect of migration of refrigerant to the cold evaporator with consequent liquid slugging on start-up. Both shall be insulated.

F. Compressor: Each module shall contain two hermetic scroll compressors independently circuited and with internal spring isolation mounted to the module with rubber-in-shear isolators. Each system also includes high discharge pressure and low suction pressure manual reset safety cut-outs.

G. Central Control System.1. Scheduling of the various compressors shall be performed by a microprocessor

based control system (Master Controller). A new lead compressor is selected every 24 hours to assure even distribution of compressor run time.

2. The Master Controller shall monitor and report the following on each refrigeration system:a. Discharge Pressure Faultb. Suction Pressure Fault

c. Compressor Winding Temperatured. Suction Temperaturee. Evaporator Leaving Chilled Water Temp.

3. The Master Controller shall be powered by the chillers single point power connection and shall monitor and report the following system parameters:a. Chilled Water Entering and Leaving Temperatureb. Condenser Water Entering and Leaving Temperaturec. Chilled Water and Condenser Water Flow Status

4. An out of tolerance indication from these controls or sensors shall cause a fault indication at the Master Controller and shutdown of that compressor with the transfer of load requirements to the next available compressor. In the case of a System Fault the entire chiller will be shut down. When a fault occurs, the Master Controller shall record conditions at the time of the fault and store the data for recall. This information shall be capable of being recalled through the keypad of the Master Controller and displayed on the Master Controller’s semi-graphical display. A history of faults shall be maintained including date and time of day of each fault (up to the last 20 occurrences).

5. Individual monitoring of leaving chilled water temperatures from each refrigeration system shall be programmed to protect against freeze-up.

6. The control system shall monitor entering and leaving hot and chilled water temperatures to determine system load and select the number of compressor circuits required to operate. Response times and set points shall be adjustable. The system shall provide for variable time between compressor sequencing and temperature sensing, so as to fine tune the chiller to different existing building conditions.

7. Optionally, the Chiller shall be capable of interfacing to a building automation system. Interface shall be accomplished using an Interoperability Web Portal and shall be capable of communication over BACNet, Modbus or LON.

H. Chiller shall have a single point power connection and external inputs and outputs to be compatible with the building management system. Inputs/Outputs include:

1. Remote Start/Stop2. Customer Alarm Relay3. Customer Hot/Chilled/Load Limit Reset Signal4. EHW to Mechanical Cooling Module5. LHW from Mechanical Cooling Module6. ECHW to Mechanical Cooling Module7. LCHW from Mechanical Cooling Module8. Power Phase Monitor9. Chilled Water Flow Switch Input

10. Condenser Water Flow Switch Input11. Full Load Indicator Relay12. Condenser Pump Relay13. Chilled Water Pump Relay

I. Each inlet water header shall incorporate a built in 30-mesh in-line strainer system to prevent heat exchanger fouling and accommodate 100% flow filtration with a minimum surface area of 475 sq inches per module.

J. Single Point Power: Chiller shall be equipped with a pre-engineered genuine buss bar electrical system for single point power. Where the equipment size exceeds the amp rating of the buss bar, multiple power connections may be applied. Pre-engineered system shall also incorporate individual module isolation circuit breakers for full redundancy and ability of a module to be taken off-line for repair while the rest of the modules continue to operate. Individual power feeds to each module shall be unacceptable.

MECHANICAL SPECIFICATIONS

30

Dedicated Heat Recovery Chiller™ (DHRC)MECHANICAL SPECIFICATIONS, cont’d

1.03 SAFETIES, CONTROLS AND OPERATIONA. Chiller safety controls system shall be provided with the unit (minimum) as

follows:1. Low evaporator refrigerant pressure2. Loss of flow through the evaporator3. Loss of flow through the condenser4. High condenser refrigerant pressure5. High compressor motor temperature6. Low suction gas temperature7. Low leaving evaporator water temperature

B. Failure of chiller to start or chiller shutdown due to any of the above safety cutouts shall be enunciated by display of the appropriate diagnostic description at the unit control panel. This annunciation will be in plain English. Alphanumeric codes shall be unacceptable.

C. The chiller shall be furnished with a Master Controller as an integral portion of the chiller control circuitry to provide the following functions:

1. Provide automatic chiller shutdown during periods when the load level decreases below the normal operating requirements of the chiller. Upon an increase in load, the chiller shall automatically restart.

2. Provisions for connection to automatically enable the chiller from a remote energy management system.

3. The control panel shall provide alphanumeric display showing all system parameters in the English language with numeric data in English units.

4. Each module shall contain a slave controller that will allow any module to run in the event of a master controller failure or loss of communication with the master controller via an on/off/manual toggle switch.

D. Dedicated Heat Recovery Controls (DHRC)1. The Dedicated Heat Recovery Chiller (DHRC) shall be equipped with a

microprocessor based return water controller. The Dedicated Heat Recovery Chiller shall have the capability to operate in response to either heating water or cooling water set points. The selection of these two modes of operation shall be made automatically by the Dedicated Heat Recovery Chiller’s Master Controller or alternatively, this mode may be set manually or through a binary input to the controller.

2. The control system shall monitor entering and leaving hot and/or chilled water temperatures to determine system load and select the number of compressor circuits required to operate. Response times and set points shall be adjustable. The system shall provide for variable time between compressor sequencing and temperature sensing, so as to fine tune the Dedicated Heat Recovery Chiller to different existing building conditions.

E. Power Phase Monitor1. Provide a Power Phase Monitor on the incoming power supply to the chiller.

This device shall prevent the chiller from operating during periods when the incoming power is unsuitable for proper operation.

2. The Power Phase Monitor shall provide protection against the following conditions:a. Low Voltage (Brown-Out)b. Phase Rotationc. Loss of Phased. Phase Imbalance

F. Optional—Variable Flow Operation--Chilled and/or Hot Water1. Butterfly type isolation valves shall incorporate appropriate accessories and

controls to allow the chiller to operate efficiently in a variable primary flow system. Valve shall modulate via a motorized actuator for leaving water temperature control, chiller minimum flow bypass, chiller no load bypass, or head pressure control.

G. Optional---Total Access Design1. Isolation valves shall be installed between the heat exchangers and

water supply mains for heat exchanger isolation and removal without the requirement to shut down the entire chiller allowing for total access to all serviceable components.

H. Optional---Double Wall Vented Condenser for Potable Water in DHRC (MS020 and MS030 only)

1.04 INSTALLATIONSPIPING SYSTEM FLUSHING PROCEDURE

A. Prior to connecting the chiller to the condenser and chilled water loop, the piping loops shall be flushed with a detergent and hot water (110-130° F) mixture to remove previously accumulated dirt and other organic materials. In old piping systems with heavy encrustation of inorganic materials consult a water treatment specialist for proper passivation and/or removal of these contaminants.

B. During the flushing 30-mesh (max.) Y-strainers (or acceptable Equivalent) shall be in place in the system piping and examined periodically as necessary to remove collected residue. The flushing process shall take no less than 6 hours or until the strainers, when examined after each flushing, are clean. Old systems with heavy encrustation shall be flushed for a minimum of 24 hours and may take as long as 48 hours before the filters run clean. Detergent and acid concentrations shall be used in strict accordance with the respective chemical manufacturer’s instructions. After flushing with the detergent and/or dilute acid concentrations the system loop shall be purged with clean water for at least one hour to ensure that all residual cleaning chemicals have been flushed out.

C. Prior to supplying water to the chiller the Water Treatment Specification shall be consulted for requirements regarding the water quality during chiller operation. The appropriate chiller manufacturer’s service literature shall be available to the operator and/or service contractor and consulted for guidelines concerning preventative maintenance and off-season shutdown procedures. The Y-strainer should remain in place for permanent operation.

1.05 WATER TREATMENT REQUIREMENTSA. Supply water for both the chilled water and condenser water circuits shall be

analyzed and treated by a professional water treatment specialist who is familiar with the operating conditions and materials of construction specified for the chiller’s heat exchangers, headers and associated piping. Cycles of concentration shall be controlled such that recirculated water quality for modular chillers using 316 stainless steel brazed plate heat exchangers and carbon steel headers is maintained within the following parameters:

1. pH Greater than 7 and less than 92. Total Dissolved Solids (TDS) Less than 1000 ppm3. Hardness as CaCO3 30 to 500 ppm4. Alkalinity as Ca CO3 30 to 500 ppm5. Chlorides Less than 200 ppm6. Sulfates Less than 200 ppm

31

Dedicated Heat Recovery Chiller™ (DHRC)ABOUT MULTISTACK

Originators…Multistack invented the modular water chiller. It started with a radically simple idea: chiller modules that could be brought into the equipment room one at a time, through standard doorways and down elevators, to form a fully integrated chiller system. The idea launched a revolution and transformed Multistack into a leader in the commercial water-chiller industry.

Innovators…Multistack perfected the modular chiller and leads the industry in innovative and environmentally friendly modular solutions. Since founding in the late 1980s, Multistack has engineered, manufactured, and distributed an impressive array of modular air conditioning firsts: the first on-board strainer, the first modular automatic blow-down device, the first modular chiller for variable flow, the first modular chiller-heater (heat pump), the first modular heat-recovery chiller, the first modular air-to-water heat pump, the first modular chiller to utilize MagLev™ compressor technology, and the first modular chiller to utilize R-410A.

Never the Imitators…Multistack sets the standard in the industry for superior customer service, fast and on time shipment, superior product quality, and new product development. Our pioneering leadership in environmental issues is well documented. If you want the best, be sure to specify the original – Multistack®.

Environmentally Friendly RefrigerantsR-410A and R-134aRefrigerant R-410A and R-134a are widely available, safe, and environmentally friendly refrigerants. R-410A is available in virtually all Multistack systems making hot water up to 140°F and R-134a is available in machines making hot water up to 180°F. Good environmental choices!

Environmental FocusIn addition to providing products to deliver reliable comfort and low operating cost, Multistack’s products can also reduce your environmental footprint. We are committed to developing and manufacturing cooling and heating products that can eliminate fossil fuel consumption and operate on the refrigerants designed to protect the environment. Dedicated heat pump boilers, air-to-water heat pumps and efficiency improvements across our product line are the result of this focus.

F164PC0311

1065 Maple Avenue P.O. Box 510 Sparta, WI 54656Phone 608-366-2400 • Fax 608-366-2450

www.multistack.com



Appendix 6

Conventional Central Plant Energy Cost Calculations

SYSTEM

Operating

Therms efficiency Input Rate Costs/Month

Month DAYS $/Therm ($)

31 PEAK 3968.0 0.95 4176.8 0.82 $3,425.01

28 PEAK 3584.0 0.95 3772.6 0.82 $3,093.56

31 PEAK 3968.0 0.95 4176.8 0.82 $3,425.01

30 PEAK 3840.0 0.95 4042.1 0.82 $3,314.53

31 PEAK 3968.0 0.95 4176.8 0.82 $3,425.01

30 PEAK 3840.0 0.95 4042.1 0.82 $3,314.53

31 PEAK 3968.0 0.95 4176.8 0.82 $3,425.01

31 PEAK 3968.0 0.95 4176.8 0.82 $3,425.01

CONVENTIONAL DHW BOILER

BOILER DHW

JUNE

JULY

AUG

MAR

APR

MAY

JAN

FEB

30 PEAK 3840.0 0.95 4042.1 0.82 $3,314.53

31 PEAK 3968.0 0.95 4176.8 0.82 $3,425.01

30 PEAK 3840.0 0.95 4042.1 0.82 $3,314.53

31 PEAK 3968.0 0.95 4176.8 0.82 $3,425.01

TOTAL $ $40,326.74

DEC

SEPT

OCT

NOV

SYSTEM SYSTEM

Operating Total Operating Operating Operating

EWT Load Therms efficiency Input Rate Costs/Day Load efficiency input Input Rate Costs/Day Costs/Day Costs/Month

Month DAYS (F) (btu) $/Therm ($) (ton‐hr) (kw/ton) (kw‐hr) (kw‐hr) ($/kw‐hr) ($) ($) ($)

off‐peak 11,037,332 110.4 0.9 122.6 0.82 $100.56 21.96774194 0.587 12.89506 12.9 0.07 $0.90 $101.47 $3,145.42

31 mid‐peak 9,908,416 99.1 0.9 110.1 0.82 $90.28 136.9548387 0.587 80.39249 80.4 0.08 $6.43 $96.71 $2,997.95

on‐peak 0 0.0 0.9 0.0 0.82 $0.00 0 0.587 0 0.0 0 $0.00 $0.00 $0.00

$190.84 $7.33 $6,143.37

off‐peak 10,273,982 102.7 0.9 114.2 0.82 $93.61 31.10714286 0.587 18.25989 18.3 0.07 $1.28 $94.89 $2,656.80

28 mid‐peak 8,376,132 83.8 0.9 93.1 0.82 $76.32 271.2928571 0.587 159.2489 159.2 0.08 $12.74 $89.06 $2,493.56

on‐peak 0 0.0 0.9 0.0 0.82 $0.00 0 0.587 0 0.0 0 $0.00 $0.00 $0.00

$169.92 $14.02 $5,150.36

off‐peak 7,495,342 75.0 0.9 83.3 0.82 $68.29 83.63870968 0.587 49.09592 49.1 0.07 $3.44 $71.73 $2,223.56

31 mid‐peak 5,951,600 59.5 0.9 66.1 0.82 $54.23 634.5483871 0.587 372.4799 372.5 0.08 $29.80 $84.02 $2,604.75

on‐peak 0 0.0 0.9 0.0 0.82 $0.00 0 0.587 0 0.0 0 $0.00 $0.00 $0.00

$122.52 $33.24 $4,828.30

off‐peak 8,254,570 82.5 0.9 91.7 0.82 $75.21 90.11666667 0.587 52.89848 52.9 0.07 $3.70 $78.91 $2,367.34

30 mid‐peak 6,730,997 67.3 0.9 74.8 0.82 $61.33 613.03 0.587 359.8486 359.8 0.08 $28.79 $90.11 $2,703.44

on‐peak 0 0.0 0.9 0.0 0.82 $0.00 0 0.587 0 0.0 0 $0.00 $0.00 $0.00

$136.54 $32.49 $5,070.78

off‐peak 7,487,094 74.9 0.9 83.2 0.82 $68.22 57.94516129 0.587 34.01381 34.0 0.08 $2.72 $70.94 $2,199.04

31 mid‐peak 1,323,826 13.2 0.9 14.7 0.82 $12.06 147.7096774 0.587 86.70558 86.7 0.1 $8.67 $20.73 $642.69

on‐peak 4,248,597 42.5 0.9 47.2 0.82 $38.71 407.7258065 0.587 239.335 239.3 0.14 $33.51 $72.22 $2,238.71

$118.99 $44.90 $5,080.44

off‐peak 5,590,247 55.9 0.9 62.1 0.82 $50.93 256.23 0.587 150.407 150.4 0.08 $12.03 $62.97 $1,888.98

30 mid‐peak 970,350 9.7 0.9 10.8 0.82 $8.84 314.3133333 0.587 184.5019 184.5 0.1 $18.45 $27.29 $818.73

on‐peak 3,293,737 32.9 0.9 36.6 0.82 $30.01 944.63 0.587 554.4978 554.5 0.14 $77.63 $107.64 $3,229.18

$89.78 $108.11 $5,936.89

Heating Cooling

JUNE 85

MAR 85

APR 85

MAY 85

CHILLER AND BOILER

CONVENTIONAL CHILLER/BOILER

JAN 85

FEB 85

off‐peak 5,445,477 54.5 0.9 60.5 0.82 $49.61 324.0709677 0.587 190.2297 190.2 0.08 $15.22 $64.83 $2,009.81

31 mid‐peak 947,461 9.5 0.9 10.5 0.82 $8.63 316.2419355 0.587 185.634 185.6 0.1 $18.56 $27.20 $843.07

on‐peak 3,126,884 31.3 0.9 34.7 0.82 $28.49 982.3032258 0.587 576.612 576.6 0.14 $80.73 $109.22 $3,385.67

$86.74 $114.51 $6,238.55

off‐peak 4,811,374 48.1 0.9 53.5 0.82 $43.84 359.5032258 0.587 211.0284 211.0 0.08 $16.88 $60.72 $1,882.30

31 mid‐peak 993,942 9.9 0.9 11.0 0.82 $9.06 370.3225806 0.587 217.3794 217.4 0.1 $21.74 $30.79 $954.61

on‐peak 3,133,287 31.3 0.9 34.8 0.82 $28.55 1241.93871 0.587 729.018 729.0 0.14 $102.06 $130.61 $4,048.92

$81.44 $140.68 $6,885.82

off‐peak 3,743,500 37.4 0.9 41.6 0.82 $34.11 689.6202151 0.587 404.8071 404.8 0.08 $32.38 $66.49 $1,994.76

30 mid‐peak 1,199,767 12.0 0.9 13.3 0.82 $10.93 560.7066667 0.587 329.1348 329.1 0.1 $32.91 $43.84 $1,315.34

on‐peak 3,842,880 38.4 0.9 42.7 0.82 $35.01 1675.326667 0.587 983.4168 983.4 0.14 $137.68 $172.69 $5,180.74

$80.05 $202.98 $8,490.84

off‐peak 6,630,958 66.3 0.9 59.7 0.82 $48.94 157.316129 0.587 92.34457 92.3 0.08 $7.39 $56.32 $1,746.05

31 mid‐peak 1,125,129 11.3 0.9 10.1 0.82 $8.30 234.9806452 0.587 137.9336 137.9 0.1 $13.79 $22.10 $685.00

on‐peak 3,680,565 36.8 0.9 33.1 0.82 $27.16 724.9903226 0.587 425.5693 425.6 0.14 $59.58 $86.74 $2,689.01

$84.40 $80.76 $5,120.06

off‐peak 8,662,410 86.6 0.9 78.0 0.82 $63.93 46.73333333 0.587 27.43247 27.4 0.07 $1.92 $65.85 $1,975.47

30 mid‐peak 7,178,960 71.8 0.9 64.6 0.82 $52.98 313.46 0.587 184.001 184.0 0.08 $14.72 $67.70 $2,031.02

on‐peak 0 0.0 0.9 0.0 0.82 $0.00 0 0.587 0 0.0 0 $0.00 $0.00 $0.00

$116.91 $16.64 $4,006.49

off‐peak 9,916,561 99.2 0.9 89.2 0.82 $73.18 40.88709677 0.587 24.00073 113.2 0.07 $7.93 $81.11 $2,514.46

31 mid‐peak 8,625,890 86.3 0.9 77.6 0.82 $63.66 186.0483871 0.587 109.2104 186.8 0.08 $14.95 $78.61 $2,436.80

on‐peak 0 0.0 0.9 0.0 0.82 $0.00 0 0.587 0 0.0 0 $0.00 $0.00 $0.00

$136.84 $22.87 $4,951.27

TOTAL $ $67,903.17

DEC 85

SEPT 85

OCT 85

NOV 85

JULY 85

AUG 85

SYSTEM

Operating Operating

Load Load input Rate Costs/Day Costs/Month

Month DAYS (ton‐hr) (kw/ton) (kw‐hr) ($/kw‐hr) ($) ($)

off‐peak 21.97 0.044 0.966581 0.07 $0.07 $2.10

31 mid‐peak 136.95 0.044 6.026013 0.08 $0.48 $14.94

on‐peak 0.00 0.044 0 0 $0.00 $0.00

$0.55 $17.04

off‐peak 31.11 0.044 1.368714 0.07 $0.10 $2.68

28 mid‐peak 271.29 0.044 11.93689 0.08 $0.95 $26.74

on‐peak 0.00 0.044 0 0 $0.00 $0.00

$1.05 $29.42

off‐peak 83.64 0.044 3.680103 0.07 $0.26 $7.99

31 mid‐peak 634.55 0.044 27.92013 0.08 $2.23 $69.24

on‐peak 0.00 0.044 0 0 $0.00 $0.00

$2.49 $77.23

off‐peak 90.12 0.044 3.965133 0.07 $0.28 $8.33

30 mid‐peak 613.03 0.044 26.97332 0.08 $2.16 $64.74

on‐peak 0.00 0.044 0 0 $0.00 $0.00

703.15 $2.44 $73.06

off‐peak 57.95 0.044 2.549587 0.08 $0.20 $6.32

31 mid‐peak 147.71 0.044 6.499226 0.1 $0.65 $20.15

on‐peak 407.73 0.044 17.93994 0.14 $2.51 $77.86

$3.37 $104.33

off‐peak 256.23 0.044 11.27412 0.08 $0.90 $27.06

30 mid‐peak 314.31 0.044 13.82979 0.1 $1.38 $41.49

on‐peak 944.63 0.044 41.56372 0.14 $5.82 $174.57

$8.10 $243.11

off‐peak 324.07 0.044 14.25912 0.08 $1.14 $35.36

31 mid‐peak 316.24 0.044 13.91465 0.1 $1.39 $43.14

on‐peak 982.30 0.044 43.22134 0.14 $6.05 $187.58

$8.58 $266.08

off‐peak 359.50 0.044 15.81814 0.08 $1.27 $39.23

31 mid‐peak 370.32 0.044 16.29419 0.1 $1.63 $50.51

on‐peak 1241.94 0.044 54.6453 0.14 $7.65 $237.16

$10.55 $326.90

JULY

AUG

CONVENTIONAL CHILLER CONDENSER PUMP

APR

MAY

JUNE

CONDENSER PUMP

JAN

FEB

MAR

off‐peak 689.62 0.044 30.34329 0.08 $2.43 $72.82

30 mid‐peak 560.71 0.044 24.67109 0.1 $2.47 $74.01

on‐peak 1675.33 0.044 73.71437 0.14 $10.32 $309.60

$15.21 $456.44

off‐peak 157.32 0.044 6.92191 0.08 $0.55 $17.17

31 mid‐peak 234.98 0.044 10.33915 0.1 $1.03 $32.05

on‐peak 724.99 0.044 31.89957 0.14 $4.47 $138.44

$6.05 $187.66

off‐peak 46.73 0.044 2.056267 0.07 $0.14 $4.32

30 mid‐peak 313.46 0.044 13.79224 0.08 $1.10 $33.10

on‐peak 0.00 0.044 0 0 $0.00 $0.00

$1.25 $37.42

off‐peak 40.89 0.044 1.799032 0.07 $0.13 $3.90

31 mid‐peak 186.05 0.044 8.186129 0.08 $0.65 $20.30

on‐peak 0.00 0.044 0 0 $0.00 $0.00

$0.78 $24.21

TOTAL $1,842.90

OCT

NOV

DEC

SEPT

SYSTEM

Operating Operating



off‐peak 21.97 0.067 1.471839 0.07 $0.10 $3.19

31 mid‐peak 136.95 0.067 9.175974 0.08 $0.73 $22.76

on‐peak 0.00 0.067 0 0 $0.00 $0.00

$0.84 $25.95

off‐peak 31.11 0.067 2.084179 0.07 $0.15 $4.08

28 mid‐peak 271.29 0.067 18.17662 0.08 $1.45 $40.72

on‐peak 0.00 0.067 0 0 $0.00 $0.00

$1.60 $44.80

off‐peak 83.64 0.067 5.603794 0.07 $0.39 $12.16

31 mid‐peak 634.55 0.067 42.51474 0.08 $3.40 $105.44

on‐peak 0.00 0.067 0 0 $0.00 $0.00

$3.79 $117.60

off‐peak 90.12 0.067 6.037817 0.07 $0.42 $12.68

30 mid‐peak 613.03 0.067 41.07301 0.08 $3.29 $98.58

on‐peak 0.00 0.067 0 0 $0.00 $0.00

$3.71 $111.25

off‐peak 57.95 0.067 3.882326 0.08 $0.31 $9.63

31 mid‐peak 147.71 0.067 9.896548 0.1 $0.99 $30.68

on‐peak 407.73 0.067 27.31763 0.14 $3.82 $118.56

$5.12 $158.87

off‐peak 256.23 0.067 17.16741 0.08 $1.37 $41.20

30 mid‐peak 314.31 0.067 21.05899 0.1 $2.11 $63.18

on‐peak 944.63 0.067 63.29021 0.14 $8.86 $265.82

$12.34 $370.20

off‐peak 324.07 0.067 21.71275 0.08 $1.74 $53.85

31 mid‐peak 316.24 0.067 21.18821 0.1 $2.12 $65.68

on‐peak 982.30 0.067 65.81432 0.14 $9.21 $285.63

$13.07 $405.17

off‐peak 359.50 0.067 24.08672 0.08 $1.93 $59.74

31 mid‐peak 370.32 0.067 24.81161 0.1 $2.48 $76.92

on‐peak 1241.94 0.067 83.20989 0.14 $11.65 $361.13

$16.06 $497.78

JUNE

JULY

AUG

COOLING TOWER

CONVENTIONAL CHILLER COOLING TOWER

MAR

APR

MAY

JAN

FEB

off‐peak 689.62 0.067 46.20455 0.08 $3.70 $110.89

30 mid‐peak 560.71 0.067 37.56735 0.1 $3.76 $112.70

on‐peak 1675.33 0.067 112.2469 0.14 $15.71 $471.44

$23.17 $695.03

off‐peak 157.32 0.067 10.54018 0.08 $0.84 $26.14

31 mid‐peak 234.98 0.067 15.7437 0.1 $1.57 $48.81

on‐peak 724.99 0.067 48.57435 0.14 $6.80 $210.81

$9.22 $285.76

off‐peak 46.73 0.067 3.131133 0.07 $0.22 $6.58

30 mid‐peak 313.46 0.067 21.00182 0.08 $1.68 $50.40

on‐peak 0.00 0.067 0 0 $0.00 $0.00

$1.90 $56.98

off‐peak 40.89 0.067 2.739435 0.07 $0.19 $5.94

31 mid‐peak 186.05 0.067 12.46524 0.08 $1.00 $30.91

on‐peak 0.00 0.067 0 0 $0.00 $0.00

$1.19 $36.86

TOTAL $2,806.24

DEC

SEPT

OCT

NOV



Appendix 7

Geothermal Central Plant Energy Cost Calculations

Total Operating

EWT Monthly Therms LOAD Ton‐Hr efficiency input Input Rate Costs/Month

Month DAYS (F) Therms Btu (kw/ton) (kw‐hr) (kw‐hr) ($/kw‐hr) ($)

off‐peak 1,250 124971129.3 10414.3 0.98 10206.0 10206.0 0.07 $714.42

31 3968.0 mid‐peak 2,718 271828870.7 22652.4 0.98 22199.4 22199.4 0.08 $1,775.95

on‐peak 0 0.0 0.0 0.98 0.0 0.0 0 $0.00

$2,490.37

off‐peak 1,129 112877149.0 9406.4 0.98 9218.3 9218.3 0.07 $645.28

28 3584.0 mid‐peak 2,455 245522851.0 20460.2 0.98 20051.0 20051.0 0.08 $1,604.08

on‐peak 0 0.0 0.0 0.98 0.0 0.0 0 $0.00

$2,249.36

off‐peak 1,250 124971129.3 10414.3 0.98 10206.0 10206.0 0.07 $714.42

31 3968.0 mid‐peak 2,718 271828870.7 22652.4 0.98 22199.4 22199.4 0.08 $1,775.95

on‐peak 0 0.0 0.0 0.98 0.0 0.0 0 $0.00

$2,490.37

off‐peak 1,209 120939802.5 10078.3 0.85 8566.6 8566.6 0.07 $599.66

30 3840.0 mid‐peak 2,631 263060197.5 21921.7 0.85 18633.4 18633.4 0.08 $1,490.67

on‐peak 0 0.0 0.0 0.85 0.0 0.0 0 $0.00

$2,090.33

off‐peak 1,489 148896883.3 12408.1 0.8 9926.5 9926.5 0.08 $794.12

31 3968.0 mid‐peak 563 56343653.5 4695.3 0.8 3756.2 3756.2 0.1 $375.62

on‐peak 1,916 191559463.2 15963.3 0.8 12770.6 12770.6 0.14 $1,787.89

$2,957.63

off‐peak 1,441 144093758.0 12007.8 0.75 9005.9 9005.9 0.08 $720.47

30 3840.0 mid‐peak 545 54526116.3 4543.8 0.75 3407.9 3407.9 0.1 $340.79

on‐peak 1,854 185380125.7 15448.3 0.75 11586.3 11586.3 0.14 $1,622.08

$2,683.33

off‐peak 1,489 148896883.3 12408.1 0.67 8313.4 8313.4 0.08 $665.07

31 3968.0 mid‐peak 563 56343653.5 4695.3 0.67 3145.9 3145.9 0.1 $314.59

on‐peak 1,916 191559463.2 15963.3 0.67 10695.4 10695.4 0.14 $1,497.36

$2,477.01

off‐peak 1,489 148896883.3 12408.1 0.67 8313.4 8313.4 0.08 $665.07

31 3968.0 mid‐peak 563 56343653.5 4695.3 0.67 3145.9 3145.9 0.1 $314.59

on‐peak 1,916 191559463.2 15963.3 0.67 10695.4 10695.4 0.14 $1,497.36

$2,477.01

off‐peak 1,441 144093758.0 12007.8 0.67 8045.2 8045.2 0.08 $643.62

30 3840.0 mid‐peak 545 54526116.3 4543.8 0.67 3044.4 3044.4 0.1 $304.44

on‐peak 1,854 185380125.7 15448.3 0.67 10350.4 10350.4 0.14 $1,449.05

$2,397.11

off‐peak 1,344 134350651.8 11195.9 0.67 7501.2 7501.2 0.08 $600.10

31 3968.0 mid‐peak 636 63600031.0 5300.0 0.67 3551.0 3551.0 0.1 $355.10

on‐peak 1,988 198849317.2 16570.8 0.67 11102.4 11102.4 0.14 $1,554.34

$2,509.54

off‐peak 1,209 120939802.5 10078.3 0.67 6752.5 6752.5 0.07 $472.67

30 3840.0 mid‐peak 2,631 263060197.5 21921.7 0.67 14687.5 14687.5 0.08 $1,175.00

on‐peak 0 0.0 0.0 0.67 0.0 0.0 0 $0.00

$1,647.68

off‐peak 1,250 124971129.3 10414.3 0.8 8331.4 8331.4 0.07 $583.20

31 3968.0 mid‐peak 2,718 271828870.7 22652.4 0.8 18121.9 18121.9 0.08 $1,449.75

on‐peak 0 0.0 0.0 0.8 0.0 0.0 0 $0.00

$2,032.95

TOTAL $28,502.70

ADJUSTED TOTAL* $11,401.08

DEC 78

93

AUG 93

SEPT 93

OCT 93

NOV 93

* In the operation of the geothermal system, approximately 60% of the domestic water

heating will occur simultaneously with cooling. The waste heat of the cooling process

will be used to preheat the DHW. Therefore the $28,502.70 DHW heating cost is

redcued to 40%. This value has been entered in the System Cost Comparison in

Appendix 3.

GEOTHERMAL DHW

Heating

JAN 58

FEB 58

MAR 58

APR 70

MAY 78

JUNE 83

JULY

Total Operating Operating

EWT Load Load efficiency input Load efficiency input Input Rate Costs/Day Costs/Month

Month DAYS (F) (btu) (ton‐hr) (kw/ton) (kw‐hr) (ton‐hr) (kw/ton) (kw‐hr) (kw‐hr) ($/kw‐hr) ($) ($)

off‐peak 11,037,332 919.8 1.05 965.8 21.96774194 0.58 12.74129 978.5 0.07 $68.50 $2,123.36

31 mid‐peak 9,908,416 825.7 1.05 867.0 136.9548387 0.58 79.43381 946.4 0.08 $75.71 $2,347.12

on‐peak 0 0.0 1.05 0.0 0 0.58 0 0.0 0 $0.00 $0.00

$144.21 $4,470.48

off‐peak 10,273,982 856.2 1.05 899.0 31.10714286 0.58 18.04214 917.0 0.07 $64.19 $1,797.35

28 mid‐peak 8,376,132 698.0 1.05 732.9 271.2928571 0.58 157.3499 890.3 0.08 $71.22 $1,994.19

on‐peak 0 0.0 1.05 0.0 0 0.58 0 0.0 0 $0.00 $0.00

$135.41 $3,791.54

off‐peak 7,495,342 624.6 1.05 655.8 83.63870968 0.58 48.51045 704.4 0.07 $49.30 $1,528.45

31 mid‐peak 5,951,600 496.0 1.05 520.8 634.5483871 0.58 368.0381 888.8 0.08 $71.10 $2,204.23

on‐peak 0 0.0 1.05 0.0 0 0.58 0 0.0 0 $0.00 $0.00

$120.41 $3,732.68

off‐peak 8,254,570 687.9 1.05 722.3 90.11666667 0.58 52.26767 774.5 0.07 $54.22 $1,626.54

30 mid‐peak 6,730,997 560.9 1.05 589.0 613.03 0.58 355.5574 944.5 0.08 $75.56 $2,266.85

on‐peak 0 0.0 1.05 0.0 0 0.58 0 0.0 0 $0.00 $0.00

$129.78 $3,893.39

off‐peak 7,487,094 623.9 0.8 499.1 57.94516129 0.72 41.72052 540.9 0.08 $43.27 $1,341.33

31 mid‐peak 1,323,826 110.3 0.8 88.3 147.7096774 0.72 106.351 194.6 0.1 $19.46 $603.28

on‐peak 4,248,597 354.0 0.8 283.2 407.7258065 0.72 293.5626 576.8 0.14 $80.75 $2,503.32

$143.48 $4,447.93

off‐peak 5,590,247 465.9 0.75 349.4 256.23 0.78 199.8594 549.2 0.08 $43.94 $1,318.20

30 mid‐peak 970,350 80.9 0.75 60.6 314.3133333 0.78 245.1644 305.8 0.1 $30.58 $917.43

on‐peak 3,293,737 274.5 0.75 205.9 944.63 0.78 736.8114 942.7 0.14 $131.97 $3,959.21

$206.49 $6,194.85

off‐peak 5,445,477 453.8 0.67 304.0 324.0709677 0.78 252.7754 556.8 0.08 $44.55 $1,380.90

31 mid‐peak 947,461 79.0 0.67 52.9 316.2419355 0.78 246.6687 299.6 0.1 $29.96 $928.66

on‐peak 3,126,884 260.6 0.67 174.6 982.3032258 0.78 766.1965 940.8 0.14 $131.71 $4,082.99

$206.21 $6,392.55

off‐peak 4,811,374 400.9 0.67 268.6 359.5032258 0.78 280.4125 549.0 0.08 $43.92 $1,361.64

31 mid‐peak 993,942 82.8 0.67 55.5 370.3225806 0.78 288.8516 344.3 0.1 $34.43 $1,067.47AUG 83

MAY 78

JUNE 83

JULY 83

FEB 53

MAR 53

APR 53

GEOTHERMAL HEAT PUMP HEATING AND COOLING

Heating Cooling

JAN 53

on‐peak 3,133,287 261.1 0.67 174.9 1241.93871 0.78 968.7122 1143.7 0.14 $160.11 $4,963.46

$238.47 $7,392.57

off‐peak 3,743,500 312.0 0.67 209.0 689.6202151 0.78 537.9038 746.9 0.08 $59.75 $1,792.60

30 mid‐peak 1,199,767 100.0 0.67 67.0 560.7066667 0.78 437.3512 504.3 0.1 $50.43 $1,513.01

on‐peak 3,842,880 320.2 0.67 214.6 1675.326667 0.78 1306.755 1521.3 0.14 $212.98 $6,389.53

$323.17 $9,695.14

off‐peak 6,630,958 552.6 0.67 370.2 157.316129 0.78 122.7066 492.9 0.08 $39.43 $1,222.48

31 mid‐peak 1,125,129 93.8 0.67 62.8 234.9806452 0.78 183.2849 246.1 0.1 $24.61 $762.92

on‐peak 3,680,565 306.7 0.67 205.5 724.9903226 0.78 565.4925 771.0 0.14 $107.94 $3,346.10

$171.98 $5,331.50

off‐peak 8,662,410 721.9 0.75 541.4 46.73333333 0.78 36.452 577.9 0.07 $40.45 $1,213.49

30 mid‐peak 7,178,960 598.2 0.75 448.7 313.46 0.78 244.4988 693.2 0.08 $55.45 $1,663.64

on‐peak 0 0.0 0.75 0.0 0 0.78 0 0.0 0 $0.00 $0.00

$95.90 $2,877.13

off‐peak 9,916,561 826.4 0.8 661.1 40.88709677 0.72 29.43871 690.5 0.07 $48.34 $1,498.48

31 mid‐peak 8,625,890 718.8 0.8 575.1 186.0483871 0.72 133.9548 709.0 0.08 $56.72 $1,758.36

on‐peak 0 0.0 0.8 0.0 0 0.72 0 0.0 0 $0.00 $0.00

$105.06 $3,256.83

TOTAL $ $61,476.59

DEC 78

NOV 83

SEPT 83

OCT 83

SYSTEM

Operating Operating



off‐peak 21.96774194 0.057 1.252161 0.07 $0.09 $2.72

31 mid‐peak 136.9548387 0.057 7.806426 0.08 $0.62 $19.36

on‐peak 0 0.057 0 0 $0.00 $0.00

$0.71 $22.08

off‐peak 31.10714286 0.057 1.773107 0.07 $0.12 $3.48

28 mid‐peak 271.2928571 0.057 15.46369 0.08 $1.24 $34.64

on‐peak 0 0.057 0 0 $0.00 $0.00

$1.36 $38.11

off‐peak 83.63870968 0.057 4.767406 0.07 $0.33 $10.35

31 mid‐peak 634.5483871 0.057 36.16926 0.08 $2.89 $89.70

on‐peak 0 0.057 0 0 $0.00 $0.00

$3.23 $100.05

off‐peak 90.11666667 0.057 5.13665 0.07 $0.36 $10.79

30 mid‐peak 613.03 0.057 34.94271 0.08 $2.80 $83.86

on‐peak 0 0.057 0 0 $0.00 $0.00

703.1466667 $3.15 $94.65

off‐peak 57.94516129 0.057 3.302874 0.08 $0.26 $8.19

31 mid‐peak 147.7096774 0.057 8.419452 0.1 $0.84 $26.10

on‐peak 407.7258065 0.057 23.24037 0.14 $3.25 $100.86

$4.36 $135.15

off‐peak 256.23 0.057 14.60511 0.08 $1.17 $35.05

30 mid‐peak 314.3133333 0.057 17.91586 0.1 $1.79 $53.75

on‐peak 944.63 0.057 53.84391 0.14 $7.54 $226.14

$10.50 $314.94

off‐peak 324.0709677 0.057 18.47205 0.08 $1.48 $45.81

31 mid‐peak 316.2419355 0.057 18.02579 0.1 $1.80 $55.88

on‐peak 982.3032258 0.057 55.99128 0.14 $7.84 $243.00

$11.12 $344.69

off‐peak 359.5032258 0.057 20.49168 0.08 $1.64 $50.82

31 mid‐peak 370.3225806 0.057 21.10839 0.1 $2.11 $65.44

on‐peak 1241.93871 0.057 70.79051 0.14 $9.91 $307.23

1971.764516 $13.66 $423.49

GEOTHERMAL CONDENSER PUMP

CONDENSER PUMP

JAN

FEB

MAR

APR

MAY

JUNE

JULY

AUG

off‐peak 689.6202151 0.057 39.30835 0.08 $3.14 $94.34

30 mid‐peak 560.7066667 0.057 31.96028 0.1 $3.20 $95.88

on‐peak 1675.326667 0.057 95.49362 0.14 $13.37 $401.07

$19.71 $591.29

off‐peak 157.316129 0.057 8.967019 0.08 $0.72 $22.24

31 mid‐peak 234.9806452 0.057 13.3939 0.1 $1.34 $41.52

on‐peak 724.9903226 0.057 41.32445 0.14 $5.79 $179.35

$7.84 $243.11

off‐peak 46.73333333 0.057 2.6638 0.07 $0.19 $5.59

30 mid‐peak 313.46 0.057 17.86722 0.08 $1.43 $42.88

on‐peak 0 0.057 0 0 $0.00 $0.00

$1.62 $48.48

off‐peak 40.88709677 0.057 2.330565 0.07 $0.16 $5.06

31 mid‐peak 186.0483871 0.057 10.60476 0.08 $0.85 $26.30

on‐peak 0 0.057 0 0 $0.00 $0.00

$1.01 $31.36

TOTAL $2,387.40

DEC

NOV

SEPT

OCT

Operating

Hours Demand Load Rate Costs/year

kW (ton‐hr) ($/kw‐hr) ($)

1580 16.1 25438 0.08 $2,035.04

$2,035.04

GEOTHERMAL COOLING TOWER

FULL YEAR

GEOTHERMAL COOLING TOWER



Appendix 8

Building Heating and Cooling Loads

BUILDING HEATING AND COOLING LOADS

JANUARY DAYS IN MONTH 31 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE

AVERAGE DAY HEATING LOAD HEATING LOAD Cooling Load Cooling Load

RATE LEVEL BTU/H Therms Clg (Tons) Ton-hrs

OFF PEAK 929461.29 9.29 0.00 0.00

OFF PEAK 965338.71 9.65 0.00 0.00

OFF PEAK 996174.19 9.96 1.45 1.45

OFF PEAK 1030116.13 10.30 0.00 0.00

OFF PEAK 1040580.65 10.41 0.00 0.00

OFF PEAK 998887.10 9.99 0.00 0.00

OFF PEAK 1047654.84 10.48 0.00 0.00

OFF PEAK 1179687.10 11.80 1.69 1.69

OFF PEAK 1033996.77 10.34 3.06 3.06

OFF PEAK 936032.26 9.36 15.76 15.76

MID PEAK 856177.42 8.56 18.91 18.91

MID PEAK 805296.77 8.05 25.13 25.13

MID PEAK 802025.81 8.02 18.87 18.87

MID PEAK 748487.10 7.48 21.35 21.35

MID PEAK 732238.71 7.32 20.49 20.49

MID PEAK 749583.87 7.50 16.21 16.21

MID PEAK 764203.23 7.64 6.06 6.06

MID PEAK 766645.16 7.67 1.48 1.48

MID PEAK 724635.48 7.25 3.62 3.62

MID PEAK 690022.58 6.90 1.82 1.82

MID PEAK 711680.65 7.12 1.55 1.55

MID PEAK 747196.77 7.47 1.46 1.46

MID PEAK 810222.58 8.10 0.00 0.00

OFF PEAK 879403.23 8.79 0.00 0.002324

2122

1920

12

910

78

1718

1516

1314

Hour

56

3

4

1

2

11


FEBRUARY DAYS IN MONTH 28 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 843232.14 8.43 1.14 1.14

OFF PEAK 900139.29 9.00 0.00 0.00

OFF PEAK 938707.14 9.39 1.13 1.13

OFF PEAK 965675.00 9.66 0.00 0.00

OFF PEAK 985967.86 9.86 0.00 0.00

OFF PEAK 964703.57 9.65 0.00 0.00

OFF PEAK 1001621.43 10.02 0.00 0.00

OFF PEAK 1115271.43 11.15 0.00 0.00

OFF PEAK 941625.00 9.42 7.88 7.88

OFF PEAK 827157.14 8.27 18.68 18.68

MID PEAK 748846.43 7.49 20.83 20.83

MID PEAK 676564.29 6.77 31.44 31.44

MID PEAK 644289.29 6.44 31.07 31.07

MID PEAK 607567.86 6.08 40.44 40.44

MID PEAK 576407.14 5.76 42.21 42.21

MID PEAK 577382.14 5.77 41.05 41.05

MID PEAK 554653.57 5.55 36.41 36.41

MID PEAK 669650.00 6.70 16.55 16.55

MID PEAK 642996.43 6.43 6.37 6.37

MID PEAK 624271.43 6.24 2.66 2.66

MID PEAK 654125.00 6.54 2.27 2.27

MID PEAK 679189.29 6.79 0.00 0.00

MID PEAK 720189.29 7.20 0.00 0.00

OFF PEAK 789882.14 7.90 2.28 2.28

2122

1920

1718

2324

910

78

56

1516

1314

1112

3

4

1

2

Hour


MARCH DAYS IN MONTH 31 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 599522.58 6.00 7.29 7.29

OFF PEAK 643077.42 6.43 4.73 4.73

OFF PEAK 669022.58 6.69 3.20 3.20

OFF PEAK 692970.97 6.93 2.01 2.01

OFF PEAK 697738.71 6.98 0.93 0.93

OFF PEAK 698596.77 6.99 0.00 0.00

OFF PEAK 730932.26 7.31 3.00 3.00

OFF PEAK 818141.94 8.18 5.70 5.70

OFF PEAK 708103.23 7.08 17.51 17.51

OFF PEAK 656874.19 6.57 30.92 30.92

MID PEAK 533709.68 5.34 41.49 41.49

MID PEAK 456003.23 4.56 51.75 51.75

MID PEAK 426338.71 4.26 59.15 59.15

MID PEAK 403816.13 4.04 70.07 70.07

MID PEAK 400358.06 4.00 81.87 81.87

MID PEAK 425619.35 4.26 82.83 82.83

MID PEAK 382087.10 3.82 79.84 79.84

MID PEAK 416232.26 4.16 66.00 66.00

MID PEAK 457158.06 4.57 43.35 43.35

MID PEAK 494148.39 4.94 22.24 22.24

MID PEAK 499867.74 5.00 15.30 15.30

MID PEAK 524267.74 5.24 11.85 11.85

MID PEAK 531993.55 5.32 8.81 8.81

OFF PEAK 580361.29 5.80 8.35 8.35

1920

1718

1516

2324

2122

78

56

3

4

1314

1112

910

1

2

Hour


APRIL DAYS IN MONTH 30 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 665823.33 6.66 7.23 7.23

OFF PEAK 722926.67 7.23 5.43 5.43

OFF PEAK 747413.33 7.47 5.86 5.86

OFF PEAK 790300.00 7.90 3.63 3.63

OFF PEAK 799156.67 7.99 3.20 3.20

OFF PEAK 804523.33 8.05 1.11 1.11

OFF PEAK 826070.00 8.26 2.39 2.39

OFF PEAK 881456.67 8.81 5.65 5.65

OFF PEAK 719336.67 7.19 15.99 15.99

OFF PEAK 667450.00 6.67 30.36 30.36

MID PEAK 589763.33 5.90 41.29 41.29

MID PEAK 542130.00 5.42 55.43 55.43

MID PEAK 512950.00 5.13 63.56 63.56

MID PEAK 498756.67 4.99 74.07 74.07

MID PEAK 490830.00 4.91 73.55 73.55

MID PEAK 497866.67 4.98 75.22 75.22

MID PEAK 445970.00 4.46 75.63 75.63

MID PEAK 472246.67 4.72 57.43 57.43

MID PEAK 505596.67 5.06 39.31 39.31

MID PEAK 508866.67 5.09 23.76 23.76

MID PEAK 530416.67 5.30 13.51 13.51

MID PEAK 557546.67 5.58 10.60 10.60

MID PEAK 578056.67 5.78 9.67 9.67

OFF PEAK 630113.33 6.30 9.27 9.27

1718

1516

1314

2324

2122

1920

56

3

4

1

2

1112

910

78

Hour


MAY DAYS IN MONTH 31 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 616477.42 6.16 1.10 1.10

OFF PEAK 668474.19 6.68 1.77 1.77

OFF PEAK 675696.77 6.76 0.00 0.00

OFF PEAK 714593.55 7.15 0.00 0.00

OFF PEAK 718900.00 7.19 0.00 0.00

OFF PEAK 718900.00 7.19 0.00 0.00

OFF PEAK 722109.68 7.22 0.86 0.86

OFF PEAK 762051.61 7.62 10.07 10.07

OFF PEAK 655806.45 6.56 18.46 18.46

OFF PEAK 629812.90 6.30 24.68 24.68

MID PEAK 514958.06 5.15 39.83 39.83

MID PEAK 435138.71 4.35 50.47 50.47

MID PEAK 373729.03 3.74 57.41 57.41

ON PEAK 367119.35 3.67 66.81 66.81

ON PEAK 352116.13 3.52 72.36 72.36

ON PEAK 346845.16 3.47 76.25 76.25

ON PEAK 316567.74 3.17 73.68 73.68

ON PEAK 356358.06 3.56 57.00 57.00

ON PEAK 404541.94 4.05 34.56 34.56

ON PEAK 506312.90 5.06 14.68 14.68

ON PEAK 521216.13 5.21 5.19 5.19

ON PEAK 515764.52 5.16 4.27 4.27

ON PEAK 561754.84 5.62 2.91 2.91

OFF PEAK 604270.97 6.04 0.99 0.992324

1516

1314

1112

2122

1920

1718

3

4

1

2

Hour

910

78

56


JUNE DAYS IN MONTH 30 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 503750.00 5.04 16.02 16.02

OFF PEAK 517216.67 5.17 14.86 14.86

OFF PEAK 524733.33 5.25 16.16 16.16

OFF PEAK 559653.33 5.60 14.74 14.74

OFF PEAK 582030.00 5.82 13.09 13.09

OFF PEAK 576186.67 5.76 8.85 8.85

OFF PEAK 567950.00 5.68 16.57 16.57

OFF PEAK 553766.67 5.54 34.60 34.60

OFF PEAK 387663.33 3.88 46.08 46.08

OFF PEAK 350760.00 3.51 57.69 57.69

MID PEAK 316540.00 3.17 81.51 81.51

MID PEAK 317503.33 3.18 110.47 110.47

MID PEAK 336306.67 3.36 122.34 122.34

ON PEAK 354766.67 3.55 137.44 137.44

ON PEAK 353640.00 3.54 147.00 147.00

ON PEAK 360120.00 3.60 151.48 151.48

ON PEAK 305530.00 3.06 152.98 152.98

ON PEAK 312226.67 3.12 129.81 129.81

ON PEAK 305123.33 3.05 87.87 87.87

ON PEAK 272063.33 2.72 57.96 57.96

ON PEAK 262800.00 2.63 38.05 38.05

ON PEAK 350153.33 3.50 24.70 24.70

ON PEAK 417313.33 4.17 17.34 17.34

OFF PEAK 466536.67 4.67 17.58 17.582324

2122

1314

1112

910

1920

1718

1516

1

2

Hour

78

56

3

4


JULY DAYS IN MONTH 31 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 473712.90 4.74 24.92 24.92

OFF PEAK 497438.71 4.97 25.65 25.65

OFF PEAK 491693.55 4.92 23.63 23.63

OFF PEAK 522280.65 5.22 22.86 22.86

OFF PEAK 546770.97 5.47 21.54 21.54

OFF PEAK 541545.16 5.42 16.62 16.62

OFF PEAK 536593.55 5.37 21.03 21.03

OFF PEAK 549493.55 5.49 36.92 36.92

OFF PEAK 435429.03 4.35 48.62 48.62

OFF PEAK 368761.29 3.69 57.69 57.69

MID PEAK 324648.39 3.25 82.99 82.99

MID PEAK 304806.45 3.05 109.59 109.59

MID PEAK 318006.45 3.18 123.66 123.66

ON PEAK 332906.45 3.33 138.69 138.69

ON PEAK 334319.35 3.34 149.22 149.22

ON PEAK 331722.58 3.32 151.05 151.05

ON PEAK 275696.77 2.76 150.31 150.31

ON PEAK 283141.94 2.83 130.71 130.71

ON PEAK 282335.48 2.82 95.42 95.42

ON PEAK 251654.84 2.52 68.02 68.02

ON PEAK 270812.90 2.71 44.75 44.75

ON PEAK 340112.90 3.40 31.12 31.12

ON PEAK 424180.65 4.24 23.01 23.01

OFF PEAK 481758.06 4.82 24.60 24.602324

2122

1920

1112

910

78

1718

1516

1314

Hour

56

3

4

1

2


AUGUST DAYS IN MONTH 31 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 371619.35 3.72 33.21 33.21

OFF PEAK 418787.10 4.19 29.86 29.86

OFF PEAK 443593.55 4.44 27.65 27.65

OFF PEAK 501309.68 5.01 25.73 25.73

OFF PEAK 513958.06 5.14 23.13 23.13

OFF PEAK 503235.48 5.03 20.32 20.32

OFF PEAK 506112.90 5.06 22.01 22.01

OFF PEAK 517770.97 5.18 33.74 33.74

OFF PEAK 385274.19 3.85 46.62 46.62

OFF PEAK 342270.97 3.42 60.62 60.62

MID PEAK 323793.55 3.24 88.39 88.39

MID PEAK 316280.65 3.16 129.65 129.65

MID PEAK 353867.74 3.54 152.27 152.27

ON PEAK 368464.52 3.68 172.22 172.22

ON PEAK 369451.61 3.69 185.27 185.27

ON PEAK 366264.52 3.66 190.31 190.31

ON PEAK 320838.71 3.21 190.71 190.71

ON PEAK 323251.61 3.23 166.60 166.60

ON PEAK 336293.55 3.36 117.15 117.15

ON PEAK 282522.58 2.83 78.94 78.94

ON PEAK 246370.97 2.46 57.05 57.05

ON PEAK 247477.42 2.47 45.06 45.06

ON PEAK 272351.61 2.72 38.63 38.63

OFF PEAK 307441.94 3.07 36.61 36.61

2122

1920

1718

2324

910

78

56

1516

1314

1112

3

4

1

2

Hour


SEPTEMBER DAYS IN MONTH 30 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 325223.33 3.25 65.28 65.28

OFF PEAK 330573.33 3.31 58.14 58.14

OFF PEAK 326970.00 3.27 54.33 54.33

OFF PEAK 346143.33 3.46 50.10 50.10

OFF PEAK 342723.33 3.43 45.97 45.97

OFF PEAK 335326.67 3.35 44.03 44.03

OFF PEAK 342183.33 3.42 46.11 46.11

OFF PEAK 381796.67 3.82 54.33 54.33

OFF PEAK 333133.33 3.33 82.93 82.93

OFF PEAK 367636.67 3.68 119.89 119.89

MID PEAK 377250.00 3.77 161.68 161.68

MID PEAK 385670.00 3.86 196.15 196.15

MID PEAK 436846.67 4.37 202.88 202.88

ON PEAK 445386.67 4.45 219.18 219.18

ON PEAK 442940.00 4.43 233.26 233.26

ON PEAK 435466.67 4.35 237.63 237.63

ON PEAK 387006.67 3.87 235.24 235.24

ON PEAK 395750.00 3.96 207.20 207.20

ON PEAK 423930.00 4.24 153.55 153.55

ON PEAK 370716.67 3.71 119.15 119.15

ON PEAK 327853.33 3.28 102.06 102.06

ON PEAK 308250.00 3.08 90.10 90.10

ON PEAK 305580.00 3.06 77.95 77.95

OFF PEAK 311790.32 3.12 68.49 68.49

1920

1718

1516

2324

2122

78

56

3

4

1314

1112

910

1

2

Hour


OCTOBER DAYS IN MONTH 31 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 545096.77 5.45 14.07 14.07

OFF PEAK 578606.45 5.79 13.20 13.20

OFF PEAK 589264.52 5.89 10.25 10.25

OFF PEAK 619825.81 6.20 8.71 8.71

OFF PEAK 653958.06 6.54 6.56 6.56

OFF PEAK 631074.19 6.31 3.15 3.15

OFF PEAK 662887.10 6.63 6.32 6.32

OFF PEAK 721493.55 7.21 12.74 12.74

OFF PEAK 615958.06 6.16 28.98 28.98

OFF PEAK 503980.65 5.04 39.85 39.85

MID PEAK 418003.23 4.18 57.87 57.87

MID PEAK 356235.48 3.56 80.70 80.70

MID PEAK 350890.32 3.51 96.41 96.41

ON PEAK 359541.94 3.60 118.41 118.41

ON PEAK 373174.19 3.73 128.65 128.65

ON PEAK 362454.84 3.62 126.33 126.33

ON PEAK 319793.55 3.20 118.28 118.28

ON PEAK 317193.55 3.17 88.67 88.67

ON PEAK 340064.52 3.40 53.37 53.37

ON PEAK 331151.61 3.31 34.51 34.51

ON PEAK 372919.35 3.73 24.46 24.46

ON PEAK 434938.71 4.35 17.79 17.79

ON PEAK 469332.26 4.69 14.52 14.52

OFF PEAK 508812.90 5.09 13.48 13.48

1718

1516

1314

2324

2122

1920

56

3

4

1

2

1112

910

78

Hour


NOVEMBER DAYS IN MONTH 30 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE



OFF PEAK 722446.67 7.22 0.00 0.00

OFF PEAK 755696.67 7.56 0.00 0.00

OFF PEAK 781700.00 7.82 1.11 1.11

OFF PEAK 817676.67 8.18 0.00 0.00

OFF PEAK 838706.67 8.39 0.00 0.00

OFF PEAK 805550.00 8.06 0.00 0.00

OFF PEAK 846063.33 8.46 0.00 0.00

OFF PEAK 911746.67 9.12 6.93 6.93

OFF PEAK 775626.67 7.76 15.74 15.74

OFF PEAK 718236.67 7.18 21.83 21.83

MID PEAK 638216.67 6.38 27.11 27.11

MID PEAK 538643.33 5.39 36.87 36.87

MID PEAK 480113.33 4.80 40.05 40.05

MID PEAK 442333.33 4.42 50.76 50.76

MID PEAK 435143.33 4.35 54.01 54.01

MID PEAK 447926.67 4.48 50.06 50.06

MID PEAK 576030.00 5.76 33.45 33.45

MID PEAK 619110.00 6.19 9.30 9.30

MID PEAK 595980.00 5.96 6.13 6.13

MID PEAK 587503.33 5.88 3.49 3.49

MID PEAK 588953.33 5.89 1.07 1.07

MID PEAK 599890.00 6.00 0.00 0.00

MID PEAK 629116.67 6.29 1.16 1.16

OFF PEAK 688960.00 6.89 1.13 1.132324

1516

1314

1112

2122

1920

1718

3

4

1

2

Hour

910

78

56


DECEMBER DAYS IN MONTH 31 HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE HOURLY AVERAGE


BTU/H Therms Clg (Tons) Ton-hrs

OFF PEAK 832032.26 8.32 1.44 1.44

OFF PEAK 864219.35 8.64 1.30 1.30

OFF PEAK 905009.68 9.05 1.29 1.29

OFF PEAK 930987.10 9.31 1.29 1.29

OFF PEAK 949887.10 9.50 0.00 0.00

OFF PEAK 908280.65 9.08 0.00 0.00

OFF PEAK 946493.55 9.46 0.00 0.00

OFF PEAK 1063735.48 10.64 5.24 5.24

OFF PEAK 921448.39 9.21 9.17 9.17

OFF PEAK 815716.13 8.16 19.59 19.59

MID PEAK 745232.26 7.45 28.10 28.10

MID PEAK 685870.97 6.86 21.54 21.54

MID PEAK 659503.23 6.60 23.19 23.19

MID PEAK 608680.65 6.09 33.87 33.87

MID PEAK 594148.39 5.94 31.55 31.55

MID PEAK 615077.42 6.15 26.21 26.21

MID PEAK 680422.58 6.80 12.12 12.12

MID PEAK 719096.77 7.19 2.69 2.69

MID PEAK 671883.87 6.72 1.34 1.34

MID PEAK 614545.16 6.15 1.25 1.25

MID PEAK 634177.42 6.34 1.35 1.35

MID PEAK 674154.84 6.74 1.35 1.35

MID PEAK 723096.77 7.23 1.48 1.48

OFF PEAK 778751.61 7.79 1.57 1.572324

2122

1314

1112

910

1920

1718

1516

1

2

Hour

78

56

3

4



Appendix 9

Formation Thermal Conductivity Test and Data Analysis

dave.troup

Sticky Note

San Mateo County Replacement Jail Thermal Conductivity Testing (TL-1) Redwood City, CA 94063

Page 2 of 11

Executive Summary A formation thermal conductivity test was performed at the San Mateo County Replacement Jail in Redwood City, CA. The vertical test bore was completed February 21, 2013 by Pitcher Drilling. Meline Engineering Corporation’s test unit was attached to the vertical bore at 9:02am on March 1, 2013. On March 3, 2013, at 9:52am the test unit was detached and data collection completed.

Meline Engineering Corporation analyzed the collected data using the “line source” method.

This report provides a general overview of the test and procedures that were used to perform the thermal conductivity test along with a plot of the data in real time and in a form used to calculate the formation thermal conductivity. The following average formation thermal conductivity was found from the data analysis.

Formation Thermal Conductivity = 0.94 Btu/hr-ft-°F Due to the necessity of a thermal diffusivity value in the design calculation process, an attempt was made to estimate the average thermal diffusivity for the encountered formation. Formation Thermal Diffusivity = 0.82/day An estimate of the undisturbed soil temperature value was determined from the initial temperature data at startup. Estimated Undisturbed Soil Temperature = 66.0°F


Page 3 of 11

Test Procedures

The American Society of Heating, Refrigeration, and Air-Conditioning Engineers (ASHRAE) recently adopted and published a set of recommended procedures for performing formation thermal conductivity tests for geothermal applications. Meline Engineering is committed to adhering to ASHRAE recommendations. Some of these recommended procedures are listed below:

(1) Required Test Duration — minimum test duration of 36 hours is recommended, with a preference toward 48 hours.

(2) Power Quality — The standard deviation of the power should be 1.5% of the average power, with maximum power variation of 10% of the average power. The heat flux rate should be 51 Btu/hr (15 W) to 85 Btu/hr (25 W) per foot of borehole depth to best simulate the expected peak loads on the u-bend.

(3) Undisturbed Soil Temperature Measurement — The undisturbed soil temperature should be determined by recording the minimum loop temperature as the water returns from the u-bend at test startup.

(4) Installation Procedures for Test Loops — The bore diameter is to be no larger than 6 inches, with 4.5 inches being the target diameter. To ensure against bridging and voids, the bore annulus is to be uniformly grouted from the bottom to the top using a tremie pipe.

(5) Time Between Loop Installation and Testing — A minimum delay of five days between loop installation and test startup is recommended if the formation is expected to have a low thermal conductivity or if low conductivity grouts (< 0.75 Btu/hrft°F) are used. A minimum delay of three days is recommended for all other conditions.

For a complete list of recommended procedures, refer to ASHRAE’s 2011 HVAC Applications handbook, page 34.13.


Page 4 of 11

Data Analysis

Meline Engineering, Inc. uses the “line source” method of data analysis. The line source equation used is not valid for early test times. Also, the line source method assumes an infinitely thin line source of heat in a continuous medium. If a u-bend grouted in a borehole is used to inject heat into the ground at a constant rate in order to determine the average formation thermal conductivity, the test must be run long enough to allow the finite dimensions of the u-bend pipes and the grout to become insignificant. Experience has shown that the amount of time required to allow early test time error and finite borehole dimension effects to become insignificant is approximately ten hours.

In order to analyze real data from a formation thermal conductivity test, the average temperature of the water entering and exiting the u-bend heat exchanger is plotted versus the natural log of time. Using the Method of Least Squares, the linear equation coefficients are then calculated that produce a line that fits the data. This procedure is normally repeated for various time intervals to ensure that variations in the power or other effects are not producing erroneous results.

Through the analysis process, the collected raw data is converted to spreadsheet format (Microsoft Excel®) for final analysis. A hard copy of the data can be obtained at any time. If desired, please contact Meline Engineering, Corp. and provide a ship-to address or e-mail address at one of the following:

Phone: (916) 366-3458 Fax: (916) 366-3958 E-mail: [email protected]


Page 5 of 11

Formation Thermal Conductivity Test Report

Date: March 1-3, 2013 Location: San Mateo County Replacement Jail Maple Street Redwood City, CA 94063

Borehole Data

Provided by Pitcher Drilling

Bore Hole Depth: 252' U-bend Size: 1" U-Bend Length: 250’ Grout Type: Wyo-ben 0.93 Grout Solids: (4:1 mix) Grouted Portion: 250’

Test Data Test Duration: 48 hrs. Average Power: 4,581 W Total Heat Input Rate: 15,634 BTU/hr Calculated Circulator Flow Rate: 9.0 GPM Undisturbed Soil Temperature: 66.0 deg F Borehole Diameter: 5''


Page 6 of 11

Drillers Log Summary Legal Description of the location of the test hole (TL-1): 70 Chemical Way Redwood City, CA San Mateo County APN Book: 052 Page: 392 Parcel: 200

Drillers Log: Ft. Fill 0-7 Bay Mud 7-14 Old Bay Clay 14-30 Brown and Grey Clay 30-140 Gravel Mix Clay 140-170 Grey Clay 170-188 Rock Shell Melange 188-242 Competent Rock (Sandstone) 242-252

A mud rotary drill rig was used at this location. The driller noted that very competent sandstone slowed drilling considerably below 242 feet. This information should be factored into the design of the ground heat exchanger.

.


Page 7 of 11

Figure 1: Temperature versus Time Data

Line Source Data Analysis

The temperature versus time data was analyzed using the line source analysis for the time period shown above. An average linear curve fit was applied to the data between 10 and 48 hours. The slope of the curve was found to be 5.315. The resulting thermal conductivity was found to be 0.94 BTU/hr-ft-°F.


Page 8 of 11

Figure 2: Temperature versus Natural Log of Time.


Page 9 of 11

Figure 3: Temperature versus Natural Log of Time from hour 10 to completion.


Page 10 of 11

Estimated Thermal Diffusivity

The reported drilling log for this test borehole indicated that the formation consisted of mostly clay and some gravel with competent sand stone below 222 feet. Saturated moisture contents were assumed for sand and clay in order to calculate heat capacity values. A heat capacity value for clay was calculated from specific heat and density values listed by Kavanaugh and Rafferty (Ground-Source Heat Pumps - Design of Geothermal Systems for Commercial and Institutional Buildings, ASHRAE, 1997). A weighted average of these values based on the indicated formation was used to develop an average heat capacity for the formation. An estimated diffusivity value was then found using the calculated formation thermal conductivity and the estimated heat capacity. The thermal diffusivity for this formation was estimated to be approximately 0.82 ft2/day.

Est. Average Heat Capacity

(Btu/ft3 °F)

Thermal Conductivity (Btu/hr-ft-°F)

Est. Thermal Diffusivity

(ft2/day)

27.3 0.94 0.82

Time Period Slope

Average Heat

(BTU/hr-ft)

at Input (W/ft)

Thermal Conductivity (BTU/hr-ft-°F)

48 hrs 5.315 62.5 18.3 0.94


Page 11 of 11

Frequently Asked Questions (FAQ’s) Regarding FTC Testing

Q: Thermally-enhanced grout is specified for the final loop field design. The test bore was grouted with a low conductivity, 20% solids, bentonite grout. How do I adjust the thermal conductivity value to account for this? A: While the conductivity of the grout is important for the loop field design, it is not important for determining formation thermal conductivity. We use the “line source” method to analyze data, which assumes an infinitely thin line rejecting heat at a constant rate into an infinite medium. The initial ten hours, which is influenced by the bore dimensions and grout conductivity, is ignored in the analysis. However, once the heat has penetrated into the formation, the temperature rise of the formation approaches steady-state. It is the slope of the temperature rise that is used in the analysis. Hence, no adjustment to the reported formation thermal conductivity is required.

Q: The software I use to design the loop field requires that I input a value for “soil conductivity”. Is this the same as formation thermal conductivity? A: Absolutely. Formation, soil, and ground are all used interchangeably to describe the conditions in which the u-bends will be installed. The use of the word “formation” simply implies that the installation conditions may be soil, rock, or some combination of the two.

Q: I’ve just received your report. I have a formation conductivity of 1.54 Btu/hrft°F. How do I translate that into a loop length requirement, in terms of bore depth (in feet) per ton? A: The formation thermal conductivity test provides values for three key parameters required for the ground loop design. These are the “Undisturbed Soil Temperature, Formation Thermal Conductivity, and Formation Thermal Diffusivity.” These parameters, along with many others, are inputs to commercially available loop design software (e.g. GchpCalc, available at GeoKiss.com/software). The software uses all of the inputs to determine the required loop length in bore depth per ton.

Q: Is the “Undisturbed Soil Temperature” value listed in the report the temperature that I enter into my loop design software where it calls for the “Deep-Earth Temperature”? A: Generally, yes. The “Undisturbed Soil Temperature” is the constant temperature of the formation. We attempt to determine this value by measuring the temperature of the water entering the test unit at the beginning of the test. However, the value we measure and report may be inaccurate if the test is initiated too quickly after the installation of the test bore.


Page 2 of 11

Executive Summary A formation thermal conductivity test was performed at the San Mateo County Replacement Jail in Redwood City, CA. The vertical test bore was completed February 22, 2013 by Pitcher Drilling. Meline Engineering Corporation’s test unit was attached to the vertical bore at 6:01am on February 27, 2013. On March 1, 2013, at 6:41pm the test unit was detached and data collection completed.

Meline Engineering Corporation analyzed the collected data using the “line source” method.

This report provides a general overview of the test and procedures that were used to perform the thermal conductivity test along with a plot of the data in real time and in a form used to calculate the formation thermal conductivity. The following average formation thermal conductivity was found from the data analysis.

Formation Thermal Conductivity = 1.15 Btu/hr-ft-°F Due to the necessity of a thermal diffusivity value in the design calculation process, an attempt was made to estimate the average thermal diffusivity for the encountered formation. Formation Thermal Diffusivity = 01.01/day An estimate of the undisturbed soil temperature value was determined from the initial temperature data at startup. Estimated Undisturbed Soil Temperature = 67.0°F


Page 3 of 11

Test Procedures

The American Society of Heating, Refrigeration, and Air-Conditioning Engineers (ASHRAE) recently adopted and published a set of recommended procedures for performing formation thermal conductivity tests for geothermal applications. Meline Engineering is committed to adhering to ASHRAE recommendations. Some of these recommended procedures are listed below:

(1) Required Test Duration — minimum test duration of 36 hours is recommended, with a preference toward 48 hours.

(2) Power Quality — The standard deviation of the power should be 1.5% of the average power, with maximum power variation of 10% of the average power. The heat flux rate should be 51 Btu/hr (15 W) to 85 Btu/hr (25 W) per foot of borehole depth to best simulate the expected peak loads on the u-bend.

(3) Undisturbed Soil Temperature Measurement — The undisturbed soil temperature should be determined by recording the minimum loop temperature as the water returns from the u-bend at test startup.

(4) Installation Procedures for Test Loops — The bore diameter is to be no larger than 6 inches, with 4.5 inches being the target diameter. To ensure against bridging and voids, the bore annulus is to be uniformly grouted from the bottom to the top using a tremie pipe.

(5) Time Between Loop Installation and Testing — A minimum delay of five days between loop installation and test startup is recommended if the formation is expected to have a low thermal conductivity or if low conductivity grouts (< 0.75 Btu/hrft°F) are used. A minimum delay of three days is recommended for all other conditions.

For a complete list of recommended procedures, refer to ASHRAE’s 2011 HVAC Applications handbook, page 34.13.


Page 4 of 11

Data Analysis

Meline Engineering, Inc. uses the “line source” method of data analysis. The line source equation used is not valid for early test times. Also, the line source method assumes an infinitely thin line source of heat in a continuous medium. If a u-bend grouted in a borehole is used to inject heat into the ground at a constant rate in order to determine the average formation thermal conductivity, the test must be run long enough to allow the finite dimensions of the u-bend pipes and the grout to become insignificant. Experience has shown that the amount of time required to allow early test time error and finite borehole dimension effects to become insignificant is approximately ten hours.

In order to analyze real data from a formation thermal conductivity test, the average temperature of the water entering and exiting the u-bend heat exchanger is plotted versus the natural log of time. Using the Method of Least Squares, the linear equation coefficients are then calculated that produce a line that fits the data. This procedure is normally repeated for various time intervals to ensure that variations in the power or other effects are not producing erroneous results.

Through the analysis process, the collected raw data is converted to spreadsheet format (Microsoft Excel®) for final analysis. A hard copy of this data can be obtained at any time. If desired, please contact Meline Engineering, Corp. and provide a ship-to address or e-mail address at one of the following:

Phone: (916) 366-3458 Fax: (916) 366-3958 E-mail: [email protected]


Page 5 of 11

Formation Thermal Conductivity Test Report

Date: February 27 – March 1, 2013 Location: San Mateo County Replacement Jail Maple Street Redwood City, CA 94063

Borehole Data

Provided by Pitcher Drilling

Bore Hole Depth: 252' U-bend Size: 1" U-Bend Length: 250’ Grout Type: Wyo-ben 0.93 Grout Solids: (4:1 mix) Grouted Portion: 250’

Test Data Test Duration: 50.1 hrs. Average Power: 5152 W Total Heat Input Rate: 17,584 BTU/hr Calculated Circulator Flow Rate: 8.2 GPM Undisturbed Soil Temperature: 67 deg F Borehole Diameter: 5''


Page 6 of 11

Drillers Log Summary Legal Description of the location of the test hole (TL-2): 70 Chemical Way Redwood City, CA San Mateo County APN Book: 052 Page: 392 Parcel: 200

Drillers Log: Ft. Fill 0-10 Bay Mud 10-20 Old Bay Clay 20-35 Brown and Grey Clay 30-160 Gravel Mix with Grey Clay 160-172 Grey Clay 172-192 Rock Shell Melange 192-222 Hard Sandstone 222-252

A mud rotary drill rig was used at this location. The driller noted that very competent sandstone slowed drilling considerably below 222 feet. This information should be factored into the design of the ground heat exchanger.


Page 7 of 11

Figure 1: Temperature versus Time Data

Line Source Data Analysis

The temperature versus time data was analyzed using the line source analysis for the time period shown above. An average linear curve fit was applied to the data between 10 and 60 hours. The slope of the curve was found to be 4.346. The resulting thermal conductivity was found to be 1.15 BTU/hr-ft-°F.


Page 8 of 11

Figure 2: Temperature versus Natural Log of Time.


Page 9 of 11

Figure 3: Temperature versus Natural Log of Time from hour 10 to completion.


Page 10 of 11

Estimated Thermal Diffusivity

The reported drilling log for this test borehole indicated that the formation consisted of mostly clay and some gravel with competent sand stone below 222 feet. Saturated moisture contents were assumed for sand and clay in order to calculate heat capacity values. A heat capacity value for clay was calculated from specific heat and density values listed by Kavanaugh and Rafferty (Ground-Source Heat Pumps - Design of Geothermal Systems for Commercial and Institutional Buildings, ASHRAE, 1997). A weighted average of these values based on the indicated formation was used to develop an average heat capacity for the formation. An estimated diffusivity value was then found using the calculated formation thermal conductivity and the estimated heat capacity. The thermal diffusivity for this formation was estimated to be approximately 1.01 ft2/day.

Est. Average Heat Capacity

(Btu/ft3 °F)

Thermal Conductivity (Btu/hr-ft-°F)

Est. Thermal Diffusivity (ft2/day)

27.3 1.15 1.01

Time Period Slope

Average Heat

(BTU/hr-ft)

at Input (W/ft)

Thermal Conductivity (BTU/hr-ft-°F)

60 hrs 4.346 62.8 18.4 1.15


Page 11 of 11

Frequently Asked Questions (FAQ’s) Regarding FTC Testing

Q: Thermally-enhanced grout is specified for the final loop field design. The test bore was grouted with a low conductivity, 20% solids, bentonite grout. How do I adjust the thermal conductivity value to account for this? A: While the conductivity of the grout is important for the loop field design, it is not important for determining formation thermal conductivity. We use the “line source” method to analyze data, which assumes an infinitely thin line rejecting heat at a constant rate into an infinite medium. The initial ten hours, which is influenced by the bore dimensions and grout conductivity, is ignored in the analysis. However, once the heat has penetrated into the formation, the temperature rise of the formation approaches steady-state. It is the slope of the temperature rise that is used in the analysis. Hence, no adjustment to the reported formation thermal conductivity is required.

Q: The software I use to design the loop field requires that I input a value for “soil conductivity”. Is this the same as formation thermal conductivity? A: Absolutely. Formation, soil, and ground are all used interchangeably to describe the conditions in which the u-bends will be installed. The use of the word “formation” simply implies that the installation conditions may be soil, rock, or some combination of the two.

Q: I’ve just received your report. I have a formation conductivity of 1.54 Btu/hrft°F. How do I translate that into a loop length requirement, in terms of bore depth (in feet) per ton? A: The formation thermal conductivity test provides values for three key parameters required for the ground loop design. These are the “Undisturbed Soil Temperature, Formation Thermal Conductivity, and Formation Thermal Diffusivity.” These parameters, along with many others, are inputs to commercially available loop design software (e.g. GchpCalc, available at GeoKiss.com/software). The software uses all of the inputs to determine the required loop length in bore depth per ton.

Q: Is the “Undisturbed Soil Temperature” value listed in the report the temperature that I enter into my loop design software where it calls for the “Deep-Earth Temperature”? A: Generally, yes. The “Undisturbed Soil Temperature” is the constant temperature of the formation. We attempt to determine this value by measuring the temperature of the water entering the test unit at the beginning of the test. However, the value we measure and report may be inaccurate if the test is initiated too quickly after the installation of the test bore.

SAN MATEO JAIL GEOTHERMAL FEASIBILITY...Geothermal Heat Pump systems have a number of potential...

Documents

Transcript of SAN MATEO JAIL GEOTHERMAL FEASIBILITY...Geothermal Heat Pump systems have a number of potential...