Tubman African American Museum · Project Info: - Atlanta, GA - 45,000 Sq. Ft.-Two stories - Museum Structural:-Steel construction with composite metal deck-Fabricated curved steel

Tubman African Tubman African American MuseumAmerican Museum

Atlanta, GeorgiaAtlanta, Georgia

Christopher ChampagneChristopher ChampagneMechanical EmphasisMechanical Emphasis

The Pennsylvania State UniversityThe Pennsylvania State UniversitySpring 2003Spring 2003

Tubman African American Museum

Project Team:Client: Tubman African American Museum (Macon, GA)

Architect: E. Verner Johnson and Associates, Inc. (Boston, MA)

M/E/P Engineer: Vanderweil Engineers (Boston, MA)

Structural Engineer: Souza, True and Partners, Inc. (Watertown, MA)

Civil Engineer: Cunningham & Company (Macon, GA)

Exhibit Designer: PRD(Fairfax, VA)

Christopher J. Champagne

Architectural Engineering – Mechanical Option

Project Info:- Atlanta, GA- 45,000 Sq. Ft.- Two stories- Museum

Structural:- Steel construction with composite metal deck- Fabricated curved steel around balcony- Cooper dome with gabled truss design using moment connections

Construction:Started: October 2001Planned Completion: Spring 2004Construction Cost: 15.5 million

Mechanical:- (2) 121.5 ton HCFC-22 air-cooled water chillers- (2) 25,000 CFM constant volume and (1) 18,000 CFM variable air volume custom air-handling units- Temperature, humidity and CO2sensors - Duct electric humidifier serving galleries and collection storage areas. - (2) 1040 MBH Gas fired boilers - Air conditioning unit with air cooled condenser serving vault room.

Lighting:- Surface mounted single circuit & recessed metal hallide downlights in gallery and display areas- Incandescent mono-point head cross baffle flush ceiling mounted canopy luminaries around balcony area- Bare lamp fluorescent strip with asymmetric reflectors and custom fascia

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Christopher Champagne Architectural Engineering Mechanical Emphasis

Table of Contents- I Executive Summary 1 II Existing Conditions Project Team 2 Building Function / Primary Use 2 Location and Site 2 Architecture 3 Construction Schedule 3 Cost Information 3 Electrical 3 Lighting 4 Structural 4 III Existing Mechanical System Design Objectives and Requirements 5 Mechanical System Summary 6 Energy Sources and Rates 7 Description of System of Operation for AHUs 7 Hot Water System 10 Chilled Water System 10 IV Reasons for Investigation 11 V Proposed Mechanical System - Optimization of Chillers Executive Summary 12 Calculation Technique 12 Source of Equations 12 Calculation Scenarios 14 Life Cycle Cost Analysis 16 Chiller Controls 17 Piping Size 17 Conclusions 18 VI Proposed Mechanical System - Chilled Water Pumping Executive Summary 19 Advantages of Variable Speed Pumps 19



Possibility of Switch 20 Should the Switch Be Made? 21 Current Piping Arrangement 22 New Piping Arrangement 22 Cost Savings - Piping and Valves 22 Cost Savings - Pump Electrical Demand 23

HAP Results 23

Bell & Gossett ESP-Plus Online Program 24 Engineering Equation Solver (EES) 24 Life Cycle Cost Analysis 28 Payback Time 29 Conclusion 29 VII Lighting Executive Summary 30 Design Criteria 30 Hardware Selection 32 Placement of Luminaries 32 Lightscape Renderings 35 Photometric Data 37 Conclusion 39 VIII Electrical Executive Summary 40 Current Wiring to Chiller 40 New Chiller Electrical Load 40 New Wiring Calculation 41 Conclusion 42 IX Conclusions 43 X References 44 XI Acknowledgements 47



XII Appendices 48 Appendix A - Electric Utility Rates Appendix B - Hourly Analysis Program Results Appendix C - Chiller Performance Sheets Appendix D - Chiller EES Equations - Sample Parametric Table Appendix E - Current Chilled Water Schematic

- Current Pump Cutsheet and System Graph

Appendix F - Proposed Chilled Water Schematic - Proposed Pump System Graph

Appendix G - Bell and Gossett ESP Plus Online Program

Appendix H - EES Pump Formatted Equations Appendix I - Luminaire Product Data Appendix J - Electrical Riser Diagram Appendix K - Electrical Data for Chiller Appendix L - NEC Table 430.150 and 430-52


Christopher Champagne Page 1 Architectural Engineering Mechanical Emphasis

Executive Summary-

HVAC systems typically utilize a large portion of a building’s energy load.

Therefore it is important that the system be as energy efficient as possible with the

limitation of first cost. Saving energy translates directly into saving money. The existing

mechanical system for the Tubman African American Museum, a two story, 45,000 ft2

building located in Atlanta, Georgia was investigated and alternatives are presented to

improve the design. Design objectives, factors that affected the design and the actual

mechanical system as designed by the engineer were analyzed and reviewed. Two

changes are researched. They are changing the chiller size and staging strategy of the

two chillers so they work at optimum efficiency. Also, the modification of the pumps

from constant speed to variable speed was examined. Issues of coordination and

integration of other architectural engineering areas are analyzed. The lighting system of

one of the gallery spaces was redesigned. The electrical system changes that occur as a

result of the mechanical changes are summarized.



Existing Conditions-

The following is a summary of the general condition of the Tubman Museum.

Project Team Members-

Client: Tubman African American Museum Macon, GA Architect: E. Verner Johnson and Associates, Inc. Boston, MA CM/GG: Harmon-Piedmont Construction, LLC Atlanta, GA M/E/P Engineer: Vanderweil Engineers Boston, MA Structural Engineer: Souza, True and Partners, Inc.

Watertown, MA Civil Engineer: Cunningham & Company Macon, GA Exhibit Designer: PRD Fairfax, VA

Building Function / Primary Use- The building is a museum educating patrons about African American art, history

and culture. The majority of the space is galleries, exhibit displays and storage areas for

the artifacts. The first floor has a cafe and kitchen along with offices and meeting spaces.

A receiving area along the west side of the building stores, stages and conditions the

artwork. The second floor consists of more gallery spaces and a studio.



Location and Site- The building is located in Atlanta, Georgia. It is positioned on a one-block by

one-block parcel of land surrounded by Broadway Lane, Cherry Street, Fifth Street and

Cherry Street Lane.

Architecture- The exterior of the building is brick with ceramic tiles located at the entrances of

the building. The lobby in the center of the building stretches from the first floor up

through the second floor, which has an overhanging balcony, up to a dome located on the

roof of the building. This dome is the focal point of the architectural design as can be

seen below.

Construction Schedule- Construction: Started: October 2001 Planned Completion: Spring 2004 Cost Information- Construction Cost: $15.5 million Electrical- The building has a secondary service through Georgia Power, who supplies the

transformer. There are two distribution panel boards, one that is 480/277V 3Φ, 4 W and

a ground and the other is 208/120V 3 Φ, 4 W and a ground. There are eight dry type

transformers with the following kVAs: 9, 15, 30, 45, 75, 112 ½, 150 and 225.



Lighting- Surface mounted single circuit & recessed metal halide downlights are placed in

gallery and display areas. Incandescent mono-point head, cross baffle are flush ceiling

mounted around balcony area. Bare lamp, fluorescent strip with asymmetric reflectors

and custom fascia are located around the exterior of the building. There are five lighting

control cabinets that provide relay control of the lights.

Structural- The building is steel construction with a composite metal deck. The deck is

fabricated from type ASTM A653, Grade 33 steel and is galvanized. The structural steel

conforms to ASTM 572, Grade 50. Fabricated curved steel is located around balcony.

The cooper dome on the roof is a gabled truss design using moment connections.



Existing Mechanical System-

Design Objectives and Requirements-

A museum has special temperature and humidity concerns compared with other

buildings. As a result, ASHRAE Applications suggests that the building should contain

as much thermal and humidity controls as is economically possible. Proper environment

is an important for two reasons: reduction in the deterioration rate of the pieces of

artwork and comfort provided to the occupants who are visiting and working there.

ASHRAE Applications 1999 (Chapter 20 – Museums, Libraries, and Archives)

lists five factors that an engineer should consider when designing such spaces:

1. The relationship between building shape, orientation, and environmental

control.

2. The amount of fenestration. When the fenestration is a high percentage of the

exterior envelope surface area the exterior load can be a significant part of the

total air-conditioning load. Also, natural light may be detrimental to the

building contents.

3. Noise control, both inside and outside.

4. Quality and quantity of indoor and outdoor air. Select appropriate filters to

support the needs of the structure and consider the effects that off-gassing

might have on the contents.

5. Minimizing the building’s influence on the environment, including the

reduction of pollution into the atmosphere.

Table 2 of the chapter lists the specification range for temperature and humidity

based on type of artifact displayed, set points of temperature and relative humidity and

the maximum fluctuations and gradients in the controlled space. Although not clearly

stated in any of the design documents, it would seem most feasible that the museum



would be Control Class A (See ASHRAE Applications 1999 Chapter 20 – Table 2). The

control sheet of the design documents (H4.1) states for the building system control the

system allows a ± 5% relative humidity. Class A is the optimal design for most museums

and galleries, providing only a “small risk of mechanical damage to the high vulnerability

artifacts with no risk to most artifacts, paintings, photographs and books.” With Atlanta

having mild winters, Control Class AA would be possible, but seems to be unlikely due

to budget concerns.

A museum can be split into separate zones with different design targets, so each

specific collections can individually addressed. Gallery Spine 142, Temporary Exhibits

143, 144, & 145 on the first floor and African Collection 233, Gallery Spines 251 & 252 ,

and Collection Galleries 253, 254, 255, 256, 257, & 258 are all separated from the rest of

the building. All perimeter walls for return air plenum are required to continue to the

deck or structure above. Sealant or non-flammable spray-in foam is applied to prevent

any air leakage into wall cavities, between floors or to the exterior construction. There

are air-tight barriers required to be between the ceiling and the deck above. All

penetrations of walls for ductwork and piping going through such spaces must have

sealed penetrations.

Mechanical System Summary-

The following is a summary of the highlights of the mechanical system:

• (2) 121.5 ton HCFC-22 air-cooled water chillers

• (2) 25,000 CFM constant volume and (1) 18,000 CFM variable

volume custom air handling unit.

• Temperature, humidity and CO2 sensors

• Duct electric humidifier serving galleries and collection storage areas.

• (2) 1040 MBH Gas fired boilers

• Air conditioning unit with air cooled condenser located on roof serving

vault room.



Energy Sources and Rates-

Since the museum has not been built yet and the utility selection has not been

made, the following information would be a typical case for a museum located in Atlanta.

The natural gas would be provided by Georgia Natural Gas and the electricity would be

provided by Georgia Power (a subsidiary of Southern Company). The natural gas, which

is used by the boilers, costs a rate of $4.90 / month with a charge of $0.609 per therm

with an $8.50 penalty per DDDC. DDDC is Designated Design Day Capacity, which is a

measure of the pipeline capacity for gas needed to serve the business on peak demand

days, typically the coldest day of the year.

The electric bill would be as follows:

Base Charge (includes first 25 kWh or less $14.00 All consumption (kWh) not greater than 200 hours times the billing demand. First 3,000 kWh 8.757¢ per kWh Next 7,000 kWh 8.026¢ per kWh Next 190,000 kWh 6.910¢ per kWh

$6.42 per kW in excess of 30 kW accounts for the billing demand. Georgia

Power bases billing demand on the “highest 30-minute kW measurement during the

current month and the proceeding eleven (11) months”

All of the following utility cost calculations use the above rates. See Appendix A

for more details.

Description of System of Operation for Air Handling Units-

The following is a sequence of operation of the air side and water side of the

HVAC system. Sequences of operations outlined shall be performed by Direct Digital



Control Field Panels (DDCFPS) which determine occupied and unoccupied mode

operation.

AHU-1A & 1B:

These air handling units are constant volume and serve the gallery spaces.

Therefore, the system is always running (occupied mode) since the artifacts always need

to have a very controlled environment.

Occupied Mode-

The fan runs continuously throughout the cycle after the supply and return

dampers are closed. The discharge air temperature is set at 50.5˚F leaving the cooling

coil. In order to maintain this temperature, the control valve modulates the chilled water

running through the cooling coil. The variable frequency drives (VFD) on the supply

fans shall modulate in order to maintain the necessary duct static pressure which the

constant volume terminal boxes need to function properly.

CO2 Demand Controlled Ventilation-

The minimum outdoor air damper is open for all hours of operation, which is set

at 2,000 CFM for the base ventilation rate. The maximum outdoor air set point is 15,000

CFM. CO2 demand controls the secondary outdoor air damper. The return air and

outdoor air dampers are modulated as required to satisfy all the CO2 space sensor

requirements. The maximum CO2 set point is 900 PPM. The DDC system monitors the

outdoor air CO2 to ensure permissible levels.

AHU-2:

This air handling unit is variable volume and serves the offices and meeting

spaces.

Occupied Mode-



The unit runs continuously under static pressure control. It has an economizer

cycle for free cooling. When the outdoor air temperature is below 55˚F, the secondary

outdoor air damper opens and the return air damper closes while maintaining the same

discharge air temperature. When the outdoor air temperature is above 55˚F, the

secondary outdoor air damper closes and the return air damper will fully open since there

is no economizing possibility. The cooling coil valve will modulate open.

When cooling is required the following steps will be taken:

1) Utilize outdoor air for cooling.

2) When the return air damper is closed, if the cooling coil leaving air

temperature raises 3˚F above the set point for 60 seconds, the control

valve for the cooling coil opens allowing chilled water flow.

3) When the outside air temperature rises above the economizer set point,

the secondary outside air damper will close 100% and

Unoccupied Mode-

The outdoor and exhaust dampers close and the supply and return fans cycle as

required keeping the space at 85˚F during the summer and 65˚F during the winter.

CO2 Demand Controlled Ventilation-

The minimum outdoor air damper is open for all hours of operation, which is set

at 1,000 CFM for the base ventilation rate. The maximum outdoor air set point is 4,000

CFM. CO2 demand controls the secondary outdoor air damper. The return air and

outdoor air dampers are modulated as required to satisfy all the CO2 space sensor

requirements. The maximum CO2 set point is 900 PPM. The DDC system monitors the

outdoor air CO2 to ensure permissible levels.



Hot Water System-

The hot water boiler plant runs continuously year round. The base hot water

supply temperature is 140˚F and maximum is 160˚F.

Hot Water Pumps-

The first pump is turned on by the automatic temperature control (ATC). The

second pump starts if, when the first pump is operating, the hot water return temperature

drops 25˚F below the hot water supply set point for 10 minutes. The second pump turns

off when the hot water return temperature is 10˚F below the hot water supply temperature

set point for 10 minutes.

Chilled Water System-

The ATC in unison with the DDC controls all aspect of cycling the chillers.

When cooling is called for, the control valve at the chiller opens and the associated

chilled water pump turns on. When flow through the piping is proven by evaporator

differential pressure, the chiller starts and runs. The chiller shall operate to maintain 45˚F

chilled water supply temperature. The lead/lag chiller shall be switched by the building

management system. Both chillers and associated pumps shall be programmed in a lead-

lag scenario.



Reason for Investigation- Several different options were investigated in order to make the Tubman Museum

more energy efficient. The first alternative investigated was resizing the chillers so there

is a smaller chiller for off-hours cooling and a larger one for occupied mode. This would

make sense since the museum will have low load profiles during the evenings when only

the exhibit spaces or anywhere artwork is stored needed to be cooled. After several

simulations, it was determined that the chiller could only be sized slightly smaller.

Therefore the staging of the chillers were investigated to see if an energy savings could

be realized.

Also switching from constant speed pumping to variable speed pumping was

explored. There are many advantages to such system. They are: improved efficiency

(motor and pump) and consequently energy savings; reduced system noise; improved

control of system flow to respond to flow and pressure requirements of the system;

extended motor life due to soft stops & starts which puts less wear and tear on the parts of

the pump; control valve in the bypass ensures that neither of the chillers would become

“starved” during a low load situation, as flow is diverted directly from the supply back to

the chillers.

These options were chosen due to their potential energy savings and feasibility.



Optimization of Chillers- Executive Summary-

This section shows the technique and results from optimizing the design size and

staging arrangement of the chillers based on several different scenarios.

Calculation Technique- Engineering Equation Solver (EES) was used to simulate two air-cooled chillers

operating in parallel of equal size. The original chiller were Trane Air-Cooled Series R

Rotary Liquid Chillers Model RTAA 125 (Design Capacity = 120.1 ton). The other two

chiller types were the Trane RTAA 110 (Design Capacity = 108.5 ton) and the Trane

RTAA 100 (Design Capacity = 100.6 ton). (See Appendix B for manufacturer’s

information) The maximum cooling load is 189.1 ton on July 15th at 2 pm according to

the EES model using Atlanta Bin Data and Hourly Analysis Program (HAP) data. (See

Appendix C for HAP results) The RTAA 100 provides very little safety factor in design,

but was investigated. Also the upper capacity that one chiller would run before the

second chiller was run was varied from 85% to 100% of capacity to see which is the most

efficient. The lower capacity at which the second chiller would turn off was set to 40%.

The EES formatted equations for the simulations can be found in Appendix D along with

a sample portion of the parametric table.

Source of Equations-

The optimization equations used in the EES simulation are from the California

Energy Commission’s 2001 Non-Residential Alternative Calculation Methods (ACMs)

document, specifically Chapter 2 entitled “Reference Method and Required Modeling

Capabilities for Alternative Calculation Methods (ACMs).”

The following three terms are functions of chilled water supply temperature

(Tchws) and the outdoor dry-bulb temperature (Toa). They are used to establish the

efficiency of the chiller operation. For air-cooled equipment, the outdoor dry-bulb



temperature (Toa) replaces the condenser water supply temperature (Tcws) in the

equations. Tcws is used for water-cooled equipment.

• CAP_FT is the full load capacity as a fraction of rated capacity. It is a capacity

correction that is a function of those terms.

• EIR_FT is the full load efficiency (kW/ton) as fraction of rated capacity. It is an

efficiency correction factor.

• EIR_FPLR is the fraction of full load power as a function of fraction of full load

output.

The coefficients (a1, b1, c1, etc.) of the three previous terms are found in Tables 2-

10, 2-12 and 2-14 of the California Energy Commission’s document.

The following three terms are also used to evaluate chiller efficiency.

• Coefficient of Performance (COP) is the kW of refrigeration effect divided by the

kW input.

• Energy Efficiency Ration (EER) is the Btu/h of refrigeration effect divided by the

watt input.

• Part Load Ratio (PLR) is the number of tons the chiller is currently operating

divided by the design tonnage.

Equations for the chiller operating curve were obtained using linear regression

function (with 3-degree polynomials) from EES:

Chiller Curve for RTAA 125 EIR_FPLR = 3.64872200E-02 + 7.34742980E-01 * (PLR) + 2.19947480E-01 * (PLR2) + 7.73310932E-17 * (PLR3) Chiller Curve for RTAA 110 EIR_FPLR = 3.64872200E-02 + 7.34742980E-01 * (PLR) + 2.19947480E-01 * (PLR2) - 1.32814766E-18 * (PLR3) Chiller Curve for RTAA 100 EIR_FPLR = 3.64872200E-02 + 7.34742980E-01 * (PLR) + 2.19947480E-01 * (PLR2) +

4.86332437E-17*PLR^3}



Calculation Scenarios-

The hourly weather data for specific days and times from HAP for Atlanta was

entered into the EES program along with the load from the two air systems (constant

volume and variable volume). Each year has 8760 runs (24 hours a day multiplied by

365 days a year). The chilled water temperature was set to 45˚F.

The following is a summary of the setup of the twelve different scenarios chosen

for the EES simulation.

Case Model Ton kW Lower Upper

(RTAA-

#) Cap. (%)

Cap. (%)

A 125 120.1 120.1 40 90 B 110 108.5 108.5 40 90 C 100 100.6 113.6 40 90 D 125 120.1 120.1 40 85 E 110 108.5 108.5 40 85 F 100 100.6 113.6 40 85 G 125 120.1 120.1 40 95 H 110 108.5 108.5 40 95 I 100 100.6 113.6 40 95 J 125 120.1 120.1 40 100 K 110 108.5 108.5 40 100 L 100 100.6 113.6 40 100

Since all of the monthly utility rates fall below 200,000 kWh, the monthly electric

cost formula is:

Cost = (Total kWh – (3,000 kWh + 7,000 kWh)) * ($0.06910/kWh) + (3000

kWh) * ($0.08757/kWh) + (7,000 kWh) * ($0.08026/kWh) + $14 + (200

kW)*($6.42/kW)



Case AEC Operating

Cost Operating

Time Cost Operating

Time (kWh) ($) (hrs) Rankings Rankings

A 1,033,188 88,572 13,618 6 4 B 1,043,601 89,291 14,339 9 8 C 1,038,866 88,964 15,014 8 11 D 1,096,997 92,981 14,034 10 6 E 1,108,762 93,794 14,762 12 9 F 1,104,441 93,495 15,350 11 12 G 977,400 84,717 13,136 4 2 H 985,828 85,299 13,966 5 5 I 1,038,866 88,964 14,907 7 10 J 927,718 81,284 12,670 1 1 K 934,654 81,763 13,583 3 3 L 929,304 81,393 14,121 2 7

(Note: AEC = Annual Energy Consumption

Cost rankings = 1 is lowest cost, 12 is highest cost

Operating time = 1 is smallest amount of time, 12 is largest amount of time)

75,000

80,000

85,000

90,000

95,000

Cos

t ($)

1

Annual Energy Cost

A B C D E F G H I J K L



0

5,000

10,000

15,000

20,000

Hour

s

1

Annual Operating Hours

A B C D E F G H I J K L

Cases J, K and L have the three best operating energy, which is for staging to occur when the first chiller reaches 100% of capacity. Annual operating hours shows the amount of wear placed on the chillers. Life Cycle Cost (LCC) Analysis- The following formula from CoolTools was used in the calculation of the LCC.

( ) ( )( )∑=

+÷++=N

j

jjj dMCUCFCLCC

11

Where: FC = first cost of plant UCj = plant utility cost for year j MCj = relative maintenance cost for year j d = discount rate N = number of years of analysis

Case Model Ton First Cost (FC) (RTAA-#) ($)

A 125 120.1 96,000B 110 108.5 84,000C 100 100.6 75,000

(Note: First cost information obtained from mechanical contractor familiar with purchasing similar units.)

For this calculation, MCj = $500 d = 12 %



N = 20

$706,880.98

$698,458.84

$686,695.15

500,

000.

00

550,

000.

00

600,

000.

00

650,

000.

00

700,

000.

00

750,

000.

00

Cost ($)

RTAA 125

RTAA 110

RTAA 100

Tran

e M

odel

Nu

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LCC of Different Size Chillers

Selecting the RTAA 110 saves $8,422.14 and the RTAA 100 saves $20,185.83 compared to the RTAA 125 over the life of the system. Chiller Controls- Trane has several control features that benefit the system according to the

specifications (RLC-PRC016-EN). The Unit Control Module (UCM) “maximizes both

the compressor and motor life by equalizing both the number of starts and the operating

hours.” The Trane Chiller Plant Manager Building Management System provides duty

cycle and demand limiting among other features. This allows for the upper capacity limit

on one chiller (UCap in the EES program) that is proposed to be practical.

Piping Size-

Although the chillers are different tonnage, the pipe size should stay the same.

Using the Trane recommended formula of GPM = (Tons * 24)/(∆T) the chillers have

required flow rates of 288 gpm, 260 gpm and 240 gpm for the RTAA Models 125, 110

and 100 respectively. The flow rates from the EES simulation never rise above these



points. Following design guidelines from previous experience, 5” Schedule 40 Steel for

chilled water systems can support 240-440 gpm.

Conclusions- The RTAA 100 has the smallest life cycle cost based on the assumptions stated

above. However given its tonnage being only slightly above the design cooling load, this

might not be a wise selection. The RTAA 110 would still provide cost savings over the

RTAA 125, along with some added safety to the designer. The staging should be set to

100% of capacity of the first chiller before the second chiller is turned on.



Chilled Water System Pumping- Executive Summary-

One method of saving energy used by a building is changing the primary pumps

of a primary-only, chilled water system from constant speed to variable speed. An

important question is what is the overall economic benefit? In this section, after proving

the chilled water system meets the requirements for being switched from constant speed

to variable speed pumps, an investigation is performed to determine the cost savings

associated with the change.

The advantages of variable speed pumps-

The following is a list of some of the benefits of using variable speed pumps

instead of constant speed:

- Improved efficiency (motor and pump) and consequently energy savings.

- Reduced system noise.

- Improved control of system flow to respond to flow and pressure requirements

of the system.

- Extended motor life due to soft stops & starts which puts less wear and tear on

the parts of the pump. The maintenance cost is also reduced along with time

spent working on the pump.

The Trane Engineers Newsletter mentions the following additional benefits

(Trane, 1999):

- Lower installation cost. No balancing valves, pressure-relief valves and

special piping for bypass lines are required. There is an elimination of the

need for separate distribution pumps. By not having those pumps, the

material and installation labor costs of the chilled water system are lower

along with the electrical service for the pump’s VFDs.



- The control valve in the bypass ensures that neither of the chillers would

become “starved” during a low load situation, as flow is diverted directly from

the supply back to the chillers.

Is it possible to switch from constant speed to variable speed pumping in this case?-

Several authors writing on the subject mentioned the importance of not just

adding a variable speed pumps to every existing system without first looking at the

current system. Hegberg writes “Consideration should be include total load flow (gpm)

vs. existing flow gpm capacity; load frequency of expected percent capacity vs. percent

of time; distribution of gpm capacity to the mains, risers, zones and terminals; and actual

as-balanced flows from a recent balancing reports.” (Hegberg, 1991)

Trane mentions four situations where variable primary flow should not be used

(Trane, 1999). They are for system where:

1. System chilled-water temperature is critical. Examples are a “clean-room” or

computer chip making plants.

- Although there are specific temperature and humidity guidelines for a museum,

they are not critical. Slight temporary fluctuations will not cause permanent

damage to the artifacts.

2. The system flow rate, and consequently the load, does not vary.

- The load does vary in the Tubman Museum, between the occupied hours and the

unoccupied hours. Also, due to the large transient load of occupants, the location

of the load varies frequently within the inside of the building during the occupied

hours.

3. It is unlikely that the owner/operator will run the plant as designed.

- This is a slight area of concern that will be discussed later, but something that

doesn’t eliminate the use of variable speed pumps for the system.

4. Existing chiller controls are old and inaccurate.

- This is a new construction project, so this also is not a concern.



Should the switch be made?-

After determining whether it is possible to switch from constant to variable speed

pumps, the next step in the design process is to decide if the change should be made. The

largest factor in this decision is the electricity rates and potential savings. The greater the

numbers of hours the pumps are running, the higher the energy cost savings.

Two of the air handling units are constant volume and serve the gallery spaces.

Therefore, the system is constantly running since the artifacts continuously need to have a

very controlled environment. The other unit air handling unit is variable volume and

serves the offices and meeting spaces. If the load goes to half for example and it is all on

one air handling unit (such would be the case at night when the offices and other spaces

were empty), with the current system the water separates into both branches of the supply

piping, but goes straight through the bypass for the air handling unit that doesn’t need

chilled water. The other air handling unit is potentially starved when this situation arises.

There is some concern with installing this system. Steven Taylor of Taylor

Engineering had this response in the Trane article. “Because of their lower first costs and

lower energy costs, variable-primary-flow systems are clearly the right choice for many

applications, but not all. They require complex staging control sequences and minimum

flow (bypass) controls, so the designer and operator of the system have to be more

sophisticated if the system is to be a success. On some projects, the ‘fail-safe’ nature of

primary-secondary system may offset their energy and first costs disadvantages.” (Trane,

1999) Without familiarity of the facility staff, based on the size of the building and the

budget concerns, there may be concern with the ability of the owner to deal with the

complexities that Taylor mentions. However, given the right guidelines though O & M

manuals from the engineer and manufacturers, the owner’s workers would be able to

monitor and maintain the system to ensure proper function.



Current Piping Arrangement-

Appendix E shows a diagram for the current system.

New Piping Arrangement-

Appendix F shows a diagram for the proposed new system. Dashed-line circles

are shown in areas where changes have occurred from the current system.

Cost Savings – Piping and Valves-

The three-way valves are replaced with two-way valves at the air handling units

with two-way valves costing less than three-way valves. There is also less piping that

needs to be around the load. According to the specifications, steel schedule 40 piping is

used, which costs $97 per linear foot for 6” piping (R.S. Means, 2002). Examining the

construction drawings, it is realistic to say that 100 feet of piping is saved, meaning a

savings of $9,700. The omitted fittings and welds also increase the cost savings. A

control valve in the bypass has to be added in the bypass line, which would typically cost

$1950 (Means Mechanical, 2002) lowering the savings slightly. Also three variable

frequency drives must be purchased each costing $5,800 (Means Mechanical, 2002).

These three requirements equate to an additional cost of $9,650.

According to Bahnfleth, measuring the “evaporator chilled water flow is critically

important in this type of system because of minimum and maximum flow-rate

limitations.” (Bahnfleth, 2001) He suggests using a flow meter instead of a differential

pressure loss sensor around the evaporator. There is currently a combination flow

meter/shutoff/balancing valve (circuit setter) shown on the plans. There is no

manufacturer listed or any accuracy measurements given for it. This information would

have to be checked before deciding whether the flow meter would have to be replaced in

the new system.



Care must be taken to adding unnecessary parts. When Rishel was asked about

the single most common problem in variable-speed pumping applications he responded

with the following. “The most significant problem in variable-speed pump applications

is the lack of understanding on how to apply them to hot- and chilled-water systems. Too

often balancing valves, reducing valves, and mechanical devices used for constant-speed

pumps are applied wrongly to variable volume, variable-speed HVAC systems.” (Rishel,

1999) Variable flow pumps should never have balancing valves on the discharge,

because the pumps can take can of the varying speed alone.

Cost Savings – Pump Electrical Demand-

There are several different techniques available for calculating the energy savings

of variable speed pumps. Carrier’s Hourly Analysis Program (HAP), Bell & Gossett

ESP-Plus Online Program and Engineering Equation Solver (EES) were used to

determine the kWh saved switching to variable speed pumps and compare the results.

HAP Results- Previously the museum was modeled using HAP. In order to see the amount of

energy saved switching to variable speed pumps, two cases were simulated with the only

change being the pump distribution type from constant speed to variable speed.

Constant Speed Case: Variable Speed Case: Primary Energy Primary Energy CHW Cost CHW Cost Pumps Pumps Month (kWh) ($) Month (kWh) ($) January 930 81.44 January 421 36.87 February 860 75.31 February 383 33.54 March 1,036 90.72 March 440 38.53 April 1,223 107.10 April 502 43.96 May 1,499 131.27 May 665 58.23 June 1,710 149.74 June 854 74.78



July 1,859 162.79 July 1,079 94.49 August 1,843 161.39 August 1,010 88.45 September 1,680 147.12 September 845 74.00 October 1,203 105.35 October 491 43.00 November 1,025 89.76 November 437 38.27 December 961 84.15 December 425 37.22

Total 15,829 1,386.15 Total 7,551 661.33

The energy cost savings would be $1,386.15 - $661.33 = $724.82 per year.

Bell & Gossett ESP-Plus Online Program-

Since Bell & Gossett is the manufacturer of the original pumps, an investigation

of their online program was executed to compare results. Although able to produce

results much quicker than HAP, there were some serious drawbacks to ESP-Plus

Program. The major issue was deciding on a load profile for the building. A museum

was not an option for the load profile, so the closest match was chosen,

“School/University, cooling.” The kWh needed was larger than the value calculated by

HAP, but it showed potential cost savings. Bell & Gossett Series 1510 Model 2-1/2 BB

pumps as specified on the construction drawings could be retrofitted to be a variable

speed pumps.

For the constant speed and variable speed examples, see Appendix G. The energy

cost savings using this method is $3,063.67 per year.

Engineering Equations Solver (EES)-

Another method of simulating the pumps was using EES. (See Appendix H for

formatted equations) Using data from manufacturer’s pump curves and ASHRAE

Systems and Equipment 2000, relationships between the following terms were created

using lookup tables:

• Flow Rate vs. Head



• Flow Rate vs. Pump Efficiency

• Percent of Nameplate Load vs. Motor Efficiency

• Percent of Design Speed vs. Drive Efficiency (for the variable speed pumps only)

Individual functions were created for total power, pump efficiency, pump model

curve, percent of nameplate load for both the variable and constant speed pumps.

Functions were also created that decided how many pumps would run based on the load

and at what speed would the variable speed pumps operate at. Total efficiency of the

pump is the product of drive, motor and pump efficiencies. Total power was calculated

using a function containing the terms flow rate, head, and total efficiency. The number of

hours the pumps would run at was calculated using the Qflow value from the chiller EES

model discussed earlier and the COUNTIF function of Microsoft Excel. Ranges of flow

rate were established to determine the number of hours the pumps would run, which is

summarized in the following chart and table. Also the cost savings per year was

calculated by multiplying the power savings by hours by the utility cost previously stated.

Flow Power Flow Time Ran Electric Cost

Rate Savings Range at GPM Savings Savings (GPM) (kW) (GPM) (hours) (kWh) ($/year)

0.1 0.04506 0-10 0 0.00 0.00 20 1.021 11-30 0 0.00 0.00 40 1.438 31-50 0 0.00 0.00 60 1.677 51-70 0 0.00 0.00 80 1.845 71-90 24 44.28 3.88

100 1.91 91-110 49 93.59 8.20 120 1.925 111-130 78 150.15 13.15 140 1.886 131-150 124 233.86 20.48 160 1.78 151-170 200 356.00 31.17 180 1.582 171-190 600 949.20 83.12 200 1.243 191-210 1031 1,281.53 112.22 220 0.6637 211-230 984 653.08 57.19 240 -0.4575 231-250 730 -333.98 -29.25 260 1.815 251-270 712 1,292.28 113.16 280 1.848 271-290 738 1,363.82 119.43 300 3.917 291-310 754 2,953.42 258.63 320 3.912 311-330 697 2,726.66 238.77 340 3.902 331-350 758 2,957.72 259.01



360 3.886 351-370 784 3,046.62 266.79 380 3.866 371-390 337 1,302.84 114.09 400 3.844 391-410 70 269.08 23.56 420 3.818 411-430 43 164.17 14.38 440 3.79 431-450 28 106.12 9.29 460 3.759 451-470 15 56.39 4.94 480 3.726 471-490 4 14.90 1.31 500 3.69 491-510 0 0.00 0.00 520 3.65 511-530 0 0.00 0.00 540 3.606 531-550 0 0.00 0.00 560 3.556 551-570 0 0.00 0.00 580 3.499 570-580 0 0.00 0.00

8760 19,681.75 1,723.53

0

200

400

600

800

1000

1200

Hour

s

0-19

60-79

120-1

39

180-1

99

240-2

59

300-3

19

360-3

79

420-4

39

480-4

99

540-5

59

Flow Rate Ranges (gpm)

Hours vs. Flow Rate Ranges



-500.000.00

500.001,000.001,500.002,000.002,500.003,000.003,500.00

Cost

($)

0-19

60-79

120-1

39

180-1

99

240-2

59

300-3

19

360-3

79

420-4

39

480-4

99

540-5

59

Flow Rate Ranges (gpm)

Cost Savings vs. Flow Rate Ranges

Flow Time Ran CS VS

CS Energy

VS Energy

CS Yearly

VS Yearly

Rate at GPM Power Power Yearly Use

Yearly Use

Op. Cost

Yearly Use

(GPM) (hours) (kW) (kW) (kWh) (kWh) ($) (kWh) 0.1 0 0.1305 0.08541 0 0 0.00 0.0020 0 1.722 0.7012 0 0 0.00 0.0040 0 2.23 0.7919 0 0 0.00 0.0060 0 2.539 0.8616 0 0 0.00 0.0080 24 2.777 0.9326 66.648 22.3824 5.84 1.96

100 49 2.984 1.073 146.216 52.577 12.80 4.60120 78 3.173 1.248 247.494 97.344 21.67 8.52140 124 3.354 1.468 415.896 182.032 36.42 15.94160 200 3.531 1.751 706.2 350.2 61.84 30.67180 600 3.706 2.124 2223.6 1274.4 194.72 111.60200 1031 3.882 2.639 4002.342 2720.809 350.49 238.26220 984 4.062 3.398 3997.008 3343.632 350.02 292.80240 730 4.246 4.704 3099.58 3433.92 271.43 300.71260 712 4.439 2.624 3160.568 1868.288 276.77 163.61280 738 4.641 2.793 3425.058 2061.234 299.93 180.50300 754 6.886 2.968 5192.044 2237.872 454.67 195.97320 697 7.062 3.149 4922.214 2194.853 431.04 192.20340 758 7.237 3.336 5485.646 2528.688 480.38 221.44360 784 7.412 3.526 5811.008 2764.384 508.87 242.08380 337 7.588 3.722 2557.156 1254.314 223.93 109.84400 70 7.765 3.921 543.55 274.47 47.60 24.04420 43 7.943 4.125 341.549 177.375 29.91 15.53



440 28 8.124 4.334 227.472 121.352 19.92 10.63460 15 8.307 4.547 124.605 68.205 10.91 5.97480 4 8.493 4.767 33.972 19.068 2.97 1.67500 0 8.683 4.993 0 0 0.00 0.00520 0 8.877 5.227 0 0 0.00 0.00540 0 9.077 5.471 0 0 0.00 0.00560 0 9.283 5.727 0 0 0.00 0.00580 0 9.496 5.997 0 0 0.00 0.00

8760 46,730 27,047 4,092 2,369 Life Cycle Cost Analysis-

The following formula from CoolTools was used in the calculation of the LCC.

( ) ( )( )∑=

+÷++=N

j

jjj dMCUCFCLCC

11

Where:

FC = first cost of equipment

UCj = utility cost for year j

MCj = relative maintenance cost for year j

d = discount rate

N = number of years of analysis

In this example,

FCconstant = $0

FCvariable = $9,650

MCj = $500

d = 12%

N = 20 years

UCj constant speed = $4,092

UCj variable speed = $2,369



$34,299.69

$31,079.83

25,0

00.0

0

26,0

00.0

0

27,0

00.0

0

28,0

00.0

0

29,0

00.0

0

30,0

00.0

0

31,0

00.0

0

32,0

00.0

0

33,0

00.0

0

34,0

00.0

0

35,0

00.0

0

Cost ($)

Constant Speed

Variable Speed

LCC of Pumps

Payback Time- Initial Additional Cost for Variable Speed Pumps = $9,650 Yearly Savings = $1,723.53 Payback Period = ($9,650 / $1,723.53) = 5.6 years Conclusion-

Based solely on cost, it makes sense to switch from constant speed pumps to

variable-speed pumps. The LLC is $3,219.85 less for variable speed. Variable speed

control also has some advantages that are not quantifiable in economic terms. “Looking

into the future, the variable-speed pump will become the standard for most HVAC water

systems. Its ability to save water system energy will make its use mandatory in areas

where electrical energy is not abundant. The variable-speed pump with digital control

will simplify these water systems to where they will consist mostly of heating and

cooling coils and piping with few valves other than manual shut-off valves. Total digital

control of water systems is now a reality.” (Rishel, 1995) The payback period is slightly

lengthy, but realistic.



Lighting- Executive Summary-

The lighting system for a gallery space in the museum (Collection Gallery 255)

was designed using industry guidelines. Design criteria were used in selecting the

lighting fixtures that best illuminated the exhibits that are displayed in the gallery.

Lightscape was used to summarize the results in a graphical nature.

Design Criteria-

The following guidelines are from The IESNA Lighting Handbook – Ninth

Edition (2000). The three most relevant locations/tasks for the gallery space were

selected.

Interior Location / Task Importance Design Issues Flat Display on vertical surface Very Important Color Appearance (And Color Contrast) Daylighting Integration and Control

Light Distribution on Task Place (Uniformity)

Reflected Glare Shadows Source/Task/Eye Geometry Important Appearance of Space and Luminaries Direct Glare Light Distribution on Surfaces Luminances of Room Surfaces Point(s) of Interest Surface Characteristics System Control and Flexibility

Somewhat Important Flicker (and Strobe)

Not Important Modeling of Faces or Objects Sparkle/Desirable Reflected Highlights



3-Dimensional Objects Very Important Color Appearance (And Color Contrast) Daylighting Integration and Control Direct Glare Light Distribution on Surfaces


Modeling of Faces or Objects Reflected Glare Shadows Source/Task/Eye Geometry Important Appearance of Space and Luminaries Luminances of Room Surfaces Point(s) of Interest Surface Characteristics System Control and Flexibility

Somewhat Important Flicker (and Strobe)

Sparkle/Desirable Reflected Highlights Not Important Lobbies, general gallery areas Very Important Appearance of Space and Luminaries Daylighting Integration and Control Point(s) of Interest Important Modeling of Faces or Objects Surface Characteristics

Somewhat Important Color Appearance (And Color Contrast)

Direct Glare Flicker (and Strobe) Light Distribution on Surfaces


Luminances of Room Surfaces Source/Task/Eye Geometry System Control and Flexibility Not Important Reflected Glare Shadows Sparkle/Desirable Reflected Highlights



Hardware Selection-

Two types of fixtures were needed to illuminate the gallery. A spotlight was

needed for the artwork along the walls, which is flat display on vertical surface. The

ERCO Standard Spotlight (Product number 77900.000 black) was selected. It provided a

uniform distribution pattern based on the literature and is used for accent lighting (See

Appendix I). For the ambient lighting and the 3-dimensional displays in the center of the

room, the same fixture can be used, the ERCO Gimbal Directional Luminaire (See

Appendix I). They are “specifically for highlighting artifacts whether in exhibitions,

glass cabinets or free-standing” according to the company’s website.

Placement of Luminaries-

The placement of the lamps must also be carefully selected. The spotlights were

located in front of the piece of artwork they were illuminated. There is a track that forms

a rectangle around the gypsum portion of the ceiling. This allows for the spotlights to be

moved along the track if the displays are changed. The distance between the wall and the

track (X) was calculated using the following figure (Fig. 14-6 from the IESNA Lighting

Handbook)



X = (Ceiling height – eye level) * 0.577

= (15’-0” – 5’6”) * 0.577

= (180” – 66”) * 0.577

= 66”

= 5’-6”

This distance ensured the 30˚ angle that is important in the prevention of shadows,

good Source/Task/Eye geometry and uniformity of light distribution on the painting.

The Gimbal fixtures were located directly above the current location of the

models. Figure 14-7 from IESNA Lighting Handbook shows a typical arrangement of

the fixture.

It should be noted that the beam direction can be angled in any direction up to 40°

from the perpendicular to directly downward, which gives the exhibit designers the

flexibility to move the 3-dimensional artifacts. The light also produced enough

illumination for the general gallery areas around the artifacts.



The following table is a summary of the location of the lamps in the space, the

angle at which they were aimed. All coordinates are in inches and are based from a 0, 0,

0 point (x, y, z) at the southwest corner of the room at the intersection of the floor and

walls.

Spotlights Absolute

Light # X Y Z X angle Y angle Z Angle cd 1 85 234 180 30 0 0 3,499.5 2 360 234 180 30 0 0 3,499.5 3 460 234 180 30 0 0 3,499.5 4 506 60 180 0 -30 0 3,499.5 5 57 195 180 0 -30 0 3,499.5 6 57 100 180 0 -30 0 3,499.5 7 110 56 180 -30 0 0 3,499.5 8 225 56 180 -30 0 0 3,499.5 9 334 56 180 -30 0 0 3,499.5 10 447 56 180 -30 0 0 3,499.5

Downlights Absolute

Light # X Y Z X angle Y angle Z Angle cd 1 135 112 180 0 0 0 1,700.3 2 275 112 180 0 0 0 1,700.3 3 414 112 180 0 0 0 1,700.3



Lightscape Renderings- The following are a sampling of the renderings of the gallery space.

(Southeast corner of room from above)

(South of the room from above)



(Northeast corner of the room from above)

(Close-up of northwest corner of the room)



Photometric Data-

The illuminance of the gallery space was also determined using Lightscape.

According to the IESNA Lighting Handbook target illuminance for the flat displays and

3-dimensional objects is 300 lx (30 fc) and for lobbies, general gallery areas and

corridors is 100 lx (10 fc). The following figures show the light analysis.

(South of the room from above)



(East of room from above)

(North of room from above)



Conclusion- The new lighting design is compliant with the lighting requirements stated in the IESNA Lighting Handbook.



Electrical- Executive Summary- The investigation of the impact on the electrical system of changing the chiller

size was performed using standard sizing equations and guidelines and values from the

National Electric Code. The size of the branch circuit from the bus bar to the two chillers

is investigated.

Current Wiring to Chiller- The current electrical riser diagram can be found in Appendix J. The two chillers

are supplied with 480/277 V 3Φ, 4 W. Feeder #18, which serves the chillers, consists of

4 – 250 kcmil and 1 #4 Ground contained in a 3” raceway. The nominal ampere rating of

the wire is 250. There is a fused disconnect switch, which is weather proof, located

before the point of connection to the chillers. The feeder is connected to the bus bar

which is connected to Distribution Panel 41 (DP-41) which has a AIIC of 35,000.

New Chiller Electrical Load- For the purposes of this exercise, all three chiller sizes were investigated. The

electrical loads for the three chiller sizes are found in Appendix K. Note 2 of Tables P-4,

P-5 and P-6 states that the “kW input is for compressors only.” The input for the ten fans

must also be included in the load of the chiller. The total kW values are converted in

horsepower in the table below.

Compressor Fan Total Total Chiller Size kW kW kW hp RTAA 125 136.3 10 146.3 196 RTAA 110 123.7 10 133.7 180 RTAA 100 113.6 10 123.6 166



New Wiring Calculation- The rated current of the motor must be determined using Table 430.150 from the

NEC code. This value must be used in order except for overload protection. Using the

next biggest hp value and the values found under the “460 Volts” heading. The full-load

current is determined.

Chiller Size Full Load Current (A) RTAA 125 240 RTAA 110 216 RTAA 100 200

From Section 430.22 – Single Motor of the NEC code (Appendix L) the minimum

ampacity is found multiplying the full load current by 125%.

Chiller Size Minimum Ampacity (A) RTAA 125 240 RTAA 110 216 RTAA 100 200

From the design document specifications, the electrical wiring should be copper,

with a temperature rating of 90˚C and either THWN-THHW or XHHW insulation. Using

Table 310.16 (Appendix L) the following sizes of wire are determined, which are slightly

smaller than the design values of 250 kcmil.

Chiller Size Conductor Size (AWG) RTAA 125 4/0 RTAA 110 4/0 RTAA 100 3/0

The following cost data for different wire sizes is from R.S. Means Construction

Cost Data page 455. (Note CLF = one hundred linear feet)

Wire Size Mat. Cost ($/CLF) Labor Cost ($) 250 kcmil 224 142 4/0 188 129 3/0 150 113



The distance between the chillers, located on the second floor, and the electrical

bus bar is 30’. There are two sets of wiring, each going from the bus bar to the respective

chiller. Therefore the cost savings would be:

Material Labor Total Two Sets of Wires Wire Size Savings ($) Savings ($) ($) ($) 250 kcmil - - - - 4/0 12.60 4.55 17.15 34.30 3/0 25.90 10.15 36.05 72.10

Conclusion- Based on the very small cost savings it would seem unlikely that the change would be made to smaller wire for the chillers.



Conclusions-

The RTAA 100 has the smallest life cycle cost based on the assumptions stated

above. However given its tonnage being only slightly above the design cooling load, this

might not be a wise selection. The RTAA 110 would still provide cost savings over

the RTAA 125, along with some added safety to the designer and should be selected.

The staging should be set to 100% of capacity of the first chiller before the second

chiller is turned on.

Based solely on cost, it makes sense to switch from constant speed pumps to

variable-speed pumps. The LLC is $3,219.85 less for variable speed. Variable speed

control also has some advantages that are not quantifiable in economic terms. “Looking

into the future, the variable-speed pump will become the standard for most HVAC water

systems. Its ability to save water system energy will make its use mandatory in areas

where electrical energy is not abundant. The variable-speed pump with digital control

will simplify these water systems to where they will consist mostly of heating and

cooling coils and piping with few valves other than manual shut-off valves. Total digital

control of water systems is now a reality.” (Rishel, 1995) The payback period is slightly

lengthy, but realistic. Therefore, the constant speed pumps should be switched to

variable speed pumps.

The new lighting design is compliant with the lighting requirements stated in

the IESNA Lighting Handbook.

Based on the very small cost savings it would seem unlikely that the change

would be made to smaller wire for the chillers.



References-

ASHRAE Application 1999. Chapter 20 - Museum, Libraries and Archives

ASHRAE Systems and Equipment 2000.

Bernier, M., B. Bourret. 1999. Pumping Energy and Variable Frequency Drives.

ASHRAE Journal December 1999: 37-40.

Bahnfleth, W., E. Peyer. 2001. Comparative Analysis of Variable and Constant Primary-

Flow Chilled-Water-Plant Performance. HPAC Engineering April 2001:41-50.

California Energy Commission – Energy Efficiency Committee Proposed AB 970 - 2001

Non-Residential Alternative Calculation Methods (ACMs) – “Chapter 2 – Reference

Method and Required Modeling Capabilities for Alternative”

Coad, W. 1998. A Fundamental Prospective on Chilled Water Systems. HPAC

Heating/Piping/AirConditioning August 1998: 59-66.

Gill, N. 1997. Adjustable Speed Pumps: Your Control Valve Alternative?

Hartman, T. 1996. Library and Museum HVAC: New Technologies/New Opportunities

- Part 1. HPAC Heating/Piping/AirConditioning April 1996: 57-60.

Hartman, T. 1996. Library and Museum HVAC: New Technologies/New Opportunities -

Part 2. HPAC Heating/Piping/AirConditioning May 1996: 63, 64, 67, 68, 72, & 103.



Hegberg, R. 1991. Converting Constant-Speed Hydronic Pumping System to Variable-

Speed Pumping. ASHRAE Transactions Pt.1 1991 ASHRAE Winter Meetings –

Technical Papers: 739-745.

Hughes, S. David, Electrical Systems in Buildings, 1988.

The IESNA Lighting Handbook – Reference & Application, 2000, Chapter 14 - Lighting

Pacific Gas and Electric Company. 2000. CoolTools Chilled Water Plant Design and

Specification Guide.

Martino, F. 2002. Elusive Energy Savings: Centrifugal Pumps and Variable Speed

Drives. www.powerqualityanddrives.com/pumpvfd.html.

National Electric Code (NEC) 2002

Pacific Gas and Electric Company. 2000. CoolTools Chilled Water Plant Design and

Specification Guide.

Rishel, J. 1995. The History of HVAC Variable-Speed Pumping. ASHRAE Transactions

No. 1, 1995 ASHRAE Winter Meetings – Proceedings: 1260-1263.

R.S. Means Building Construction Cost Data 2001.

R.S. Means Electrical Cost Data 2002.

R.S. Means Mechanical Cost Data 2002.



Schwedler, M., B.Bradley. 1998. An Idea for Chilled-Water Plant Whose Time Has

Come… Variable-Primary-Flow Systems. Trane Engineers Newsletter Volume 28, No.

3.



Acknowledgements-

I would like to thank the following people who have made my thesis possible:

The Pennsylvania State University Department of Architectural

Engineering faculty including:

o My advisor, Dr. James Freihaut

o Dr. William Bahnfleth and Dr. Stanley Mumma

o Jonathan Dougherty, Moses Ling and M. Kevin Parfitt

Vanderweil Engineers, especially Heather Tsatsarones and Ron Edwards

Fellow architectural engineering students who have lent their knowledge

and expertise

Mom, Dad and Jen who are always there for me

My friends who have been understanding and helpful



Appendices-



Appendix A - Electric Utility Rates

ELECTRIC SERVICE TARIFF:

POWER AND LIGHT MEDIUMSCHEDULE: “PLM-3”

PAGE EFFECTIVE DATE REVISION PAGE NO.1 of 2 With Bills Rendered for the Billing Month of March, 2002 Original 3.12

AVAILABILITY:

Throughout the Company's service area from existing lines of adequate capacity.

APPLICABILITY:To all electric service of one standard voltage required on the customer's premises, delivered at one point andmetered at or compensated to that voltage for any customer with a demand, as determined under the SpecialApplicability Provisions, of not less than 30 kW but less than 500 kW.

TYPE OF SERVICE:Single or three phase, 60 hertz, at a standard voltage.

MONTHLY RATE - Energy Charge Including Demand Charge:Base Charge........................................................................................................ $14.00All consumption (kWh) not greater than200 hours times the billing demand:

First 3,000 kWh .................................................................@............................. 8.757¢ per kWhNext 7,000 kWh .................................................................@............................. 8.026¢ per kWhNext 190,000 kWh .............................................................@............................. 6.910¢ per kWhOver 200,000 kWh.............................................................@............................. 5.355¢ per kWh

All consumption (kWh) in excess of 200hours and not greater than 400 hourstimes the billing demand ......................................................@............................. 0.892¢ per kWhAll consumption (kWh) in excess of 400hours and not greater than 600 hourstimes the billing demand ......................................................@............................. 0.672¢ per kWhAll consumption (kWh) in excess of 600hours times the billing demand ...........................................@............................. 0.586¢ per kWhMinimum Monthly Bill:A. $14.00 Base Charge plus $6.42 per kW of billing demand in excess of 30 kW plus excess kVARcharges and Fuel Cost Recovery as applied to the current month kWh.B. Metered Outdoor Lighting: The lessor of (1) that determined from paragraph "A" above, or (2) $31.91per meter plus Fuel Cost Recovery for metered outdoor lighting installations, provided service islimited to the lighting equipment itself and such incidental load as may be required to operatecoincidentally with the lighting equipment.

DETERMINATION OF REACTIVE DEMAND:Where there is an indication of a power factor of less than 95% lagging, the Company may at its option, installmetering equipment to measure Reactive Demand. The Reactive Demand shall be the highest 30-minutekVAR measured during the month. The Excess Reactive Demand shall be kVAR which is in excess ofone-third of the measured actual kW in the current month. The Company will bill excess kVAR at the rate of$0.27 per excess kVAR.

FUEL COST RECOVERY:The amount calculated at the above rate will be increased under the provisions of the Company's effective FuelCost Recovery Schedule, including any applicable adjustments.

SCHEDULE: “PLM-3”

PAGE EFFECTIVE DATE REVISION PAGE NO.2 of 2 With Bills Rendered for the Billing Month of March, 2002 Original 3.12

DETERMINATION OF BILLING DEMAND:The Billing Demand shall be based on the highest 30-minute kW measurement during the current month andthe preceding eleven (11) months.For the billing months of June through September, the Billing Demand shall be the greatest of:

(1) The current actual demand, or,(2) Ninety-Five percent (95%) of the highest actual demand occurring in any previous applicable summer

month (June through September), or,(3) Sixty percent (60%) of the highest actual demand occurring in any previous applicable winter month

(October through May).For the billing months of October through May, the Billing Demand shall be the greater of:

(1) Ninety-Five percent (95%) of the highest summer month (June through September), or,(2) Sixty percent (60%) of the highest winter month (October through May), including the current month.

In no case shall the Billing Demand be less than the greatest of:(1) The contract minimum, or,(2) Fifty percent (50%) of the total contract capacity, or,(3) 30 kW.

SPECIAL APPLICABILITY PROVISIONS:Limitation of ServiceService will be provided hereunder for those customers having a calculated demand of not less than 30 kW butless that 500 kW where that calculation is the greater of:

(1) Applying Sixty percent (60%) to the current or previous 11 months winter or off-peak demands, or,(2) Applying Ninety-Five percent (95%) to the current or previous 11 months summer or on-peak demands.

For customers on the Off-Peak (OP) and Variable Off-Peak (VOP) riders the calculation shall be based on thepercentages as stated in the riders.Construction ServiceConstruction power shall be considered as a part of permanent service and will be provided in accordance withthe Applicability section of this schedule. The Company will obtain a payment in advance for each meteringpoint to be served in the amount currently on file with the Georgia Public Service Commission.

TERM OF CONTRACT:One year.

GENERAL TERMS & CONDITIONS:

The bill calculated under this tariff is subject to change in such an amount as may approved and/or amendedby the Georgia Public Service Commission under the provisions of applicable riders.

Service hereunder subject to Rules and Regulations for Electric Service on file with the Georgia Public ServiceCommission.



Appendix B - Hourly Analysis Program Results

Air System Sizing Summary for CV AHUProject Name: Tubman Museum 04/22/2003 Prepared by: psuae 03:49PM

Air System Information Air System Name CV AHU Equipment Class CW AHU Air System Type CAV/RH

Number of zones 1Floor Area 25410.0 ft²

Sizing Calculation Information Zone and Space Sizing Method: Zone CFM Sum of space airflow rates Space CFM Individual peak space loads

Calculation Months Jan to DecSizing Data Calculated

Central Cooling Coil Sizing Data Total coil load 128.0 Tons Total coil load 1536.4 MBH Sensible coil load 1113.4 MBH Coil CFM at Jul 1500 40050 CFM Max block CFM 40050 CFM Sum of peak zone CFM 40050 CFM Sensible heat ratio 0.725 ft²/Ton 198.5 BTU/(hr-ft²) 60.5 Water flow @ 10.0 °F rise 307.47 gpm

Load occurs at Jul 1500OA DB / WB 93.0 / 75.0 °FEntering DB / WB 74.2 / 61.2 °FLeaving DB / WB 47.5 / 46.4 °FCoil ADP 44.5 °FBypass Factor 0.100Resulting RH 47 %Design supply temp. 50.5 °FZone T-stat Check 1 of 1 OKMax zone temperature deviation 0.0 °F

Central Heating Coil Sizing Data No central heating coil loads occurred during this calculation.

Humidifier Sizing Data Max steam flow at Des Htg 188.94 lb/hr Airflow Rate 40050 CFM

Air mass flow 173597.80 lb/hrMoisture gain .00109 lb/lb

Supply Fan Sizing Data Actual max CFM 40050 CFM Standard CFM 38577 CFM Actual max CFM/ft² 1.58 CFM/ft²

Fan motor BHP 49.59 BHPFan motor kW 36.98 kWFan static 4.25 in wg

Outdoor Ventilation Air Data Design airflow CFM 7378 CFM CFM/ft² 0.29 CFM/ft²

CFM/person 20.00 CFM/person

Hourly Analysis Program v.4.1 Page 1 of 1

Zone Sizing Summary for CV AHUProject Name: Tubman Museum 04/22/2003 Prepared by: psuae 03:49PM

Sizing Calculation Information Zone and Space Sizing Method: Zone CFM Sum of space airflow rates Space CFM Individual peak space loads


Zone Sizing Data

Maximum Design Minimum Time Maximum Zone Cooling Air Air of Heating Floor Sensible Flow Flow Peak Load Area ZoneZone Name (MBH) (CFM) (CFM) Load (MBH) (ft²) CFM/ft²CV Zone 799.4 40050 40050 Aug 2300 78.3 25410.0 1.58

Zone Terminal Sizing Data

Reheat Zone Zone Reheat Coil Htg Htg Mixing Coil Water Coil Water Box Fan Load gpm Load gpm AirflowZone Name (MBH) @ 20.0 °F (MBH) @ 20.0 °F (CFM)CV Zone 890.8 89.13 0.0 0.00 0

Space Loads and Airflows

Cooling Time Air Heating Floor Zone Name / Sensible of Flow Load Area Space Space Name Mult. (MBH) Load (CFM) (MBH) (ft²) CFM/ft²CV Zone 254 Collection Gallery 1 44.0 Jul 0200 2168 2.4 1040.0 2.08 255 Collection Gallery 1 51.3 Sep 0000 2527 7.7 1140.0 2.22 256 Collection Gallery 1 34.2 Oct 2300 1686 2.4 800.0 2.11 257 Collection Gallery 1 48.5 Oct 2300 2393 2.6 1150.0 2.08 258 Collection Gallery 1 43.2 Oct 2300 2131 2.3 1025.0 2.08 201 Balcony 1 21.7 Jan 2300 1069 0.0 2135.0 0.50 241 Mural Gallery 1 56.7 Oct 2300 2796 7.1 1275.0 2.19 243 Storage 1 1.0 Jan 2300 47 0.0 80.0 0.59 233 African Collection 1 99.3 Aug 2300 4896 10.7 2250.0 2.18 231 Gallery Spine 1 9.9 Jan 2300 490 0.0 350.0 1.40 218 3-D Collect. Storage 1 8.3 Jan 2300 408 0.0 440.0 0.93 219 2-D Collect. Storage 1 15.6 Jan 2300 769 0.0 830.0 0.93 212 Office 1 3.7 Jun 1800 181 1.5 130.0 1.39 213 Office 1 3.7 Jun 1800 181 1.5 130.0 1.39 214 Office 1 3.7 Jun 1800 181 1.5 130.0 1.39 220 Workroom 1 11.7 Jul 2200 576 1.3 340.0 1.69 211 Curatorial 1 18.8 Jun 1700 927 8.9 225.0 4.12 215 Corridor 1 0.4 Jan 2300 20 0.0 155.0 0.13 203 Corridor 1 0.3 Jan 2300 15 0.0 115.0 0.13 164 Fabrication 1 36.8 Jun 1800 1815 6.3 1000.0 1.82 165 Crates 1 16.1 Jun 1800 795 3.6 545.0 1.46 168 Electric Room 1 11.0 Jan 2300 540 0.0 150.0 3.60 172 Receiving 1 10.4 Oct 1400 512 2.2 400.0 1.28 175 Building Manager 1 5.5 Jul 1700 273 1.5 185.0 1.48 171 Registrar/Staging 1 8.2 Jan 2300 402 0.0 400.0 1.01 161 Corridor 1 0.5 Jan 2300 25 0.0 200.0 0.13 157 Staff Lounge 1 4.3 Jan 2300 211 0.0 175.0 1.20 142 Gallery Spine 1 22.7 Jan 2300 1120 0.0 800.0 1.40 101 Lobby 1 62.0 Jan 2300 3057 0.0 4150.0 0.74 143 Temporary Exhibits 1 46.5 Aug 0200 2294 7.4 1025.0 2.24 144 Temporary Exhibits 1 43.1 Oct 2300 2127 2.4 1020.0 2.08 145 Temporary Exhibits 1 69.4 Oct 2300 3419 5.0 1620.0 2.11


Air System Design Load Summary for CV AHUProject Name: Tubman Museum 04/22/2003 Prepared by: psuae 03:49PM

DESIGN COOLING DESIGN HEATING COOLING DATA AT Jul 1500 HEATING DATA AT DES HTG COOLING OA DB / WB 93.0 °F / 75.0 °F HEATING OA DB / WB 18.0 °F / 14.8 °F Sensible Latent Sensible LatentZONE LOADS Details (BTU/hr) (BTU/hr) Details (BTU/hr) (BTU/hr)Window & Skylight Solar Loads 457 ft² 11585 - 457 ft² - -Wall Transmission 11863 ft² 25146 - 11863 ft² 64339 -Roof Transmission 0 ft² 0 - 0 ft² 0 -Window Transmission 457 ft² 5097 - 457 ft² 13318 -Skylight Transmission 0 ft² 0 - 0 ft² 0 -Door Loads 28 ft² 725 - 28 ft² 677 -Floor Transmission 0 ft² 0 - 0 ft² 0 -Partitions 0 ft² 0 - 0 ft² 0 -Ceiling 0 ft² 0 - 0 ft² 0 -Overhead Lighting 107684 W 367409 - 0 0 -Task Lighting 0 W 0 - 0 0 -Electric Equipment 86275 W 294369 - 0 0 -People 369 91129 79375 0 0 0Infiltration - 0 0 - 0 0Miscellaneous - 0 0 - 0 0Safety Factor 0% / 0% 0 0 0% 0 0>> Total Zone Loads - 795460 79375 - 78334 0Zone Conditioning - 795405 79375 - 73297 0Plenum Wall Load 0% 0 - 0 0 -Plenum Roof Load 0% 0 - 0 0 -Plenum Lighting Load 0% 0 - 0 0 -Return Fan Load 40050 CFM 0 - 40050 CFM 0 -Ventilation Load 7378 CFM 176917 258900 7378 CFM 379035 199293Supply Fan Load 40050 CFM 126181 - 40050 CFM -126181 -Space Fan Coil Fans - 0 - - 0 -Duct Heat Gain / Loss 0% 0 - 0% 0 ->> Total System Loads - 1098503 338275 - 326150 199293Central Cooling Coil - 1113440 422982 - -450594 0Central Heating Coil - 0 - - 0 -Humidification Load - - -84707 - - 199293Terminal Reheat Coils - -14937 - - 776744 ->> Total Conditioning - 1098503 338275 - 326150 199293Key: Positive values are clg loads Positive values are htg loads Negative values are htg loads Negative values are clg loads


Air System Sizing Summary for VAV AHUProject Name: Tubman Museum 04/22/2003 Prepared by: psuae 03:49PM

Air System Information Air System Name VAV AHU Equipment Class CW AHU Air System Type 1FDDVAV

Number of zones 1Floor Area 9165.0 ft²

Sizing Calculation Information Zone and Space Sizing Method: Zone CFM Peak zone sensible load Space CFM Individual peak space loads


Central Cooling Coil Sizing Data Total coil load 41.8 Tons Total coil load 502.0 MBH Sensible coil load 401.9 MBH Coil CFM at Jul 1500 16608 CFM Max block CFM at Jun 1700 19265 CFM Sum of peak zone CFM 19265 CFM Sensible heat ratio 0.801 ft²/Ton 219.1 BTU/(hr-ft²) 54.8 Water flow @ 10.0 °F rise 100.47 gpm

Load occurs at Jul 1500OA DB / WB 93.0 / 75.0 °FEntering DB / WB 78.8 / 64.7 °FLeaving DB / WB 55.5 / 54.2 °FCoil ADP 52.9 °FBypass Factor 0.100Resulting RH 53 %Design supply temp. 55.0 °FZone T-stat Check 1 of 1 OKMax zone temperature deviation 0.0 °F

Central Heating Coil Sizing Data Max coil load 80.2 MBH Coil CFM at Des Htg 1897 CFM Max coil CFM 1897 CFM Water flow @ 20.0 °F drop 8.02 gpm

Load occurs at Des HtgBTU/(hr-ft²) 8.7Ent. DB / Lvg DB 69.4 / 110.0 °F

Supply Fan Sizing Data Actual max CFM at Jun 1700 19265 CFM Standard CFM 18556 CFM Actual max CFM/ft² 2.10 CFM/ft²


Return Fan Sizing Data Actual max CFM at Jun 1700 19265 CFM Standard CFM 18556 CFM Actual max CFM/ft² 2.10 CFM/ft²


Outdoor Ventilation Air Data Design airflow CFM 3000 CFM CFM/ft² 0.33 CFM/ft²

CFM/person 20.00 CFM/person


Zone Sizing Summary for VAV AHUProject Name: Tubman Museum 04/22/2003 Prepared by: psuae 03:49PM

Sizing Calculation Information Zone and Space Sizing Method: Zone CFM Peak zone sensible load Space CFM Individual peak space loads


Zone Sizing Data

Maximum Design Minimum Time Maximum Zone Cooling Air Air of Heating Floor Sensible Flow Flow Peak Load Area ZoneZone Name (MBH) (CFM) (CFM) Load (MBH) (ft²) CFM/ft²Zone 1 300.6 19265 193 Jun 1700 77.6 9165.0 2.10

Zone Terminal Sizing DataNo Zone Terminal Sizing Data required for this system.

Space Loads and Airflows

Cooling Time Air Heating Floor Zone Name / Sensible of Flow Load Area Space Space Name Mult. (MBH) Load (CFM) (MBH) (ft²) CFM/ft²Zone 1 262 Studio 1 21.8 Jun 1700 1395 8.3 400.0 3.49 263 Studio 1 21.9 Jun 1800 1404 2.2 630.0 2.23 264 Studio 1 19.9 Jun 1800 1277 3.0 550.0 2.32 273 Education Office 1 2.5 Jan 2300 163 0.0 120.0 1.36 274 Education Office 1 2.4 Jan 2300 151 0.0 110.0 1.37 275 Education Office 1 2.5 Jan 2300 157 0.0 115.0 1.37 276 Education Office 1 2.5 Jan 2300 157 0.0 115.0 1.37 277 Audio/Visual 1 4.5 Jan 2300 289 0.0 115.0 2.52 272 Corridor 1 1.2 Jan 2300 77 0.0 465.0 0.17 153 Office 1 4.0 Jun 1800 256 1.6 145.0 1.77 152 Kitchen 1 12.4 Jun 1800 792 2.1 355.0 2.23 151 Cafe 1 40.1 Jun 1700 2568 11.3 660.0 3.89 111 Museum Store 1 34.0 Jun 1700 2178 11.8 750.0 2.90 112 Inventory/Office 1 4.3 Jan 2300 277 0.0 200.0 1.39 113 Director 1 10.8 Jun 1800 691 4.6 400.0 1.73 114 Office 1 5.7 Jun 1800 364 3.3 180.0 2.02 116 Office 1 4.3 Jul 0900 275 1.2 135.0 2.04 117 Office 1 4.8 Jul 0900 309 1.7 150.0 2.06 118 Files 1 2.1 Jan 2300 133 0.0 110.0 1.21 119 Office 1 4.8 Jul 0900 309 1.7 150.0 2.06 125 Waiting 1 6.8 Jan 2300 437 0.0 300.0 1.46 132 Service Center 1 2.7 Jan 2300 175 0.0 130.0 1.35 130 Office 1 4.7 Jul 0900 301 1.6 145.0 2.08 131 Office 1 4.7 Jul 0900 301 1.6 145.0 2.08 133 Office 1 5.2 Jan 2300 335 0.0 260.0 1.29 134 Office 1 2.5 Jan 2300 163 0.0 120.0 1.36 135 Office 1 4.7 Jul 0900 301 1.6 145.0 2.08 136 Office 1 7.3 Oct 1400 467 1.6 270.0 1.73 137 Open Office 1 9.1 Oct 1400 581 2.6 270.0 2.15 138 Office 1 6.0 Sep 1400 382 3.4 145.0 2.63 139 Library Resource 1 47.2 Oct 1500 3024 12.3 1000.0 3.02 115 Boardroom 1 11.0 Jan 2300 702 0.0 380.0 1.85


Air System Design Load Summary for VAV AHUProject Name: Tubman Museum 04/22/2003 Prepared by: psuae 03:49PM

DESIGN COOLING DESIGN HEATING COOLING DATA AT Jul 1500 HEATING DATA AT DES HTG COOLING OA DB / WB 93.0 °F / 75.0 °F HEATING OA DB / WB 18.0 °F / 14.8 °F Sensible Latent Sensible LatentZONE LOADS Details (BTU/hr) (BTU/hr) Details (BTU/hr) (BTU/hr)Window & Skylight Solar Loads 1406 ft² 39745 - 1406 ft² - -Wall Transmission 6511 ft² 14659 - 6511 ft² 35316 -Roof Transmission 0 ft² 0 - 0 ft² 0 -Window Transmission 1406 ft² 15664 - 1406 ft² 40929 -Skylight Transmission 0 ft² 0 - 0 ft² 0 -Door Loads 56 ft² 1333 - 56 ft² 1354 -Floor Transmission 0 ft² 0 - 0 ft² 0 -Partitions 0 ft² 0 - 0 ft² 0 -Ceiling 0 ft² 0 - 0 ft² 0 -Overhead Lighting 19031 W 64933 - 0 0 -Task Lighting 0 W 0 - 0 0 -Electric Equipment 36950 W 126073 - 0 0 -People 150 36750 30750 0 0 0Infiltration - 0 0 - 0 0Miscellaneous - 0 0 - 0 0Safety Factor 0% / 0% 0 0 0% 0 0>> Total Zone Loads - 299156 30750 - 77599 0Zone Conditioning - 293869 30750 - 77150 0Plenum Wall Load 0% 0 - 0 0 -Plenum Roof Load 0% 0 - 0 0 -Plenum Lighting Load 0% 0 - 0 0 -Return Fan Load 16608 CFM 18615 - 2090 CFM -5893 -Ventilation Load 2586 CFM 52230 69343 325 CFM 18428 0Supply Fan Load 16608 CFM 37231 - 2090 CFM -11786 -Space Fan Coil Fans - 0 - - 0 -Duct Heat Gain / Loss 0% 0 - 0% 0 ->> Total System Loads - 401945 100093 - 77899 0Central Cooling Coil - 401945 100099 - -2280 0Central Heating Coil - 0 - - 80179 ->> Total Conditioning - 401945 100099 - 77899 0Key: Positive values are clg loads Positive values are htg loads Negative values are htg loads Negative values are clg loads




Appendix C - Chiller Performance Sheets

Air-Cooled Series R™

Rotary Liquid Chiller

Model RTAA

70 to 125 Tons

Built for the Industrial and Commercial Markets

RLC-PRC016-ENAugust 2002

23RLC-PRC016-EN

Table P-3 — 60 Hz RTAA 90 Performance Data EnglishEntering Condenser Air Temperature (Degrees F)

LWT 75 85 95 105 115(Deg. F) Tons kW EER Tons kW EER Tons kW EER Tons kW EER Tons kW EER

40 94.7 81.9 12.3 89.9 88.9 10.9 84.8 97.0 9.5 79.5 106.2 8.2 73.9 116.4 7.042 97.9 83.3 12.6 93.0 90.3 11.1 87.8 98.4 9.7 82.3 107.5 8.4 76.5 117.8 7.244 101.2 84.7 12.8 96.2 91.7 11.3 90.8 99.8 9.9 85.1 108.9 8.6 79.2 119.2 7.446 104.6 86.2 13.0 99.4 93.2 11.6 93.8 101.2 10.1 88.0 110.4 8.8 81.7 120.4 7.548 108.1 87.7 13.3 102.6 94.6 11.8 96.9 102.7 10.3 91.0 111.8 9.0 82.9 120.1 7.750 111.5 89.2 13.5 106.0 96.2 12.0 100.1 104.2 10.5 93.9 113.3 9.2 84.3 120.0 7.855 120.5 93.2 14.0 114.5 100.1 12.5 108.2 108.1 11.0 101.6 117.2 9.6 88.4 119.6 8.2

Notes:1. Ratings based on sea level altitude and evaporator fouling factor of 0.00010.2. Consult Trane representative for performance at temperatures outside of the ranges shown.3. kW input is for compressors only.4. EER = Energy Efficiency Ratio (Btu/watt-hour). Power inputs include compressors, condenser fans and control power.5. Ratings are based on an evaporator temperature drop of 10°F.6. 115°F performance data reflects Adaptive Control Microprocessor control algorithms.7. Interpolation between points is permissible. Extrapolation is not permitted.8. Rated in accordance with ARI Standard 550/590-98.



40 105.1 94.3 12.0 99.9 101.7 10.6 94.2 110.5 9.3 88.2 120.5 8.1 81.9 131.9 6.942 108.6 95.9 12.2 103.2 103.3 10.8 97.4 112.0 9.5 91.2 122.1 8.2 84.7 133.5 7.144 112.2 97.5 12.4 106.6 104.9 11.0 100.6 113.6 9.7 94.3 123.7 8.4 87.6 135.1 7.246 115.9 99.2 12.6 110.1 106.6 11.2 103.9 115.3 9.9 97.4 125.3 8.6 90.6 136.7 7.448 119.6 101.0 12.8 113.6 108.3 11.4 107.3 117.0 10.1 100.6 127.0 8.8 92.0 136.7 7.550 123.4 102.8 13.0 117.2 110.1 11.6 110.7 118.7 10.3 103.8 128.7 8.9 93.4 136.6 7.655 133.1 107.5 13.5 126.5 114.7 12.1 119.4 123.2 10.7 112.0 133.1 9.3 98.1 136.6 8.0


Performance Data

MetricEntering Condenser Air Temperature (Degrees C)

LWT 30 35 40 45(Deg. C) kWo kWi COP kWo kWi COP kWo kWi COP kWo kWi COP

6 329.4 91.6 3.2 312.9 98.9 2.9 295.3 107.1 2.5 277.1 116.2 2.28 349.8 94.2 3.4 332.3 101.5 3.0 313.6 109.7 2.6 294.3 118.8 2.3

10 370.6 96.9 3.5 352.0 104.2 3.1 332.6 112.4 2.7 307.7 120.0 2.4

Notes:1. Ratings based on sea level altitude and evaporator fouling factor of 0.0000176.2. Consult Trane representative for performance at temperatures outside of the ranges shown.3. kWi input is for compressors only.4. COP = Coefficient of Performance (kWo/kWi). Power inputs include compressors, condenser fans and control power.5. Ratings are based on an evaporator temperature drop of 5.6°C.6. 115°F performance data reflects Adaptive Control Microprocessor control algorithms.7. Interpolation between points is permissible. Extrapolation is not permitted.8. Rated in accordance with ARI Standard 550/590-98.



6 365.7 104.8 3.2 347.0 112.7 2.8 327.3 121.6 2.5 306.6 131.7 2.28 387.5 107.7 3.3 367.8 115.6 2.9 347.0 124.6 2.6 325.6 134.7 2.2

10 410.0 110.9 3.4 389.2 118.7 3.0 367.4 127.7 2.7 341.1 136.5 2.3


RLC-PRC016-EN24



40 125.7 113.2 12.1 119.3 122.0 10.8 112.4 132.3 9.4 105.2 144.1 8.2 97.6 157.5 7.042 129.9 115.2 12.3 123.3 124.0 11.0 116.2 134.3 9.6 108.8 146.1 8.3 100.9 159.5 7.144 134.1 117.2 12.5 127.3 126.0 11.2 120.1 136.3 9.8 112.4 148.1 8.5 104.3 161.5 7.346 138.5 119.4 12.7 131.4 128.1 11.3 124.0 138.3 10.0 116.1 150.1 8.7 106.7 162.2 7.448 142.9 121.5 12.9 135.6 130.2 11.5 127.9 140.4 10.2 119.8 152.2 8.8 107.2 160.2 7.550 147.4 123.7 13.1 139.9 132.4 11.7 132.0 142.6 10.3 123.6 154.4 9.0 107.6 158.0 7.755 159.0 129.5 13.6 150.9 138.0 12.2 142.3 148.1 10.7 133.2 159.8 9.4 109.5 152.1 8.1




40 113.3 102.5 11.9 107.7 110.7 10.6 101.7 120.3 9.3 95.2 131.2 8.1 88.4 143.6 6.942 117.1 104.3 12.2 111.3 112.4 10.8 105.1 122.0 9.5 98.4 132.9 8.2 91.5 145.3 7.044 120.9 106.1 12.4 114.9 114.2 11.0 108.5 123.7 9.7 101.7 134.7 8.4 94.6 147.1 7.246 124.8 107.9 12.6 118.6 116.0 11.2 112.0 125.5 9.9 105.1 136.4 8.6 97.7 148.9 7.448 128.8 109.8 12.8 122.4 117.8 11.4 115.6 127.3 10.0 108.5 138.3 8.7 99.4 148.9 7.550 132.8 111.7 13.0 126.2 119.7 11.6 119.3 129.2 10.2 111.9 140.1 8.9 101.0 148.7 7.655 143.1 116.7 13.4 136.1 124.7 12.0 128.6 134.1 10.7 120.6 144.9 9.3 103.6 145.4 8.0




6 394.1 114.0 3.2 374.1 122.6 2.8 353.0 132.4 2.5 331.2 143.4 2.28 417.3 117.2 3.3 396.6 125.8 2.9 374.5 135.6 2.6 351.2 146.7 2.2

10 441.6 120.6 3.4 419.5 129.2 3.0 395.9 139.0 2.7 369.5 149.2 2.3




6 436.7 125.7 3.2 414.2 135.1 2.8 390.3 145.6 2.5 365.3 157.5 2.28 462.7 129.4 3.3 438.8 138.7 2.9 413.5 149.3 2.6 387.5 161.2 2.3

10 489.1 133.3 3.4 464.1 142.6 3.0 437.7 153.1 2.7 410.0 165.0 2.3


Performance Data

RLC-PRC016-EN28

Performance Data

Table P-14 — ARI Part-Load Values (50 Hz)Unit % Load Tons EER IPLVRTAA 70 100 60.1 11.0 15.0

75 45.0 13.250 30.0 15.925 15.0 17.9

RTAA 80 100 69.3 10.9 14.575 52.0 12.850 34.7 16.325 17.3 13.8

RTAA 90 100 78.8 10.7 13.8

75 59.1 12.450 39.4 14.825 19.7 15.0

RTAA 100 100 87.3 10.4 13.775 65.5 12.050 43.7 14.625 21.8 16.0

RTAA 110 100 94.3 10.4 13.8

75 70.7 12.050 47.1 14.825 23.6 16.6

RTAA125 100 104.0 10.5 13.775 78.0 12.150 52.0 14.825 26.0 15.3

Table P-13 — ARI Part-Load Values (60 Hz)Unit % Load Tons EER IPLVRTAA 70 100 69.3 10.2 13.6

75 51.9 12.050 34.6 14.625 17.3 16.1

RTAA 80 100 79.8 10.2 13.275 59.8 11.750 39.8 14.925 19.9 12.6

RTAA 90 100 90.8 9.9 12.675 68.0 11.350 45.3 13.525 22.7 13.6

RTAA 100 100 100.6 9.7 12.675 75.5 11.050 50.3 13.525 25.2 14.8

RTAA 110 100 108.5 9.7 12.675 81.2 11.050 54.2 13.725 27.1 14.8

RTAA125 100 120.1 9.8 12.675 89.7 11.250 59.8 13.725 29.9 13.4



Appendix D - Chiller EES Equations - Sample Parametric Table

File:P:\Thesis\Mechanical Depth\EES Chillers Case A.EES 4/22/2003 4:05:46 PM Page 1EES Ver. 6.703: #463: Architectural Engineering at Penn State University

Chris ChampagneAE Senior ThesisTubman African American Museum

Calculating optimum size for chillers

(2) Trane Air-Cooled Series R Rotary Liquid Chillers - RTAA model

Chillers-Case A - Equal Size - 120.1 tons - RTAA 125

Part Loading-Case A - Lowest Design Capacity = 40 %, Upper Design Capacity = 90 %

Procedure to determine the number of chillers operating at a given condition

N = Number of Chillers operating

Qop = The current tonnage performed by the chiller or by each chiller if both are on

Ptotal = Total power consumed [kWh] by either one chiller or both combined

Procedure NumberOfChillers (UCap, Qload, Pop : N, Qop, Ptotal)

If Qload < UCap Then

N := 1

Qop := Qload

Ptotal := Pop · 1

Else

N := 2

Qop := Qload

2

Ptotal := Pop · 2

EndIf

End NumberOfChillers

Qdesign = Design size of chiller [tons]

Qdesign = 120.1

Pdesign = Design power [kW]

Pdesign = 136.3

Qload = Current load from HAP based on Toa and Tchws

Qload = Qcv + Qvav

12

Qflow = Chilled water flow rateEWT = 55 F and LWT = 45 F, therefore delta T = 10 F


Qflow = Qop · 2455 – 45

LPercent = Low percentage of part load performance

LPercent = 40

UPercent = Upper percentage of part load performance

UPercent = 90

LCap= Lowest Capacity

LCap = LPercent

100 · Qdesign

UCap = Highest Cacapity

UCap = UPercent

100 · Qdesign

Call NumberOfChillers UCap , Qload , Pop : N , Qop , Ptotal

Coefficients for default DOE-2 electric air-cooled chiller model

CAPFT - Full load capacity as a fraction of rated capacity

a1 = – 0.09464899

b1 = 0.0383407

c1 = – 0.00009205

d1 = 0.00378007

e1 = – 0.00001375

f1 = – 0.00015464

EIRFT - Full load efficiency (kW/ton) as a fraction of rated capacity

a2 = 0.13545636

b2 = 0.02292946

c2 = – 0.00016107

d2 = – 0.00235396

e2 = 0.00012991

f2 = – 0.00018685

EIRFPLR - Fraction of full load power as a function of fraction of full load output

a3 = 0.03648722

b3 = 0.73474298

c3 = 0.21994748

Day = Day of the month

Time = Period of time during specified day - 1 hour increments


Toa = Dry bulb, outdoor air temperature

Tchws = Chilled water supply temperature

Qavail = Available capacity at arbitrary Tchws and Toa

Qavail = Qflow · a1 + b1 · Tchws + c1 · Tchws2 + d1 · Toa + e1 · Toa

2 + f1 · Tchws · Toa

CAPFT = Full load capacity as a fraction of rated capacity

CAPFT = a1 + b1 · Tchws + c1 · Tchws2 + d1 · Toa + e1 · Toa


Also defined by CAPFT = Qavail / Qflow

EIRFT = Full load efficiency (kW/ton) as fraction of rated capacity

EIRFT = a2 + b2 · Tchws + c2 · Tchws2 + d2 · Toa + e2 · Toa


PLR calculations

PLR = Qop

UCap

EIRFPLR = Fraction of full load power as a function of fraction of full load output

EIRFPLR = a3 + b3 · PLR + c3 · PLR 2

Pop = Operating power of each chiller

Pop = Pdesign · EIRFT · CAPFT · EIRFPLR

Calculation of the kW/ton for the model

Efficiency = Pop

Qop

Energy Efficiency Ratio

EER = 12

Efficiency

Coefficient of Performance

COP = 3.516

Efficiency


Parametric Table: OctoberDay Time Toa Tchws Qcv Qvav Qload N Qdesign Qavail LPercent LCap UPercent UCap Qop Qflow CAPFT EIRFT EIRFPLR PLR Pop Ptotal Efficiency EER COP

[Date] [Hour] [F] [F] [MBH] [MBH] [tons] [# of Chillers] [tons] [tons] [%] [tons] [%] [tons] [tons] [gpm] [kWh] [kWh] [kW/ton]

Run 1 1 0 71.8 45 1272 367.5 136.6 2 120.1 187.8 40 48.04 90 108.1 68.32 164 1.145 0.7381 0.5887 0.632 67.83 135.7 0.9928 12.09 3.541 Run 2 1 100 70.9 45 1292 372.3 138.7 2 120.1 191.4 40 48.04 90 108.1 69.35 166.5 1.15 0.7311 0.5985 0.6416 68.57 137.1 0.9887 12.14 3.556 Run 3 1 200 70.1 45 1264 360.8 135.4 2 120.1 187.5 40 48.04 90 108.1 67.71 162.5 1.154 0.7251 0.5831 0.6264 66.49 133 0.982 12.22 3.581 Run 4 1 300 69.4 45 1247 352.9 133.3 2 120.1 185.1 40 48.04 90 108.1 66.65 160 1.157 0.7199 0.5731 0.6166 65.09 130.2 0.9767 12.29 3.6 Run 5 1 400 68.9 45 1235 347.2 131.9 2 120.1 183.6 40 48.04 90 108.1 65.94 158.3 1.16 0.7163 0.5665 0.61 64.16 128.3 0.9731 12.33 3.613 Run 6 1 500 68.7 45 1233 344.5 131.4 2 120.1 183.1 40 48.04 90 108.1 65.72 157.7 1.161 0.7149 0.5645 0.608 63.86 127.7 0.9718 12.35 3.618 Run 7 1 600 69 45 1229 341.7 130.9 2 120.1 182.1 40 48.04 90 108.1 65.45 157.1 1.159 0.717 0.5621 0.6056 63.69 127.4 0.9731 12.33 3.613 Run 8 1 700 69.9 45 1223 339.3 130.2 2 120.1 180.5 40 48.04 90 108.1 65.11 156.3 1.155 0.7236 0.5589 0.6024 63.66 127.3 0.9777 12.27 3.596 Run 9 1 800 71.5 45 1223 339.3 130.2 2 120.1 179.2 40 48.04 90 108.1 65.1 156.2 1.147 0.7357 0.5588 0.6023 64.26 128.5 0.9871 12.16 3.562 Run 10 1 900 73.7 45 1223 339.5 130.2 2 120.1 177.4 40 48.04 90 108.1 65.1 156.2 1.135 0.7536 0.5588 0.6023 65.16 130.3 1.001 11.99 3.513 Run 11 1 1000 76.3 45 1233 348.3 131.8 2 120.1 177.4 40 48.04 90 108.1 65.9 158.2 1.122 0.7763 0.5662 0.6097 67.2 134.4 1.02 11.77 3.448 Run 12 1 1100 79.3 45 1189 334.8 127 2 120.1 168.5 40 48.04 90 108.1 63.48 152.4 1.106 0.8046 0.5439 0.5873 65.95 131.9 1.039 11.55 3.384 Run 13 1 1200 82 45 1116 310.9 118.9 2 120.1 155.7 40 48.04 90 108.1 59.45 142.7 1.091 0.8321 0.5071 0.55 62.76 125.5 1.056 11.37 3.33 Run 14 1 1300 84.1 45 1083 299.7 115.2 2 120.1 149.3 40 48.04 90 108.1 57.6 138.3 1.08 0.8548 0.4905 0.5329 61.71 123.4 1.071 11.2 3.282 Run 15 1 1400 85.5 45 1072 295.2 113.9 2 120.1 146.6 40 48.04 90 108.1 56.97 136.7 1.072 0.8706 0.4848 0.527 61.67 123.3 1.083 11.08 3.248 Run 16 1 1500 86 45 1076 294.7 114.2 2 120.1 146.6 40 48.04 90 108.1 57.11 137.1 1.069 0.8764 0.4861 0.5284 62.09 124.2 1.087 11.04 3.234 Run 17 1 1600 85.5 45 1076 291.9 114 2 120.1 146.6 40 48.04 90 108.1 56.99 136.8 1.072 0.8706 0.485 0.5272 61.7 123.4 1.083 11.08 3.248 Run 18 1 1700 84.3 45 1061 283.8 112 2 120.1 145 40 48.04 90 108.1 56.01 134.4 1.079 0.8571 0.4763 0.5182 60.01 120 1.071 11.2 3.282 Run 19 1 1800 82.4 45 1032 272.5 108.7 2 120.1 142 40 48.04 90 108.1 54.33 130.4 1.089 0.8364 0.4614 0.5027 57.28 114.6 1.054 11.38 3.335 Run 20 1 1900 80.1 45 1010 264 106.2 1 120.1 280.7 40 48.04 90 108.1 106.2 254.8 1.101 0.8126 0.9705 0.9824 118.4 118.4 1.115 10.76 3.153 Run 21 1 2000 77.9 45 999.6 259.2 104.9 1 120.1 280.3 40 48.04 90 108.1 104.9 251.8 1.113 0.7911 0.9567 0.9705 114.8 114.8 1.095 10.96 3.212 Run 22 1 2100 76 45 997.9 257.3 104.6 1 120.1 282 40 48.04 90 108.1 104.6 251 1.123 0.7735 0.9535 0.9677 112.9 112.9 1.08 11.12 3.257 Run 23 1 2200 74.2 45 1004 258 105.2 1 120.1 285.9 40 48.04 90 108.1 105.2 252.4 1.133 0.7578 0.9596 0.973 112.3 112.3 1.068 11.24 3.294 Run 24 1 2300 72.9 45 1029 264.7 107.8 1 120.1 294.9 40 48.04 90 108.1 107.8 258.8 1.139 0.7469 0.9885 0.9977 114.7 114.7 1.063 11.29 3.307 Run 25 2 0 71.8 45 1062 273.8 111.3 2 120.1 153 40 48.04 90 108.1 55.66 133.6 1.145 0.7381 0.4732 0.515 54.51 109 0.9794 12.25 3.59 Run 26 2 100 70.9 45 1032 262.9 107.9 1 120.1 297.8 40 48.04 90 108.1 107.9 259 1.15 0.7311 0.9892 0.9983 113.3 113.3 1.05 11.42 3.348 Run 27 2 200 70.1 45 983.9 246.3 102.5 1 120.1 283.9 40 48.04 90 108.1 102.5 246 1.154 0.7251 0.9312 0.9484 106.2 106.2 1.036 11.59 3.394 Run 28 2 300 69.4 45 971.9 241.2 101.1 1 120.1 280.8 40 48.04 90 108.1 101.1 242.6 1.157 0.7199 0.916 0.9353 104 104 1.029 11.66 3.416 Run 29 2 400 68.9 45 962.7 236.7 99.95 1 120.1 278.3 40 48.04 90 108.1 99.95 239.9 1.16 0.7163 0.904 0.9247 102.4 102.4 1.024 11.72 3.433 Run 30 2 500 68.7 45 952.1 232.7 98.73 1 120.1 275.1 40 48.04 90 108.1 98.73 237 1.161 0.7149 0.8911 0.9134 100.8 100.8 1.021 11.75 3.443 Run 31 2 600 69 45 938.7 227.6 97.19 1 120.1 270.5 40 48.04 90 108.1 97.19 233.3 1.159 0.717 0.875 0.8992 99.15 99.15 1.02 11.76 3.447 Run 32 2 700 69.9 45 938.6 228.5 97.26 1 120.1 269.6 40 48.04 90 108.1 97.26 233.4 1.155 0.7236 0.8757 0.8998 99.74 99.74 1.026 11.7 3.429 Run 33 2 800 71.5 45 943.7 231.8 97.96 1 120.1 269.6 40 48.04 90 108.1 97.96 235.1 1.147 0.7357 0.883 0.9063 101.5 101.5 1.037 11.58 3.392 Run 34 2 900 73.7 45 939.1 232.5 97.63 1 120.1 266 40 48.04 90 108.1 97.63 234.3 1.135 0.7536 0.8796 0.9033 102.6 102.6 1.051 11.42 3.347 Run 35 2 1000 76.3 45 934.5 232.9 97.28 1 120.1 261.9 40 48.04 90 108.1 97.28 233.5 1.122 0.7763 0.8759 0.9 104 104 1.069 11.23 3.29 Run 36 2 1100 79.3 45 942.5 237.1 98.3 1 120.1 260.9 40 48.04 90 108.1 98.3 235.9 1.106 0.8046 0.8866 0.9094 107.5 107.5 1.094 10.97 3.215 Run 37 2 1200 82 45 951.3 241.4 99.39 1 120.1 260.3 40 48.04 90 108.1 99.39 238.5 1.091 0.8321 0.8981 0.9195 111.1 111.1 1.118 10.73 3.144 Run 38 2 1300 84.1 45 955.4 239 99.53 1 120.1 257.9 40 48.04 90 108.1 99.53 238.9 1.08 0.8548 0.8996 0.9208 113.2 113.2 1.137 10.55 3.092 Run 39 2 1400 85.5 45 959.8 239.4 99.93 1 120.1 257.1 40 48.04 90 108.1 99.93 239.8 1.072 0.8706 0.9038 0.9245 115 115 1.15 10.43 3.056 Run 40 2 1500 86 45 959.7 238 99.81 1 120.1 256.1 40 48.04 90 108.1 99.81 239.5 1.069 0.8764 0.9025 0.9234 115.3 115.3 1.155 10.39 3.045 Run 41 2 1600 85.5 45 959.6 236.3 99.66 1 120.1 256.4 40 48.04 90 108.1 99.66 239.2 1.072 0.8706 0.9009 0.922 114.6 114.6 1.15 10.44 3.058 Run 42 2 1700 84.3 45 959.4 234.6 99.5 1 120.1 257.6 40 48.04 90 108.1 99.5 238.8 1.079 0.8571 0.8992 0.9205 113.3 113.3 1.139 10.54 3.088 Run 43 2 1800 82.4 45 959.3 233.6 99.41 1 120.1 259.8 40 48.04 90 108.1 99.41 238.6 1.089 0.8364 0.8983 0.9197 111.5 111.5 1.122 10.7 3.134 Run 44 2 1900 80.1 45 959.2 232.8 99.33 1 120.1 262.6 40 48.04 90 108.1 99.33 238.4 1.101 0.8126 0.8975 0.919 109.5 109.5 1.102 10.89 3.19 Run 45 2 2000 77.9 45 959.1 231.9 99.25 1 120.1 265.2 40 48.04 90 108.1 99.25 238.2 1.113 0.7911 0.8966 0.9182 107.6 107.6 1.084 11.07 3.243 Run 46 2 2100 76 45 959 231 99.17 1 120.1 267.3 40 48.04 90 108.1 99.17 238 1.123 0.7735 0.8957 0.9174 106.1 106.1 1.07 11.22 3.287 Run 47 2 2200 74.2 45 963.4 231.4 99.57 1 120.1 270.7 40 48.04 90 108.1 99.57 239 1.133 0.7578 0.8999 0.9211 105.3 105.3 1.057 11.35 3.325 Run 48 2 2300 72.9 45 967.9 231.9 100 1 120.1 273.4 40 48.04 90 108.1 100 240 1.139 0.7469 0.9043 0.925 104.9 104.9 1.049 11.44 3.351 Run 49 3 0 71.8 45 967.7 231.1 99.9 1 120.1 274.6 40 48.04 90 108.1 99.9 239.8 1.145 0.7381 0.9034 0.9242 104.1 104.1 1.042 11.52 3.375 Run 50 3 100 70.9 45 958.7 227.8 98.88 1 120.1 272.8 40 48.04 90 108.1 98.88 237.3 1.15 0.7311 0.8926 0.9147 102.3 102.3 1.034 11.6 3.399 Run 51 3 200 70.1 45 950.6 224.6 97.93 1 120.1 271.2 40 48.04 90 108.1 97.93 235 1.154 0.7251 0.8827 0.906 100.7 100.7 1.028 11.67 3.421 Run 52 3 300 69.4 45 951.9 224.2 98.01 1 120.1 272.3 40 48.04 90 108.1 98.01 235.2 1.157 0.7199 0.8835 0.9067 100.3 100.3 1.024 11.72 3.434 Run 53 3 400 68.9 45 953.3 223.9 98.1 1 120.1 273.1 40 48.04 90 108.1 98.1 235.4 1.16 0.7163 0.8845 0.9076 100.2 100.2 1.021 11.75 3.443 Run 54 3 500 68.7 45 951.6 222.7 97.86 1 120.1 272.7 40 48.04 90 108.1 97.86 234.9 1.161 0.7149 0.882 0.9053 99.77 99.77 1.02 11.77 3.449 Run 55 3 600 69 45 950 221.7 97.64 1 120.1 271.7 40 48.04 90 108.1 97.64 234.3 1.159 0.717 0.8797 0.9033 99.68 99.68 1.021 11.75 3.444 Run 56 3 700 69.9 45 949.9 222 97.66 1 120.1 270.7 40 48.04 90 108.1 97.66 234.4 1.155 0.7236 0.8799 0.9035 100.2 100.2 1.026 11.69 3.426 Run 57 3 800 71.5 45 957.9 225.1 98.58 1 120.1 271.3 40 48.04 90 108.1 98.58 236.6 1.147 0.7357 0.8896 0.912 102.3 102.3 1.038 11.56 3.388 Run 58 3 900 73.7 45 971.3 233.3 100.4 1 120.1 273.5 40 48.04 90 108.1 100.4 240.9 1.135 0.7536 0.9085 0.9287 105.9 105.9 1.055 11.37 3.331 Run 59 3 1000 76.3 45 985.9 240.5 102.2 1 120.1 275.1 40 48.04 90 108.1 102.2 245.3 1.122 0.7763 0.9278 0.9455 110.1 110.1 1.077 11.14 3.263



Appendix E - Current Chilled Water Schematic - Current Pump Cutsheet and System Graph



Appendix F - Proposed Chilled Water Schematic - Proposed Pump System Graph



Appendix G - Bell and Gossett ESP Plus Online Program

Operating Cost Analysis and System Modeling Results

Constant Speed Cost Analysis

Pump Series: 1510 Pump Model: 2-1/2BB Motor Size: 7.5 Pump Speed: 1750 Impeller Diameter=8.75 in. Pump Flow = 290 GPM Pump Head = 65 Feet

Number of Pumps = 2 Control Head = 0 Feet System Peak Flow = 580 GPM

Program Version M1.08

School/University, Cooling

Staging Method: END-OF-CURVE

Motor Size: 7.5HP Service Factor1.15 Manufacturer: US Prem Eff Catalog: E895

Load HoursFlow GPM

HeadFeet

PumpEff. BHP

MotorEff. kWHR Cost/day

Wire/Water Eff

Single Pump Operation 30% 2.40 174.0 76.84 71.59 4.72 91.86 9.19 $0.92 65.76%





Two Pumps Operating in Parallel

Page 1 of 3ESP-PLUS ON-LINE

4/22/2003file://P:\Thesis\FINAL%20REPORT\ESP-PLUS%20ON-LINE.htm

Variable Speed Cost Analysis

W/W Efficiency Comparison Table

Drive/Motor Efficiency Table (adjusted for load)

80% 2.40232.0

232.0

72.39

72.39

76.02

76.02

5.58

5.58

92.00 92.00 21.71 $2.17 69.94%


90% 1.20261.0

261.0

69.34

69.34

76.48

76.48

5.98

5.98

92.00 92.00 11.62 $1.16 70.37%

Total Kilowatt Hours = 45,339.4

Total Hours per Year = 8,760

Cost per kwhr = $0.10

Annual Operating Cost = $4,533.94

Staging Method: Best Efficiency Motor Size: 7.5 Motor/Drive: Typical, Hi-Eff

LOAD W/W Eff.1 Pump

W/W Eff.2 Pumps

30% 42.7% 60.7%

40% 42.7% 63.4%

50% 42.4% 64.1%

60% EOC 64.0%

70% EOC 64.8%

80% EOC 64.4%

90% EOC 64.1%

Generate Eff. Comparison Curve

Speed Ratio 0% 5% 10% 20% 30% 40% 60% 80% 100%



Select another pump Return to FHS Home Page

Combined Efficiency 00.0 51.8 67.2 74.3 82.0 85.5 85.5 84.6 83.8

Load HoursFlow GPM

Head Feet RPM

PumpEff. BHP

Drive/MotorEff. kWHR Cost/day

Wire/Water Eff


30% 2.40 87.0 87.0

5.9 5.9

523 523

74.13

74.13 0.17 81.90 0.76 $0.08 60.7%

40% 3.60116.0

116.0

10.4 10.4

698 698

74.13

74.13 0.41 85.49 2.58 $0.26 63.4%

50% 4.80145.0

145.0

16.2 16.2

872 872

74.89

74.89 0.79 85.63 6.64 $0.66 64.1%

60% 4.80174.0

174.0

23.4 23.4

1046

1046

74.89

74.89 1.37 85.52 11.49 $1.15 64.0%

70% 2.40203.0

203.0

31.8 31.8

1221

1221

76.11

76.11 2.15 85.09 9.02 $0.90 64.8%

80% 2.40232.0

232.0

41.6 41.6

1395

1395

76.11

76.11 3.20 84.66 13.54 $1.35 64.4%

90% 1.20261.0

261.0

52.6 52.6

1570

1570

76.11

76.11 4.56 84.22 9.69 $0.97 64.1%

Total Kilowatt Hours = 19,610.0

Total Hours per Year = 8,760

Cost per kwhr = $0.10

Annual Operating Cost = $1,961.00





Appendix H - EES Pump Formatted Equations

File:P:\Thesis\Mechanical Depth\EES Pumps FINAL.EES 4/22/2003 5:16:49 PM Page 1EES Ver. 6.703: #463: Architectural Engineering at Penn State University

Chris ChampagneAE Senior ThesisTubman African American Museum

Cost savings of switching from constant speed to variable speed pumps

Constant Speed Functions

Constant Speed Total Power Function

Function Power (Qp, Hp, η t)

If Qp < 290 Then

Ptotal := Qp · Hp

3960 · η t · 0.7457

Else

Ptotal := 2 · 0.5 · Qp · Hp

3960 · η t · 0.7457

EndIf

Power := Ptotal

End Power

Function Pumpeff (N, No, Qp)

Constant Speed Pump Efficiency Function

If Qp < 290 Then

ηp := 8.802 + 0.5609 · Qp ·

No

N – 0.0011092322 · Qp ·

No

N

2

100

Else

ηp := 8.802 + 0.5609 · 0.5 · Qp ·

No

N – 0.0011092322 · 0.5 · Qp ·

No

N

2

100

EndIf

Pumpeff := ηp

End Pumpeff

Function Pumpc (Qp)

Constant Speed Pump Model Function

If Qp < 290 Then

Hp := 75.89 + 0.07963 · Qp – 0.0004149 · Qp2

Else

Hp := 75.89 + 0.07963 · 0.5 · Qp – 0.0004149 · 0.5 · Qp2


EndIf

Pumpc := Hp

End Pumpc

Function Effoverall,c (Qp, Qsys, Hsys, Hfixed, Ptotal)

Constant Speed Overall Efficiency Function

ηoverall :=

Hfixed + Qp

Qsys

2 · Hsys – Hfixed · Qp

3960Ptotal

0.7457

Effoverall,c := ηoverall

End Effoverall,c

Function PerNPL (Qp, Ptotal)

Constant Speed PercentNPL Function

If Qp < 290 Then

bhp := 7.25

PercentNPL := Ptotal

0.7457 · bhp

Else

bhp := 7.25


2 · 0.7457 · bhp

EndIf

PerNPL := PercentNPL

End PerNPL

Function Power v (Qp, Hp, η t)

Variable Speed Functions

Variable Speed Total Power Function

If Qp < 256 Then

Ptotal := Qp · Hp

3960 · η t · 0.7457

Else

Ptotal := 2 · 0.5 · Qp · Hp

3960 · η t · 0.7457

EndIf


Powerv := Ptotal

End Power v

Function Pumpeff,v (N, No, Qp)

Variable Speed Pump Efficiency Function

If Qp < 256 Then

ηp := 8.802 + 0.5609 · Qp ·

No

N – 0.0011092322 · Qp ·

No

N

2

100

Else

ηp := 8.802 + 0.5609 · 0.5 · Qp ·

No

N – 0.0011092322 · 0.5 · Qp ·

No

N

2

100

EndIf

Pumpeff,v := ηp

End Pumpeff,v

Function Pumpv (Qp, Hfixed, Qsys, Hsys)

Variable Speed Model Function

If Qp < 256 Then

Hp := 75.89 + 0.07963 · Qp – 0.0004149 · Qp2

Hp := Hfixed + Qp

Qsys

2 · Hsys – Hfixed

Else

Hp := 75.89 + 0.07963 · 0.5 · Qp – 0.0004149 · 0.5 · Qp2

Hp := Hfixed + 0.5 · Qp

Qsys


EndIf

Pumpv := Hp

End Pumpv

Function Effoverall,v (Qp, Hp, Qsys, Hsys, Hfixed, Ptotal)

Variable Speed Overall Efficiency Function

ηoverall :=

Hp · Qp

3960Ptotal

0.7457


Hp := Hfixed + Qp

Qsys


Effoverall,v := ηoverall

End Effoverall,v

Function PerNPL,v (Qp, Ptotal)

Variable Speed PercentNPL Function

If Qp < 256 Then

bhp := 7.25


0.7457 · bhp

Else

bhp := 7.25


2 · 0.7457 · bhp

EndIf

PerNPL,v := PercentNPL

End PerNPL,v

Function Speed (Qp, Qsys, No)

Speed Function

If Qp < 256 Then

Nfixed := 790.1

N := Nfixed + Qp

Qsys

2 · No – Nfixed

Else

Nfixed := 790.1

N := Nfixed + 0.5 · Qp

Qsys

2 · No – Nfixed

EndIf

Speed := N

End Speed

Function Efficiency (NPL)

Equations used for Constant and Variable Speed Functions

Motor Efficiency Function


PercentNPL := NPL

If PercentNPL <= 0.175 Then

ηm := 0.01541 + 4.486 · PercentNPL

Else

ηm := 0.6783 + 0.7421 · PercentNPL – 0.5021 · PercentNPL2

EndIf

Efficiency := ηm

End Efficiency

Function Driveeff (N, No)

Drive Efficiency Function

ηd := 0.562 + 0.8671 · NNo

– 0.4643 · NNo

2

Driveeff := ηd

End Driveeff

Constants

No = 1750

Nc = 1750

Nfixed = 790.1

Qsys = 580

Hsys = 65

Hfixed = 30

Calculation of Percentage of Name Plate Load (Constant and Variable Speed)

PercentNPL,c = PerNPL Qp , Ptotal,c

PercentNPL,v = PerNPL,v Qp , Ptotal,v

Motor Efficiency

ηm,c = Efficiency PercentNPL,c

ηm,v = Efficiency PercentNPL,v

Pump Efficiency

ηp,c = Pumpeff Nc , No , Qp

ηp,v = Pumpeff,v N , No , Qp

Drive Efficiency

ηd,c = 1


ηd,v = Driveeff N , No

Total Efficiency

η t,c = ηd,c · ηm,c · ηp,c

η t,v = ηd,v · ηm,v · ηp,v

Overall Efficiency

ηoverall,c = Effoverall,c Qp , Qsys , Hsys , Hfixed , Ptotal,c

ηoverall,v = Effoverall,v Qp , Hp,v , Qsys , Hsys , Hfixed , Ptotal,v

Pump Head

Hp,c = Pumpc Qp

Hp,v = Pumpv Qp , Hfixed , Qsys , Hsys

Drive Speed

N = Nfixed + Qp

Qsys

2 · No – Nfixed

Nv = Speed Qp , Qsys , No

Total Power

Ptotal,c = Power Qp , Hp,c , η t,c

Ptotal,v = Power v Qp , Hp,v , η t,v

Total Power Savings

Psavings = Ptotal,c – Ptotal,v

0 100 200 300 400 500 6000

2

4

6

8

10

Qp [gpm]

Tota

l Pow

er (k

W)

Ptotal,cPtotal,cPtotal,vPtotal,v


This plot shows the energy savings of switching from constant speed to variable speed pumps for the chilled water system.

0 100 200 300 400 500 600-0.5

0

0.5

1

1.5

2

2.5

3

3.5

4

4.5

5

Qp [gpm]

P sav

ings

[kW

]

0 50 100 150 200 250 300 350 400 45030

40

50

60

70

80

Qp (GPM)

Hp

(FT

H2O

)


0 50 100 150 200 250 300 350 400 4500

10

20

30

40

50

60

70

80

Qp (GPM)

η p (%

)



Appendix I - Luminaire Product Data



Appendix J - Electrical Riser Diagram



Appendix K - Electrical Data for Chiller

29RLC-PRC016-EN

Electrical Data

Table E-1 — Electrical Data (50 & 60 Hz, 3 Phase)Unit Wiring Motor Data

FansUnit Rated # of Power Max. Fuse, HACR Rec. Time Compressor (Each) (Each) ControlSize Voltage (9) Connections (1) MCA (3) Breaker or MOP (2,11) Delay or RDE (4) Qty RLA (5) LRA (8) Qty. kW FLA kW (7, 10)RTAA 70 200/60 1 300 400 350 2 115 - 115 800 - 800 8 1.0 5.1 0.75

230/60 1 265 350 300 2 100 - 100 690 - 690 8 1.0 5.0 0.75380/60 1 163 200 200 2 61 - 61 400 - 400 8 1.0 3.2 0.75460/60 1 133 175 150 2 50 - 50 330 - 330 8 1.0 2.5 0.75575/60 1 108 125 125 2 40 - 40 270 - 270 8 1.0 2.2 0.75380/50 1 140 175 150 2 53 - 53 308 - 308 8 0.7 2.5 0.75400/50 1 133 175 150 2 50 - 50 325 - 325 8 0.7 2.5 0.75415/50 1 128 175 150 2 48 - 48 337 - 337 8 0.7 2.5 0.75

RTAA 80 200/60 1 361 500 400 2 142 - 142 800 - 800 8 1.0 5.1 0.75230/60 1 319 400 350 2 124 - 124 760 - 760 8 1.0 5.0 0.75380/60 1 194 250 225 2 75 - 75 465 - 465 8 1.0 3.2 0.75460/60 1 160 200 175 2 62 - 62 380 - 380 8 1.0 2.5 0.75575/60 1 131 175 150 2 50 - 50 304 - 304 8 1.0 2.2 0.75380/50 1 167 200 175 2 65 - 65 356 - 356 8 0.7 2.5 0.75400/50 1 160 200 175 2 62 - 62 375 - 375 8 0.7 2.5 0.75415/50 1 155 200 175 2 60 - 60 389 - 389 8 0.7 2.5 0.75

RTAA 90 200/60 1 428 600 500 2 192 - 142 990 - 800 9 1.0 5.1 0.75230/60 1 378 500 450 2 167 - 124 820 - 760 9 1.0 5.0 0.75380/60 1 230 300 300 2 101 - 75 497 - 465 9 1.0 3.2 0.75460/60 1 190 250 225 2 84 - 62 410 - 380 9 1.0 2.5 0.75575/60 1 154 200 175 2 67 - 50 328 - 304 9 1.0 2.2 0.75380/50 1 195 250 225 2 88 - 65 386 - 356 9 0.7 2.5 0.75400/50 1 190 250 225 2 84 - 62 402 - 375 9 0.7 2.5 0.75415/50 1 182 250 225 2 81 - 60 417 -389 9 0.7 2.5 0.75

RTAA 100 200/60 1 483 600 600 2 192 - 192 990 - 990 10 1.0 5.1 0.75230/60 1 426 500 500 2 167 - 167 820 - 820 10 1.0 5.0 0.75380/60 1 259 350 300 2 101 - 101 497 - 497 10 1.0 3.2 0.75460/60 1 214 250 250 2 84 - 84 410 - 410 10 1.0 2.5 0.75575/60 1 173 225 200 2 67 - 67 328 - 328 10 1.0 2.2 0.75380/50 1 223 250 250 2 88 - 88 382 - 382 10 0.7 2.5 0.75400/50 1 214 250 250 2 84 - 84 402 - 402 10 0.7 2.5 0.75415/50 1 208 250 250 2 81 - 81 417 - 417 10 0.7 2.5 0.75

RTAA 110 200/60 1 535 700 600 2 233 - 192 1190 - 990 10 1.0 5.1 0.75230/60 1 471 600 600 2 203 - 167 1044 - 820 10 1.0 5.0 0.75380/60 1 287 400 350 2 123 - 101 632 - 497 10 1.0 3.2 0.75460/60 1 235 300 300 2 101 - 84 522 - 410 10 1.0 2.5 0.75575/60 1 191 250 225 2 81 - 67 420 - 328 10 1.0 2.2 0.75380/50 1 245 300 300 2 106 - 88 487 - 382 10 0.7 2.5 0.75400/50 1 236 300 300 2 101 - 84 512 - 402 10 0.7 2.5 0.75415/50 1 228 300 300 2 97 - 81 531 - 417 10 0.7 2.5 0.75

RTAA 125 200/60 1 576 800 700 2 233 - 233 1190 - 1190 10 1.0 5.1 0.75230/60 1 507 700 600 2 203 - 203 1044 - 1044 10 1.0 5.0 0.75380/60 1 309 400 350 2 123 - 123 632 - 632 10 1.0 3.2 0.75460/60 1 253 350 300 2 101 - 101 522 - 522 10 1.0 2.5 0.75575/60 1 205 250 225 2 81 - 81 420 - 420 10 1.0 2.2 0.75380/50 1 264 350 300 2 106 - 106 487 - 487 10 0.7 2.5 0.75400/50 1 253 350 300 2 101 - 101 512 - 512 10 0.7 2.5 0.75415/50 1 244 350 300 2 97 - 97 531 - 531 10 0.7 2.5 0.75

Notes:1. As standard, all 70-215 ton units require a single point power connection.2. Max Fuse or HACR type breaker = 225 percent of the largest compressor RLA plus 100 percent of the second compressor RLA, plus the sum of the condenser fan

FLA per NEC 440-22. Use FLA per circuit, NOT FLA for the entire unit).3. MCA - Minimum Circuit Ampacity - 125 percent of largest compressor RLA plus 100 percent of the second compressor RLA plus the sum of the condenser fans

FLAs per NEC 440-33.4. RECOMMENDED TIME DELAY OR DUAL ELEMENT (RDE) FUSE SIZE: 150 percent of the largest compressor RLA plus 100 percent of the second compressor RLA

and the sum of the condenser fan FLAs.5. RLA - Rated Load Amps - rated in accordance with UL Standard 1995.6. Local codes may take precedence.7. Control kW includes operational controls only. Does not include evaporator heat tape.8. LRA - Locked Rotor Amps - based on full winding (x-line) start units. LRA for wye-delta starters is 1/3 of LRA of x-line units.9. VOLTAGE UTILIZATION RANGE:

Rated Voltage Utilization Range200 180-220230 208-254380 342-418460 414-506575 516-633

10. A 115/60/1, 15 amp customer provided power connection is required to operate the unit controls. Aseparate 115/60/1, 15 amp customer provided power connection is also needed to power the evaporatorheat tape (420 watts @ 120 volts). If the optional control power transformer is used, the customer needsonly to provide a power connection for the evaporator heat tape.

11. If factory circuit breakers are supplied with the chiller, then these values represent Maximum OvercurrentProtection (MOP).



Appendix L - NEC Table 430.150 and 430-52

Documents

Tubman African American Museum · Project Info: - Atlanta, GA - 45,000 Sq. Ft.-Two stories - Museum Structural:-Steel construction with composite metal deck-Fabricated curved steel