HomeMy WebLinkAboutSiemens IGAAPPENDIX C
ASLC INVESTMENT GRADE ENERGY AUDIT
SIEMENS INDUSTRY, INC.
BUILDING TECHNOLOGIES DIVISION
ASLC Heat Recovery Project
AEA Renewable Energy Fund Round VII Application
Alaskp SeaLife Cent
Detailed Investment Grade Audit & Energy Services Proposal
June 2011
a; Siemens Industry, Inc.
Building Technologies Division -MEN S
Alaska Seatife Center
DETAILED INVEST"v1ENT GRADE AUDIT
& ENERGY SERVICES PROPOSAL
Detailed Investment Grade Audit &
Energy Services Proposal
PREPARED FOR:
Phillip Oates
City Manager
City of Seward
401 Adams Street
Seward, AK 99664
ON BEHALF OF:
Ian Dutton, Ph.D.
President & CEO
Alaska Seatife Center
301 Railway Ave
Seward, AK 99664
DEVELOPED BY:
Siren-s Irpdust-ry; f c.
Building Technologies Division
5333 Fairbanks Street, Suite B
Anchorage, AK 99518
(907) 563-2242
PRIMARY CONTACT:
Amber M. McDonough, P.E.
Energy & Environmental Solutions
Siemens Industry, Inc.
amber.mcdonough@siemens.com
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Table of Contents
Tableof Contents.......................................................................................... - 2-
Acknowledgements....................................................................................... - 4-
Section I - Executive Summary...................................................................... - 5-
Section II - Facility Description...................................................................... 9-
Lighting.................................................................................................................- 9-
WaterDescription................................................................................................. 11 -
Boilers.................................................................................................................- 12 -
SeaWater Heat Pumps.........................................................................................- 15 -
SlabHeating....................................................................................................... 19 -
AHU-1...................................................................................................................21 -
AHU-2................................................................................................................... 24 -
AHU-3.................................................................................................................. - 26 -
AHU-4.................................................................................................................. - 31 -
AHU-5. 1 -35-
AHU-6................................................................................................................... 38 -
AHU-7..... ,.............................................................................. -
AHU-8..................................................................................................................- 44 -
AHU-9............................................................ _..................................................... 47 -
LifeSupport System............................................................................................. 49 -
Section III — Facility Improvement Measures ..............................................- 52 -
FIM 1.00 Lighting Upgrades.............................................................................- 52 -
FIM 1.01 Lighting Controls................................................................................ 54 -
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FIM 2.00 Water Conservation................................................................................ 56 -
FIM 4.00 Building Automation System Upgrade ............................................... 57 -
FIM 4.03 Night Setback Control.......................................................................- 60 -
FIM 4.04 Demand Control Ventilation............................................................... 63 -
FIM 4.06 Slab Heat Control Optimization......................................................... 65 -
FIMs Considered for Recommendation but Excluded .............................................. 67 -
Section IV — Measurement and Verification ............................................... - 68 -
Measurement and Verification Options................................................................. 68 -
Measurement and Verification Plan...................................................................... 69 -
Option -A — Measured Capacity........................................................................- 69 -
Option-B — Measured Consumption.................................................................. 72 -
Appendix I — Methodology / Utility Summary .............................................- 76 -
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Acknowledgements
SIEMENS
Siemens Industry, Inc. would like to recognize the time and effort of several Alaska
Sea Life Center employees who have facilitated the site research necessary to
complete this energy audit and the footwork required to develop an energy savings
performance contract. Most notably, the support we received from Ian Dutton,
Ph.D., Steve Carrick, and Darryl Schaefermeyer was crucial to the development of
this project. We look forward to continuing our mutual efforts to increase the
Center's energy efficiency and reduce its annual utility expenditures.
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Section I - Executive Summary
Background
On October 20, 2009 the Alaska Sea Life Center (ASLC) signed a Letter of Intent (LOI) with
Siemens Industry, Inc. Building Technologies Division (SIEMENS), an Energy Services
Company (ESCO), to perform a Detailed Investment Grade Audit (IGA) with the intent of
developing an Energy Savings Performance Contract (ESPC) Agreement. The following
report documents the results of the energy study of the ASLC and provides the basis for
the final development of an ESPC project.
Program Objective
The objective of this evaluation was to identify and analyze the operations of the ASLC
and to identify Facility Improvement Measures (FIMs) that will combine to form a project
that meets the requirements of the LOI. The intent was to focus on energy efficiency
improvements with favorable paybacks, whereby capital improvements will be funded by
energy and operational cost savings.
Facilities Included in the Audit
Table 1 lists the characteristics of the facility included in the audit. Occupancy shown
indicates the maximum seasonal number of visitors expected per hour.
Table 1
Facilities Included in the Technical Enerav Audit
Facility
Area (sq. ft.)
StaffNisitors Occupancy
Summer
Winter
Alaska Sea Life Center
1 106,290
761220
76125
Summary of Fad ty imlar auement mea-sures 4FIMs
Table 2 provides a summary of the proposed FIMs as well as the associated energy
savings. These FIMs include lighting retrofits and lighting controls integration, water
conservation, and an automation system upgrade including required motor starter
replacements.
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Table 2
Pronosed FIM Summary
Electrical
Electrical
Water/
Consumption
Demand
Fuel Oil
Sewer
Energy
Total
Savings
Savings
Savings
Savings
Operations
Savings
Savings
FIM #
FIM Description
Facility (kWh)
(kW)
(al)
(aq
Savin s ($)
Value ($)
Value ($)
1.00
Liahtina Retrofit
Facility wide
66,995
51
$3,500
$4,963
$8,463
1.01
Licihtinci Controls
Facility wide
23,941
-
-
$1,559
$1,559
2.00
Water Conservation
Facility wide
456,000
$2,945
82,945
4.00
DDC Installation
-
-
$46,911
$46,911
-Demand
Control
AHU-5, AHU-6
252,892
Ventilation
Rooms 146,
147, 145, 143,
Night Setback
144, 152, 155,
Control
156, 157, 158,
65,892
70
159, 141, 162,
163, 201, 222
Slab Heat
Control
Slab Heat
389,237
-
-
Optimization
Total I
1
1
798,956 1
122 1
1
456,000 1
$3,500
$56,378
$59,878
Pathway to Implementation
The total cost to perform this work is summarized below. This incorporates the costs
associated with the project's development, energy audit, and measurement & verification
(M&V) set-up required during the first year for the project guarantee.
ASLC Energy Project Implementation Cost = $809,876
Total Annual Energy Savings Value (Year 1) = $59,878
Simple Payback =13.5 years
This beneficial project is designed to reduce the ASLC's overall energy consumption and
year-to-year utility expenditures and meet the stated 15-year cash flow criteria of the LOI.
The Total Annual Energy Savings is based on anticipated first year energy unit costs.
Siemens guarantees units of energy, not the commodity cost of energy, so these savings
may fluctuate some based on the actual cost of energy in a given year. In general, the
cost of energy increases over time and energy escalation is taken into account in most
performance contracting cash flow scenarios.
Previous discussions with the ASLC identified the following factors should be considered
and incorporated to accurately represent the calculated energy savings over time:
Energy Savings Captured During Construction (Year 0) = $4,794
Annual Energy Savings Escalation = 5%
Annual Operation Savings Escalation = 3%
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Project Challenges
The development of this project has been challenging on multiple fronts. The on -going
proactive measures by ASLC's staff to reduce energy consumption and the future
installation of the sea water heat pumps have captured some of the energy savings
potential identified during Siemens initial site evaluations. In addition, minimum
consumption thresholds negotiated with local utility companies prevent the
incorporation of extra demand -based savings created by installing the project FIMs.
However, despite these challenges, the primary barrier to implementing this energy
project has been securing project funding. Without funding, Siemens is unable to
provide a complete ESPC Agreement. Throughout the past year the ASLC and Siemens
have attempted to secure project financing numerous times in a variety of ways.
Funding avenues jointly evaluated, but ruled out include:
• Traditional Lenders — First National Bank of Alaska and Wells Fargo
• Siemens Financial Services (SFS)— via Siemens Building Technologies & SFS direct
• USDA Community Facilities Grants & Direct Loans
• Federal grant funding via Legislative Insert
• State grant funding leveraging regional Representatives in Juneau
• American Recovery and Reinvestment Act (ARRA)
• Rasmuson Foundation Support
• Bonding options available via the City of Seward
• Loans available if the City of Seward would share the ASLCs debit obligation
The best remaining option for funding this project appears to be the State of Alaska's new
$250M Alaska Energy Efficiency Revolving Loan Fund (AEERLF) that is administered by
the Alaska Housing Finance Corporation (AHFC). The AEERLF is designed to help public
entities perform energy efficiency improvements to help reduce energy consumption
Statewide by 15% before 2025. Money from the fund is distributed by the Retrofit
Enexgy-Assessri�ent-#or-Loam{}R€M} ran. This pregiatttfequimt-he Pity -of
Seward (City), as the owner of the ASLC facility, to apply for the REAL loan to implement
the energy improvement measures described by this IGA.
Use of the AEERLF involves meeting the criteria of AHFC's REAL Manual. The Manual
details the following steps to request a loan for energy performance contracts with
guaranteed energy savings:
1) Submission of REAL Application & Preliminary Benchmarking Form to AHFC
2) Qualified ESCO (SIEMENS) prepares Investment Grade Audit (IGA)
3) Submission of IGA and Loan Application to AHFC
This document would serve as the required IGA for this loan application. The State
program requires that the energy project cash flow neutrally within 15 years and must
also include a minimum three (3) year performance guarantee.
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The annual cost for SIEMENS performance assurance service, also known as a
measurement and verification plan (M&VP), with annual labor escalations is estimated to
as follows:
Year 1 = $15,492 + Year 2 = $16,035 + Year 3 = $16,595 for a Total 3-Year Energy
Guarantee with M&V = $48,122
This performance assurance is required for every year in which the savings are to be
guaranteed by Siemens. It includes measurement and verification time for Siemens
engineers to confirm energy savings and prepare an annual report. These costs would
need to be added to the ASLC Energy Project Implementation Cost shown above to
support the REAL program requirements.
Siemens is willing to work with the City, ASLC, and AHFC to help draft up different cash
flow scenarios once a project interest rate has been established. If possible, we hope to
be able to help the City negotiate the most favorable payment schedule and terms. As
soon as funding is secured, Siemens will be able to finalize and propose a complete
Energy Savings Performance Contract (ESPC) Agreement.
The ESPC Agreement requires that interest rates be established in order to structure a
payment schedule that will cash flow neutrally for the term of the contract. Siemens
remains committed to the ASLC and supporting this project to the point that it can be
proposed and implemented as an ESPC Agreement.
Optional Building Automation Support
Depending on the final terms of the ASLC's Performance Contracting Agreement with
Siemens, an annual support agreement for the new Building Automation System (BAS)
may be provided. The reoccurring cost of this service will not be included in the total
sum financed to perform this energy project. Instead, energy savings will be used to pay
for this service directly. After the cost of BAS service program has been deducted, the
remaining annual energy savings will be applied to repay to the loan. Loan payment will
be scheduled to account for this payment structure.
This annual service agreement is designed to support ASLC's operation of their new
Siemens APOGEE automation system. This is to provide both remote and on -site
operator support with technician travel for a full day in Seward:
Building Automation System Service (Year 1) = $4,925
Annual BAS Service Agreement Escalation = 3%
In addition, software and firmware updates are included every other year to keep the
ASLC's system current and prevent a future obsolescence of the new building automation
system. This increases the annual cost of the service agreement every other year to:
Building Automation System Service (Year 2) = $8,974
Annual BAS Service Agreement Escalation = 3%
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r Alaska_ Seal-ife Center DETAILED INVESTMENT GRADE AUDIT SIEMENS
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Section II - Facility Description
Lighting
General
The Alaska SeaLife Center building is of relatively new construction and has a typical
modern lighting system comprised of 1,735 fixtures. Space types at the facility consist of
laboratories and related research support spaces, animal research, quarantine areas,
administrative areas, and exhibit galleries '
for public visitation. For the purposes of the
lighting analysis, the building consists of I
three types of spaces: Offices, Laboratories
and Public Gallery/Display Areas. The Office
and Laboratories are almost exclusively first
generation T8 fluorescent fixtures with
electronic ballasts. Many of these fixtures
are vapor tight and suspended
Direct/indirect models (Figure 1).
Figure 1 Office Lamps
The Public Gallery/Display Areas use different types of lightings. The Aquarium and
SeaLife Display Areas utilize a number of specialized High Intensity Discharge (HID)
fixtures, such as actinic lamps, which are not slated for retrofit due to the sensitive,
unique lighting requirements of each aquarium environment (Figure 2).
� f
Figure 2 Aquarium and SeaLife Display Areas
The rest of these Public Gallery/Display Areas utilize a large number of incandescent and
compact fluorescent tracks and can lighting to illuminate informational and educational
wall displays (Figure 3).
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Figure 3 Public Gallery/Display Areas
The exterior lighting consists of 150 W and 400 W Metal Halide fixtures and 70 W and
1000 W High Pressure Sodium fixtures (Figure 4).
Figure 4 Exterior Lighting
Current operation of the lights is provided by the Triatek lighting control system (Figure
5)-
i
Figure 5 Triatek Lighting Control System
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Lighting Baseline Development
On February 9, 2010 and February 10, 2010 a team from SIEMENS and Sylvania Lighting
Services conducted an energy survey and audit of the Alaska SeaLife Center to evaluate
existing lighting systems. Baseline energy use for lighting was calculated based on
existing lamps, ballasts, fixtures, lighting control systems, power measurements, and
data collected from Watt Stopper data loggers. Upgrading the lighting system to reduce
energy consumption will occur in two ways; the first reduction is to reduce the lighting
system's input wattage and the second reduction is to reduce the hours of operation.
Water Description
General
The Alaska SeaLife Center water fixtures such as water closets, urinals, and lavatories are
not low volume, low flow devices. Presently the water closets require 3.5 gallons of
water per flush and the lavatories have a flow rate of 1 gallon per minute.
Water conservation efforts will help to contain the impact of future rate increases, yield
utility savings on water supply and sewer charges, and reduce maintenance effort and
costs associated with older domestic and sanitary water fixtures.
On -site surveys indicated that the toilets currently installed at the Alaska SeaLife Center
were installed during the original construction. Areas that have been targeted to reduce
water consumption in these facilities include the following.
r Water cis in both pube -arts} private -areas that utilize -OtdeT, -fu-s'll
fixtures. These fixtures utilize 3.5 gallons per flush (gpf) as compared to the
newer low flush technology that utilizes 1.6 gpf. Although some of the early
versions of the low flush technology installed in the 1990s gained a poor
reputation for failing to clear the bowl with a single flush, more recent
versions of low flush technology operate as well as the high flush fixtures.
Existing lavatories utilize 1.0 gallons per minute (gpm) as compared to the
newer technologies that utilize 0.5 gpm.
Water Baseline Development
The baseline water usage in gallons is modeled using data collected during the site
survey and discussions with Alaska SeaLife Center personnel. The baseline calculation is
shown by Equation 1.
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Equation 1
WaterUse = (3.5gallons 200,000 flushes) + (Igallons)(
year 2 J
Boilers
400,000washes _ 900,000gallonsl year
year
General
The Boiler Plant houses the three boilers used at the Alaska SeaLife Center (Figure 6).
Boilers #1 and #2 are fuel oil boilers, and Boiler #3 is an electric boiler. The Boiler Plant is
located in the basement and provides hot water for the space heating, slab heating, and
domestic hot water.
r~_ a%■ I I
Figure 6 Boiler Room
Occupancy
The bokrs operate year retmd as needed to meet th-e heat toad.-Fue#-oif-is-�rom
October thru the end of April, at which point the electric boiler is used. The system
operates 24 hours a day, 7 days a week.
Boiler#1 and #2
Boilers 1 and 2 are 80 hp, Cleaver Brooks, fire tube, hot water boilers. They have a rated
input of 3,347,000 btuh and a max pressure of 30 psi. The boilers operate in a lead lag
fashion based on boiler run time and/or alarm status.
Boiler #3
Boiler 3 is a 500 kW, Sussman, electric, hot water boiler. It is rated at 480 volts, 60 Hz,
and 602 Amps. It operates as a swing boiler with primary use occurring during the
summer months. With the installation of the Sea Water Heat Pumps the intention of the
site is to use the Electric Boiler as the primary heat source year round. Adjustments to the
energy model indicate this plan in operation.
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Pumping
Circulation for the boiler loop is provided by pumps PMP-18&19. The pumps are constant
volume at a flow of 340 gpm, with a pressure drop of 40 feet of head. The motors have a
brake horse power of 5.25 bhp. An electrical load was calculated at 4.61 W.
Boiler Baseline Development
In order to obtain the baseline energy use for the Boilers, measurements were taken on
the points in Table 3. The data was obtained on 15-minute intervals between December
12th, 2009 and January 4th, 2010. The measured data was used to calculate the
correlation between the load (MBH) and outside air temperature and time of the day.
Table 3
List of Trended Variables, Boilers
Measurement Location
Units
Outside air temperature
Temp °
Retum water temperature
Temp
Supply water temperature
Temp °
The electric load from Boilers comes from the electric boiler and the constant volume
circulation pumps. The electric load for the pumps was calculated using the provided
pump curves and Equation 2.
Equation 2
FLkW bhp x 0.746
P'"''�O1Vef MotonEfficiency
The pump power was calculated to be a constant 4.61 kW.
The heating coil load (Btuh) was calculated using Equation 3.
Equation 3
Load Boders = 500 x WQterFlowBoik rs X (TSupplylVarer — TR..K orc r )
The calculated load for the boilers was plotted against outside air temperature for the
corresponding 15 minute trend interval. A linear equation was used to fit to the resulting
plot. The load is illustrated in Figure 7.
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Boller Load (Btuh)
4,000,000
3,200,000 • �, •.
d 2,400,000 Logx-
y=-36C-•06 __ — • • �e f���-••�+,.--.-ram-
= 1,800,000
e'
800,000
0
6 10 16 20 26 30 36 40 46 50
OAT I
Figure 7 Boiler Heat Load vs Outside Air Temperature
The resulting heat load profile as a function of outdoor air temperature is illustrated in
Equation 4.
Equation 4
LoadBo;j,,s = —3 5,709 x To„.,u,r + 3,277,828
A combustion efficiency test was performed on Boiler #2 at loadings of 30%, 60%, and
90%. Figure 8 present the results of the boiler combustion efficiency test.
94 ..—.
Boiler # 2 (# 2 Oil)
a Combustion efficiency ■ % Oxygen
- Poly. (Combustion efficiency) ••. Poly. (% Oxygen)
y=�,33 +10.167x+3A
R2=1
y = 7.777Bx2 -11 x + 92.3
=1
60% 901i
A Boiler loading
10
7.5
. 2
2.5 m
0
e
0 e
to
45
.5
t 45
•10
120%
Figure 8 Results of the Combustion Efficiency Test for Boiler #2
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A quadratic function was fit to the results for the combustion test to give an equation for
the efficiency of the boiler at varied loadings (Equation 5). This equation was then used
to determine the central plant efficiency at the varied hourly loads during the analysis.
Equation 5
Efftciencyeor,e1S = 7.7778 x %Load�;,e1S —11 x %Loadeoi1e1S + 92.3
A quadratic function was fit to the results for the percent oxygen in the exhaust at varied
loadings (Equation 6).
Equation 6
Percent0xygenBo;1@rs =—8.3333 x %Load Boi2 ,ors + 10.167 x %Load Bo,,,,s + 3.4
Sea Water Heat Pumps
General
Two new Sea Water Heat Pumps are being installed to provide pre -heat to the following
Air Handling Units (AHU): 1, 2, 4, 5, and 6, as well as to take care of the load from the
Domestic Hot Water (DHW) (Figure 9). To account for the new system additions a
baseline adjustment was made to the energy model after it was matched to the current
utility consumption to account for the load shift. The design documentation provided
was somewhat limited so certain assumptions had to be made when modeling the future
energy use of the equipment, those assumptions are outlined below.
Sf 'N-Y.*
SEA w*M R-
Figure 9 New Sea Water Heat Pumps and Existing Sea Water Cooling
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Information provided by Alaska Sea Life Center indicates that the new Sea Water Heat
Pumps will be piped in a manner so as to provide hot water at 120'F to the existing
Cooling Coils as a means to provide pre -heat to the AHUs without disrupting the existing
Heating Coils. A set of valves will reroute the water to either provide cooling or heating
as is required by the units. All AHUs on the Sea Water Heat Pump loop will receive either
hot water or cooled water depending on whether the AHUs are calling for heating or
cooling. The provide sequence of operation indicates that the Sea Water Heat Pumps will
be enabled when the Outside Air Temperature is less then 55°F.
Occupancy
The heat pumps will operate year round as needed to meet the pre -heat load. It is
assumed that both heat pumps will be operational when the fuel oil boilers are
operational and that only one heat pump will operate when the electric boiler is
operational. The system will operate 24 hours a day, 7 days a week. During the times
when only one heat pump operates the system will function in a lead/lag control strategy
so as to keep equal wear on both pieces of equipment. Direction provided by Alaska
SeaLife Center is that the Fuel Oil Boilers will not be enabled unless the Electric Boiler
along with the Sea Water Heat Pumps can not meet the load requirements of the facility.
Heat Pump #1 and #2
Heat pump 1 and 2 are 90 ton, Trane, RTWD Series R, high efficiency, water cooled, 2
pass, helical rotary chillers. They have a rated output capacity of 1,080,000 btuh. Design
for the evaporator is entering fluid temperature of 35°F, leaving fluid temperature of
27°F, and flow rate of 180 gpm. Design for the condenser is entering fluid temperature
of 90°F, leaving fluid temperature of 120°F, and flow rate of 120 gpm. From the
manufacturer's data for a high efficiency chiller, the evaporator has a rated minimum
flow rate of 92 gpm and a rated maximum flow rate of 336 gpm. Likewise the condenser
has a rated minimum flow rate 95 gpm and a maximum flow rate of 347 gpm.
Pumping
PMP-19820 and PMP-21 &22 are the new circulation pumps for the evaporator and
condenser side of the Sea Water Heat Pumps. The pumps are controlled in Lead/Lag
configuration with flow modulated using Variable Frequency Drives (VFD). The
evaporator pumps are variable volume flow with a max rated flow rate of 360 gpm, with
a pressure drop of 50 feet of head. The motors have a rated horse power of 7.5 hp. The
condenser pumps are variable volume flow with a max rated flow rate of 240 gpm, with
a pressure drop of 40 feet of head. The motors have a rated horse power of 5 hp.
Heat Exchangers
New heat exchangers are being installed for the heat transfer between the sea water and
the evaporator loop: HX-3 for the condenser loop and HX-4 for the Domestic Hot Water
loop. The information provided detailing the possible system design indicates that a set
of heat exchangers may also be installed to recover heat from the exhaust streams of
several of the fan systems. This heat recovery would be use to pre -heat the fluid entering
the evaporator of the heat pumps. HX-3 has a design capacity of 1,380 MBH with a Hot
Side entering fluid temperature of 37°F, exiting fluid temperature of 33'F, and a fluid
flow of 700 gpm; and a Cold Side entering fluid temperature of 27`F, exiting fluid
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temperature of 35°F, and a fluid flow of 360 gpm. HX-4 has a design capacity of 420
MBH with a Hot Side entering fluid temperature of 1207, exiting fluid temperature of
1007, and a fluid flow of 42.8 gpm; and a Cold Side entering fluid temperature of 407,
exiting fluid temperature of 1107, and a fluid flow of 12 gpm.
Sea Water Heat Pumps Baseline Development
In order to obtain the baseline energy use for the Sea Water Heat Pumps, design
documents provided by the Alaska Seal-ife Center and manufacturer's specifications were
consulted. The load profiles developed for all AHUs and the DHW were summed together
to develop the load on the new Sea Water Heat Pumps. Baseline Development for each
AHU and DHW can be found in appropriate sections below.
The electric load comes from the evaporator loop pumps, condenser loop pumps, and the
chillers. The maximum electric loads for the pumps were calculated using the
manufacturer's pump curves from the design data and Equation 7. Motor Efficiency was
taken from EPACT 92 for enclosed motors at 1800 RPM based on the design motor horse
power.
Equation 7
FLkW _ bhp x 0.746
P�on�aPower —
MotorEfficiency
The maximum evaporator loop pump power was calculated to be 4.85 kW.
The maximum condenser loop pump power was calculated to be 2.84 kW.
To calculate the pumping energy that would be used with the varying flow of the loops, a
linear relationship was assumed between the percent of loop flow and percent of load on
the chltr�quai`1on n every case, the calculated fluid flow was checked to make
sure that it met the minimum and maximum flow requirements for the chiller. If the
flows were less or greater than the manufacturer's specified flow rates, the value used in
the calculation was set to the manufacturer's flow rates.
Equation 8
FluidFlow = %ChillerLoad x MaximumFluidFlow
Based on observed behavior, the system should behave somewhat differently than this
because the Temperature Differential across the Heat Exchangers and the Chillers tends
to vary from the design during part load conditions. For the purpose of the baseline
adjustment this was not considered because the electrical use associated with the pumps
is minimal when compared to the total loads of the facility.
The total heating load (Btuh) was calculated by summing the calculated loads for the
AHUs and DHW. See appropriate sections below for cletails-
Siemens Industry, Inc. _ - 17 - Proprietary & Confidential
June 2011
Alaska Sea Life Center
-- - -- -
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Using the manufacturer's Maximum Capacity for the chillers and the summed loads, a
percentage load was calculated (Equation 9). Using the assumptions for the number of
chillers that were operational, either the chiller load was capped at the maximum
capacity or it was split between both units.
Equation 9
PercentLoad
AHULoad + DHWLoad
=
MaximumChillerLoad
Using the manufacturer's data for the part load efficiency of the chiller, a curve was
plotted for the kW/ton at varying load, Figure 10.
Part Load Performance
0.8 -
0.7
0.6
0.5 +
OA -
0.3
0.2
0.1
0
0
a kW/ton— Poiy. (kW/ton)
y= 8 520E-01 x2 - 8 854E-0tx+ 7.162E-01
R2 = 9 580E-01
0.2 0.4 0.6 OA
Load (°k)
Figure 10 Chiller Efficiency Curve
1 1.2
The percent load was then used to calculate the chiller electrical consumption. A sum of
the pumps and chiller electricity was done and this load was then shifted from the boilers
creating the modified baseline. A plot of the new Sea Water Heat Pump versus the
Outside Air Temperature for each hour of the analysis is shown in Figure 1 L
Sea Water Heat Pump System Load Profile
80.00 r
x70.00 1 ® Heat Pump System Power Load, kW
60.00 I --
m
li0.00 -6.-
b 40.00
1 30.00 +
w
a 20.00-
10.00 -----
to
0.00 ----
-10 0 10 20 30 40 60 60 70 80 90
Outside Air Temperature, F
Siemens Industry, Inc.
June 2011
Figure 11 Sea Water Heat Pump System Load Profile
Proprietary & Confidential
Alaska Sea Life Center
Slab Heating
DETAILED INVESTMENT GRADE AUDIT Sir
& ENERGY SERVICES PROPOSAL
General
A portion of the exterior concrete slabs that are located by the different pools are heated
by a hot water loop that is located in the slab. The purpose of the loop is to keep the
slabs from becoming slick from snow or ice. Flow through the loop is provided by a pair
of lead -lag constant volume pumps. The loop is conditioned by the central plant through
a shell and tube heat exchanger. Control to enable and disable the system is provided
manually.
Occupancy
The slab heat is manually enabled when the facility determines that the exterior
conditions require it. Once enabled the system operates 24 hours a day, 7 days a week
until disabled.
Heating
Heat is provided by a shell and tube heat exchanger that is rated at a heat transfer
capacity of 1,204 MBH with 200OF GWS, 170OF GWR, 120OF RHS, 90OF RHR, and both
fluids consisting of 40% Propylene Glycol. There are 31 different loops that are served by
the heat exchanger. Table 4 shows the loop lengths and rated flows.
Table 4
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June 201
Alaska Sea Life Center DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Pumping
Circulation for the slab heating loop is provided by a lead lag pair of pumps. The pumps
are constant volume at a flow of 90 gpm, with a pressure drop of 70 feet of head. The
motors are rated at 3 hp, 460 volts, and 3 phase. A brake horsepower was calculated at
2.273 bhp and an electrical load of 1.99 W.
Slab Heating Baseline Development
In order to obtain the baseline energy use for the slab heat, measurements were taken
on the points in Table 5. The data was obtained on 15-minute intervals between
December 12th, 2009 and January 4th, 2010. The measured data was used to calculate
the correlation between the load (M13H) and outside air temperature and time of the day.
Table 5
List of Trended Variables, Slab Heat
Measurement Location
Units
Outside air temperature
Temp °
Retum water temperature
Temp °
Supply water temperature
Temp °
The electric load from slab heating comes from the constant volume pump. The electric
load for the pump was calculated using Equation 10 and Equation 11.
The brake horsepower, bhp was calculated for the pump using information from the
mechanical schedules and Equation 10.
Equation 10
_ WaterFlow x Pr essureDrop
--- bhp PumpF_ ci ency x 3960
Full load power was then calculated by using the motor efficiency, see Equation 1,1.
Equation 11
FLkW _ bhp x 0.746
P'°"''�°"e' — MotorEfciency
The pump power was calculated to be a constant 1.99 W.
The slab heating load (Btuh) was calculated using Equation 12. The heat capacity of the
loop was de -rated.
Equation 12
Load Sla6Hc.l = 464.72 x WaterFlow Sta6Heat x (Tsupplyff akr — TRtnirnff'aw )
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June 2011
Alaska Sea Life Center
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
The calculated load for slab heat was plotted against outside air temperature for the
corresponding 15 minute trend interval. A quadratic equation was used to fit to the
resulting plot. The load to the central plant from slab heat is illustrated in Figure 12.
Slab Heat Load (Btuh)
600,000
I
660,000
r
•P...A..rrS
m 520, 000
411— Ole
460,000
y =-102.0330 + 3948.5x + 491790
61�� 1
=
Rz=0567
,
440,000
400,000
5 10 16 20 25 30 36 40 45 60
OAT 'F
Figure 12 Slab Heat Load to Central Plant
The resulting slab heat load profile as a function of outdoor air temperature is illustrated
in Equation 13.
Equation 13
Load slabHeat =—102.03 x T';.s;de fir — 3,848.5 x To„cslde.lrr + 491,790
AHU-1
General
AHU-1 is a 100% outside air, constant volume,
single duct system manufactured by TRANEo. The
unit is located above AHU-2A and AHU-213 in the
North Penthouse. AHU-1 serves the 1st floor
Surgical Suite, which includes rooms 140, 145, 146,
147, 149, and 150, where additional zone heating
is provided by reheat coils, HC-6, HC-7, and HC-8.
AHU-1 is served by one supply fan, one exhaust fan,
one heating coil, one cooling coil, and one
humidifier. AHU-1 operates continuously.
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June 2011
0 Alaska Sea Life Center
DETAILED INVESTMENT GRADE AUDIT S'
& ENERGY SERVICES PROPOSAL
EF•1
CV - 2410 cfm
................s O ■
...
pHU t
.0
---
Supply Fan
CV -2410 con
CC-1 HC-At
sroyr �r
.ro.rr�n
Figure 13 AHU-1
First Floor Levy
Rm 147
HC-7
F&at Fbor Levu
Rm •46
HC-8
IIriII-11iiII-1Ii71L��� F rst Floor lave
LLWJ Mrs
140 '45.
•50
HC-8
Occupancy
AHU-1 operates 24 hours a day 7 days a week. The Surgical Suite is occupied by the staff
members and animals.
Heating
Space heating is provided by a heating coil, HC-Al located in AHU-1, and additional zone
heating is provided by reheat coils, HC-6, HC-7, and HC-8 located at individual zones. HC-
A1 has rated heating capacity of 144MBH at the design airflow of 2,410 cfm. HC-6, HC-7,
and HC-8 each have rated heating capacity of 8.1 MBH, 21.6MBH, and 35.4MBH
respectively. Each coil is served by glycol hydronic loop system. HC-Al heating valve
modulates to maintain the supply air temperature at 55°F.
Cooling
Space cooling is provided by a cooling coil, CC-1 located in AHU-1. CC-1 has rated cooling
capacity of 36.1 MBH. CC-1 cooling valve modulates to maintain the supply air
temperature at 55°F. Heating and cooling coil valves modulate in sequence.
Ventilation
AHU-1 serves Surgical Suite and supplies 100% outside air at constant volume of 2,410
cfm at all time. Ventilation is provided by one supply fan, and one exhaust fan, EF-1. The
supply fan located in AHU-1 has a rated capacity of 2,410 cfm, a rated motor power of 3
hp, and fan operating speed of 2,039 rpm. Exhaust fan, EF-1 is located on the rooftop
near the north penthouse. EF-1 has a rated capacity of 2,410 cfm, a rated motor power
of 1 hp, and fan operating speed of 1,280 rpm. Exhaust fan operation is interlocked to
run simultaneously with AHU-1.
Humidifier
Humidification of the supply air is provided by a humidifier, HU-1. Currently HU-1 is set
be not operational because it has been disabled through the existing building automation
system. HU-1 has a rated capacity of 90 Ibslhr. The operation of HU-1 is interlocked with
the airflow switch provided with the humidifier. When operational, HU-1 modulates to
Siemens Industry, Inc. 22 _ Proprietary & Confidential
June 2011
Alaska Sea Life Cent_ DETAILED INVESTMENT GRADE AUDIT 3,..
& ENERGY SERVICES PROPOSAL S' EM EIS
maintain the space humidity set point of 45% Relative Humidity according to the system
design.
AHU-1 Baseline Development
Baseline heating energy consumption for AHU-1 was calculated based on the measured
outside air temperature, outside air relative humidity, and the operating specifications.
The data was obtained on 15-minute intervals between December 12th, 2009 and
January 4th, 2010. Heating coil heating load was calculated based on the outside air
temperature, supply air temperature of 55°F, and supply airflow of 2,410 cfm (Equation
14). Heating load (Btuh) versus outside air temperature profile was created to calculate
the annual heating energy consumption by the unit (Figure 14 and Equation 15).
Equation 14
HCA1Load =1.08 x SupplyAirflow,Ht,l x (TSappl)Air—TowsaeA,r)
120,000
100,000
m 80,000
dy
3 60'0W
i 40,000
20,000
0
AHU•1 Heat load (Stuh(
10 15 20 25 30 35 40 45 50 55 60
OAT;F
Figure 14 AHU-1 HC-Al Heating Load Profile
Equation TS
HCA1Load = —2,528 x To,„ nd,,, + 140,726
The electric load of supply and exhaust fans were calculated as follows; the brake horse
power, bhp was calculated for the each of the fans using the mechanical schedules and
Equation 16 .
Equation 16
MaxAirflow x Pr essureDrop
bhp = FanEfftciency x 6356
Full load power was calculated by using the motor efficiency (Equation 17).
Siemens Industry, Inc.
June 2011
- 23 - Proprietary & Confidential
0 Alaska Sea Life Center
DETAILED INVESTMENT GRADE AUDIT
& ENERGY SERVICES PROPOSAL
Equation 17
FLkW = bhp x 0.746
MotorEfficiency
SIENIFMr-
Supply fan and exhaust fan consume constant electrical load of 1.63 kW and 0.57 kW,
respectively.
AHU-2
General
AHU-2A and AHU-26 are 100% outside air, constant volume, single duct system
manufactured by TRANE@. AHU-2A and AHU-213 operate in leadllag mode, and alternate
operation monthly. The unit is located in the North Penthouse on the roof. AHU-2A and
AHU-213 serves the 1st floor Quarantine area, which includes rooms 133, 134, 135, 136,
137, 138, and 139, where additional zone heating is provided by reheat coils, HC-2, HC-
3, HC-4 and HC-4. AHU-2A and AHU-213 each have one supply fan, one exhaust fan, one
cooling coil, and one heating coil. AHU-2 operates continuously.
ONSdO N
-en0 +4
OA �.
AHU-2A
AHU-2
---
SW* Fan
CV -2180 c!m
OR On
CC 2B W A2B
Firs: Poor Leval
Rn 138
=T V ,....� 11111111 FcstFb m. 13l
V'-2
CV - 22100 Orr
!^`-4
-40 -----------------------------------------►-. E-
Figure 15 AHU-2Al2B
HC-2
FBI oor �eve
♦� Rms. +34 +35
138 •
HCA
HC-5
First Floor Level
Rms. 133.137
Occupancy
AHU-2 operates 24 hours a day 7 days a week. The Quarantine area is occupied by the
staff members and animals.
Heating
Space heating is provided by heating coils, HC-A2A or HC-A2B, whichever serving the
lead AHU. Additional zone heating is provided by reheat coils, HC-2, HC-3, HC-4, and HC-
5 located at individual zones. HC-A2A and HC-A2B each has a rated heating capacity of
130 MBH at the design airflow of 2,180 cfm. HC-2, HC-3, HC-4, and HC-5 each have rated
heating capacity of 7.2 MBH, 10.5 MBH, 12.1 MBH, and 29 MBH respectively. Each coil is
served by glycol hydronic loop system. HC-A2A and HC-A2B heating valve modulates to
maintain the supply air temperature at 55°F.
Siemens Industry, Inc.
June 2011
- 24 - Proprietary & Confidential
0 Alaska SeaLife Center DETAILED INVESTMENT GRADE AUDIT SIEMEN
& ENERGY SERVICES PROPOSAL
Cooling
Space cooling is provided by a cooling coils, CC-2A or CC-26, whichever is serving the
lead AHU. CC-2A and CC-26 have a rated cooling capacity of 32.7 MBH. CC-2A or CC-26
cooling valve modulates to maintain the supply air temperature at 55°F. Cooling and
heating coil valves modulate in sequence as required.
Ventilation
AHU-2A and AHU-2B serve Quarantine area and supply 100% outside air at constant
volume of 2,180 cfm at all times. Ventilation is provided by one supply fan and one
exhaust fan, EF-2A or EF-2B, whichever is serving the lead AHU. Supply fans are located
in AHU-2A and AHU-26, and each has a rated capacity of 2,180 cfm, a rated motor power
of 3 hp, and fan operating speed of 2,048 rpm. Exhaust fans, EF-2A and EF-26 are
located on the rooftop near the north penthouse. EF-2A and EF-26 each has a rated
capacity of 2,190 cfm, a rated motor power of 3 hp, and fan operating speed of 1,770
rpm. Exhaust fan operation is interlocked to run simultaneously with AHU-2A and AHU-
2B.
AHU-2 Baseline Development
Baseline energy consumption model for AHU-2 was developed based on the measured
outside air temperature, supply air temperature, and the operating specifications. The
data was obtained on 15-minute intervals between December 12th, 2009 and January
4th, 2010. Heating coil load was calculated based on the outside air temperature, supply
air temperature, and supply airflow of 2,180 cfm (Equation 18). Based on the
observation of the supply air temperature, two heating load profiles were created for
different temperature ranges; below (Figure 16 and Equation 19) or above the outside air
temperature of 32°F (Figure 17 and Equation 20).
Equation 18
HCA2Load =1.08 x SuppdyAirf7oWAM 2 x (TS„P,1� -- Ta,�;de,,r )
100000
90000
80000
70000
60000
50000
40000
10
Heat Iwd j0tLjh) @ --32 F
IS 20 23 30 33
OAT,'F
Figure 16 AHU 2 Heat Load (Outside air temperature below 32°F)
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June 2011
Proprietary & Confidential
Alaska Sea Life Center
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Equation 19
HCA2Loadbelow32F =—495.83 x T0,,,,jd1tr + 89,827
Heat load (Btuh) @ >32 F
59 + 129397 =
30 35 40 45 50 55 60
OAT;F
Figure 17 AHU-2 Heat Load (Outside air temperature above 32°F)
Equation 20
HCA2LoadabovMF=-1,695.9xTo„u;d,,A;,+129,397
The electric load of supply and exhaust fans were calculated using Equation 16 and
Equation 17. Supply fan and Exhaust fan consume constant electrical load of 1.48 kW
and 1.04 kW, respectively.
AHU-3
General
AHU-3 is a constant volume, single duct, heat recovery unit manufactured by Heatex. The
unit is located in the South Penthouse on the roof. AHU-3 serves the 1st floor Wet Lab
area, which includes rooms 154 and 160. AHU-3 is served by one supply fan, one exhaust
parr, arr(d —a e hntl`ng coil. Heat recovery unit is a flat plate air-to-air type, where outside
air is preheated by exhaust air. The unit consists of face/bypass damper for defrost mode
of operation and recirculation damper for recirculation mode of operation.
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June 2011
aAlaska Sea Life Center
ouwd. A.
Tamp v M
RH+
I OA --9...
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
EF-3
CV - 5200 ChM
Tamp+AE -�
RH'
• fCulati0
1
•
AMU-3 •
W/ j
HEATEX 50OC:
•
•
•
T Beb. Bypass Aft., Bypass
EXCHANGER A.TampanE • arT—p+np
.� 6-40.
HC-Al t I
Eshau-Aa 1
,'
RH
TaRH1
+. 1
1
Figure 18AHU-3
...................................;
1
1
1
1
1
1
1
First Foot Level
k"JA+
•--•
Rm '80
---1
Temp
O
1
1
1
1
•
AHU-3
1
i
1
1
Supply Fan
1
•-��
Fre�FoorLeve�-�
•
CV -4800 dm
Rm 154
Occupancy
AHU-3 operates 24 hours a day 7 days a week. Wet Lab area is occupied by staff members
and animals.
Face/bypass Damper
Face/bypass dampers are located at the outside air inlet right before the air enters the
heat exchanger section. Damper operation is interlocked such that the face damper is
fully open when the bypass damper is fully closed. A PI (proportional integral) controller
modulates the face/bypass dampers to maintain the leaving exhaust air temperature
above the minimum temperature set point of 370F to prevent the heat exchanger from
icing.
- ideating
Outside air is preheated through heat exchanger to recover heat from the exhaust air.
Space heating is provided by heating coil, HC-A3. HC-A3 has a rated heating capacity of
77.8 MBH at the design airflow of 4,800 cfm. There are no additional reheat coils serving
the Wet Lab area. The average measured supply air temperature during the period of
data logging was approximately 68°F.
Cooling
There is no cooling coil serving AHU-3.
Ventilation
Ventilation is provided by one supply fan and one exhaust fan, EF-3. Supply fan and
exhaust fan operate continuously at constant speed. Supply fan has a rated capacity of
4,800 cfm, a rated motor power of 5 hp, and fan operating speed of 1,940 rpm. Exhaust
fan, EF-3 has a rated capacity of 5,200 cfm, a rated motor power of 3 hp, and fan
operating speed of 900 rpm.
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June 2011
aAlaska Sea Life Center
DETAILED INVESTMENT GRADE AUDIT islip"FPic
& ENERGY SERVICES PROPOSAL
AHU-3 is equipped with a recirculation damper,
which allows full recirculation operation when the
unit is in full recirculation mode. During the full
recirculation mode, the exhaust fan is shut down,
and the outside air damper will close.
Based on the facility observation and data trending,
the recirculation damper is partially open to allow
some of the return air to be mixed back in the
supply air. Measured temperature data shows that
10% to 20% of return air on average is being re-
circulated back to the supply air at all time.
AHU-3 Baseline Development
Baseline energy consumption model for AHU-3 was developed based on the measured
data listed in Table 6 and the operating specifications. Measurement was taken on 15
minute intervals.
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June 201
Alaska Sea Life Center
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Table 6
List of Trended variables- AHUA
Measurement Location
Unit
Outside air temperature
Temp ("F)
Outside air relative humidity
RH (%)
Return air temperature
Temp (°F)
Return air relative humidity
RH (%)
Exhaust air temperature
Temp (°F)
Exhaust air relative humidity
RH (%)
Supply alr temperature after heat recovery before recirculation damper
Temp (°F)
Supply air relative humidity after heat recovery before recirculation damper
RH (e,6)
Supply air temperature after heat recovery after recirculation damper
Temp (°F)
Supply air relative humidity after heat recovery after recirculation damper
RH (%)
Supply air temperature after heating coil HC-A3
Temp ("F)
Percentage of the returned air in the supply air was calculated based on the measured
temperatures: supply air temperature before the recirculation damper, supply air
temperature after the recirculation damper, and return air temperature. The amount of
return air in the supply air is as follows:
Equation 21
p/O� — TSA_Afier_Recvndallon —73i Bfors- Recirculation x 100
TRr — T&, Before Recirculation
Where
%RA =
Tsa After—Recircuiation =
TSkllefore_ Recirculation =
TM =
Percentage return air in supply air
Supply air temperature after recirculation damper
Supply air temperature before recirculation damper
Return air tempe-rature
Logged data showed that 10% to 20% of return air on average was circulated back into
the supply air.
Outside airflow was determined based on the calculated return airflow and the total
supply airflow of 4,800 cfm. The temperature across the heat recovery unit is known, and
the outside airflow is known. Based on the temperature and the airflow data, the heating
load was calculated (Equation 22). Heat exchanger heat recovery profile was developed
and shown in Figure 19 and expressed by Equation 23.
Equation 22
HXLoad =1.08 x OutsideAirFlow x (T� ,,—Ta,t,,d,9.r )
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June 2011
Alaska Sea Life Center
120000
6 100000
m 80000
d
60000
B 40000
x
20000
0
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Heat ExchangerPmflk
10 1s 20 25 30 35 40 4S so 55 60
OAT; F
Figure 19: AHU-3 Heat Exchanger Heat Recovery Performance
Equation 23
HXLoad = 2237.3 x Tou,,,d,, r+146,581
Temperature across the heating coil, HC-A3 and the supply airflow were used to calculate
the HC-A3 heat load (Figure 20). HC-A3 heating load profile was created based on the
calculated heating value and outside air temperature (Figure 20 and Equation 25).
Equation 24
HCA3Load =1.08 x SupplyAil flow uiu 3 x (TS„ pplyAw — Tf d, y r )
120000
l00ow
B0000
60000
4Boao
20"
0
10
V = -19T21'x i 14
W = o.eaT2
Heat Load(Btoh)
hmiaaat...
un
is 20 25 30 35 40 45 so 5S 60
OAT,F
Figure 20: AHU-3 HC-A3 Heating Load Profile
Equation 25
HCA3Load =—1,972.3 x To„,,dm,r + 140,429
The electric load of supply and exhaust fans were calculated using Equation 16 and
Equation 17. Supply fan and Exhaust fan consume constant electrical load of 2.27 kW
and 1.44 kW, respectively.
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Alaska 5eaLlfe Center
AHU-4
DETAILED INVESTMENT GRADE AUDIT S1 IF FN'
& ENERGY SERVICES PROPOSAL
AHU-4 is a 100% outside air, variable volume, single duct system manufactured by
TRANE®. The unit is located in the South
Penthouse on the roof top. AHU-4 serves
the 15t floor Dry Lab area, which includes
rooms, 128, 141, 143, 144, 152, 153,r
161, 162, and 163, where additional zone _
heating is provided by reheat coils, HC-9,
HC-10, HC-11, HC-17, HC-18, and HC-19.
AHU-4 is served by one supply fan, one f r
exhaust fan, one cooling coil, one heating '-i;.
coil, and one humidifier. AHU-4 operates
continuously. }
EF4
CV - 8000 dm
--------•-----------------------------------
r'r°-� faw ��ll II II I1�II II II I1i7�L
•• L.L.LJ_LJ_L.V Fraa Floor _evr
�A.H1 _ Fast Fbm teve
Supply Fen ~� LJ_L1.LJ_LLJ Rm 767
VAV -8000 dm i �7-�HC-188��77
!— I I I I I I I I L_ F//t Fbor Loves
C1013 110144 / HG'7
;............... Fvst Fbm �avd ......
i
/
�............... Faet Fbor Lave• .......
/
/ Hc-"
�/ ��11r7II'IIr7I1�I1'I1f'II�III''1L�_ F. F., Lave
_� 1J111WJ Rm.144 ......•
/
/ Fv/t Fbor avel
/ Rm 43
/
/ 9
/
/ Fu/t Fbw _evd
Figure 21 AHU-4
Occupancy
AHU-4 operates 24 hours a day 7 days a week. Dry Lab area is occupied by the staff
members and animals.
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Alaska SeaLife Center DETAILED INVESTMENT GRADE AUDIT CI IrluC
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Heating
Space heating is provided by a heating coil, HC-A4 located in AHU-4, and additional zone
heating is provided by reheat coils, HC-9, HC-10, HC-11, HC-17, HC-18, and HC-19. HC-A4
has a rated heating capacity of 521 MBH at the design airflow of 8,000 cfm. The capacity
of reheat coils are listed in Table 7.
Table 7
AHU-4 Reheat Coil Capacity
Reheat Coil
MBH
HC-9
6.8
HC-10
22.8
HC-11
22.8
HC-17
17.8
HC-18
22.8
HC-19
22.8
Each coil is served by the glycol hydronic loop system. During data logging, supply air
temperature was maintained between 70°F and 80T.
Cooling
Space cooling is provided by a cooling coil, CC-3 located in AHU-4. CC-3 has rated cooling
capacity of 140.3 MBH. CC-3 cooling valve modulates to maintain the supply air
temperature at supply air temperature set point. Heating and cooling coil valves
modulate in sequence.
Ventilation
AHU-4 serves the Dry Lab area and supplies 100% outside air at all time. Ventilation is
provided by one supply fan, and one exhaust fan, EF-4. Supply fan is equipped with a
vana a frequency rive, an an speedIs mo u a e to maintain t e uct static pressure
set point of 1.5"w.c. EF-4 operates continuously at constant speed. Outside air is mixed
with exhaust air to maintain the constant flow velocity at EF-4. Outside air damper
modulates to maintain the duct static pressure set point of 2"w.c.
The supply fan has a rated capacity of 8,000 cfm, a rated motor power of 10 hp, and fan
operating speed of 1,115 rpm. EF-4 has a rated capacity of 8,000 cfm, a rated motor
power of 10 hp, and fan operating speed of 1,170 rpm. There are no interlocks in
operation of the supply fan and exhaust fan.
Humidifier
Humidification of the supply air is provided by a humidifier, HU-2. Currently HU-2 is not
operational because it has been disabled through the existing building automation
system. HU-2 has a rated capacity of 285 Ibslhr. When operational, HU-2 modulates to
maintain the space humidity set point of 45% Relative Humidity according to the system
design.
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June 2011
�- Alas_k_a Sea_Life Center DETAILED INVESTMENT GRADE AUDIT S' EM EN«
I 11 & ENERGY SERVICES PROPOSAL
�a.<. 1
n�
AHU-4 Baseline Development
Baseline energy consumption model for AHU-4 was developed based on the measured
data listed in Table 8 and the operating specifications. The data was obtained on 15-
minute intervals between December 12th, 2009 and January 4th, 2010.
Table 8
I ict of Tranded Variables
Measurement Location
Unit
Outside air temperature
Temp °
Outside air relative humidity
RH %
Supply fan VFD electrical load
Amperage A
Supply air temperature
Temp °
Supply air relative humidity
RH %
Based on the measured supply fan VFD electrical load and outside air temperature,
supply fan operating profile was created (Figure 22 and Equation 29). Fan electrical load
was calculated using Equation 16, Equation 17, and Equation 26 through Equation 28.
Equation 26
FLkW x1000
FLAmps =
Volts x PoiverFactor xMotorEfficiency x 1.732
Equation 27
%Amps = MonitorAmps
FLAmps
Equation 28
kW = FLkW x %Amps
Fan kW
2.5
23
2.0
9
t� 1.6 -
C L
im
13
1-0
10 is m 25 30 3S 40 45 so SS 60
OAT 'F
Figure 22 AHU-4 Supply Fan Electrical Load vs. Outside Air Temperature
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A FNFRGY SFRVIr. FS PRnPncA1
Equation 29
SupplyFanPowerAnU4 =—0.0003 x To,dsde.4,r — 0.0283 x T,,ufsidmjr + 1.3356
Supply fan airflow was calculated using Equation 16, Equation 17, Equation 26, Equation
27, and Equation 30, where supply fan VFD electrical load was related to VFD speed
shown in Figure 23 to calculate %Flow.
Equation 30
SupplyAirflow = %Flow x Maxim umAirFlow
VFD Speed vs. Electrical Load
120%
100%
80%
y 60%
C
40%
20%
0%
0% 20% 40% 60% 80% 100%
%kW/%hp
Figure 23 VFD Speed vs. Electrical Load
AHU-4 heating load was calculated based on the supply air temperature and supply fan
airflow determined based on the measured VFD electrical load (Equation 31) AHU-4
heating load profile is shown in Figure 24 and expressed as Equation 32.
Equation 31
HCA4Load =1.08 x SupplyAirflow.4mu4 x (TS„,�Y —T, ,� }
3SO,W0
3WAW
250AW
200A00
1SOAW
100AW
SOA00
0
10
Heatlns load (OWh)
15 20 2S 30 3S 40 45 s0 SS 60
OAT; F
Figure 24 AHU-4 HC-A4 Heating Load Profile
Equation 32
HCA4Load = —3,892 x Touc�de ,.r -* 343,753
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4 1 . G 4 Ji f b t. .
AHU-5
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
General
The Air Handling Unit 5 (AHU-5) serves areas located on the first and second floor that
are primarily used for offices, gallery, and lobby. The system is a mixed air, single duct,
variable volume unit with reheat coils. It is located in the North Penthouse.
Figure 25 AHU-5
Occupancy
Hours of operation are 24 hours a day, 7 days a week.
Heating
The system is designed to deliver 55°F temperature supply air. A mixed air damper is
modulated along with the heating coil valve to maintain the set point. When heat needs
to be added to the air stream, it is done through a hot water coil that has a rated capacity
of 1,782 MBH.
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Cooling
The system is designed to deliver 55°F temperature supply air. A mixed air damper is
modulated along with the cooling coil valve to maintain the set point. When there is a
need for cooling of the air stream it is done through a chilled water coil that has a rated
capacity of 526 MBH.
Ventilation
The supply fan is a 30,000 cfm fan with a rated static pressure of 3.31" w.c. at a speed of
693 RPM. The supply fan motor is rated at 30 hp, 460 volts, and 3 phase. It is modulated
by a Variable Frequency Drive (VFD). The VFD modulates the motor to maintain the duct
static pressure set point of 1.5" w.c.
Reheat Coils
Reheat Coils (RHC) are used to raise the air temperature of the discharge air provided by
AHU 5 at the point of distribution to the zones. There are three different capacities of
coils. Heating Coil 1 (HC-1) serves the Lobby 103 area and has a rated heating capacity of
170 MBH at a flow of 12.2 gpm and an entering air temperature of 55°F. Heating Coil 20
(HC-20) serves the Office 201 area and has a rated heating capacity of 11.9 MBH at a
flow of 0.85 gpm and an entering air temperature of 55°F. Heating Coil 21 (HC-21)
serves the Gallery 222 area and has a rated heating capacity of 28.4 MBH at a flow of 2
gpm and an entering air temperature of 55°F.
Return Air
The return air is either re -circulated by the AHU as required by the system or exhausted
from the building by Exhaust Fan 5 (EF-5). EF-5 is a constant volume, 3,050 cfm fan with
a rated static pressure of 0.75" w.c. at a speed of 3,050 RPM. The exhaust fan motor is
rated at % hp, 120 volts, and single phase.
In order to obtain the baseline energy use for the AHU-5, measurements were taken on
the following points (Table 9). The data was obtained on , 5-minute intervals between
December 12th, 2009 and January 4th, 2010. The measured data was used to calculate
the correlation between the load (MBH and kW) and outside air temperature and time of
the day.
Siemens Industry, Inc.
June 2011
Table 9
List of Trended Variables, AHU-5
Measurement Location
Units
Outside air temperature
Tern °
Outside air relative humidity
RH %
Return a:r temperature
Temp °
Return alr relative humidity
RH %
Mixed air temperature
Temp °
Mixed air relatve humidity
RH %
Supply air tem eratuLt
°
Supply air relative humidity
—Temp
RH %
Su fanspeed
Seed %
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lr
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
The electric load from AHU 5 comes from the variable flow supply air fan and the
constant volume exhaust fan. The electric load for the supply fan was calculated using
Equation 16, Equation 17, and Equation 26 through Equation 28.
Calculated supply fan power use was plotted for corresponding values of outside air
temperature. A quadratic equation was used to fit to the resulting plot (Figure 26 and
Equation 33).
10
a
0
Total Fan flee Load (kW)
0 s 10 15 20 25 30 35 40 45 so
OAT; F
Figure 26 Supply Fan Power vs. OAT, Occupied
Equation 33
SupplyFanP ower,, j„ 5 =—0.0012 x T2u�;dea,r — 0.0959 x Tou,,deA,r + 6.6423
The exhaust fan power was calculated to be a constant 0.36 W.
Percent current was calculated using Equation 27, and it was used with the relationship
for current to flow for a variable frequency drive to determine the percentage flow
{Figure 23}rThe percentage flow wastrsedto calculate the Sll�air flaw (Equation 34)- — — -
Equation 34
Supp1yAkfl0wAM.-5 = %Flow THUS xMazimumAirF7ows rely
The load on the central plant from AHU-5 comes from the heating coil. The heating coil
load (Btuh) was calculated using Equation 35.
Equation 35
HCA5Load =1.08 x SupplyAir f7owAH, , 5 x (T&PPIyA r — Tm.,,";r )
The calculated load for AHU-5 was plotted against outside air temperature for the
corresponding 15 minute trend interval. A quadratic equation was used to fit to the
resulting plot. The load to the central plant from the heating coil and the heating coil is
illustrated in Figure 27.
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. une 201 "
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DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Heat toad (Stub)
600,000
480,000
m
360,000
240,000
x
120,000
i
y_
250.06x—
736—
—
. ..
.18385x.+
R3
0.7959
0
0 5 10 15 20 25 30 35 40 45 50
OAT;F
Figure 27 AHU-5 Heat Load to Central Plant
The resulting heat load profile as a function of outdoor air temperature is illustrated in
Equation 36.
Equation 36
HCASLoad = 250.06 x T uMsde t„—18,385 x To„,dm,, + 462,736
AHU-6
General
The Air Handling Unit 6 (AHU-6) serves areas located on the first and second floor that
are primarily used for offices and the exhibit. The system is a mixed air, single duct,
variable volume unit. It is located in the South Penthouse.
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& ENERGY SERVICES PROPOSAL
Second Floor Plenum
Sis—d Floor
Leval
R. 238
Se d F ddr
Lave;
Rm 237 & 238
(-tenor)
Sec�ndFbor
_avd
Rm 237
SemM Floor
Laval
Rm 235 �C1"
SeraW Fbor
Rm 253 (swN)
Second Four
71
......;..... s .Oval
Rms 245, 248
247.248, 250
CC-5 HC-AB
EF-8
CV — 310 dm
EA .-------- Restrooms
Figure 28 AHU-6
Occupancy
Hours of operation are 24 hours a day, 7 days a week.
_Oval
Rms 251. 252
Frd Floor .ave
Rm 181
Fast F oor Levd
Rm 180
F,d Floor Leval
Rms 178 179
Heating
The system is designed to deliver 55aF temperature supply air. A mixed air damper is
moduiate-d rtong W-ith-The iieat`nng coil valve% maintain -the se-t pWlnl:. When-heeat-nee&
to be added to the air stream it is done through a hot water coil that has a rated capacity
of 1,342 MBH.
Cooling
The system is designed to deliver 55eF temperature supply air. A mixed air damper is
modulated along with the cooling coil valve to maintain the set point. When there is a
need for cooling of the air stream it is done through a chilled water coil that has a rated
capacity of 396 MBH.
Ventilation
The supply fan is a 22,600 cfm fan with a rated static pressure of 3.36" w.c. at a speed of
1,033 RPM. The supply fan motor is rated at 25 hp, 460 volts, and 3 phase. It is
modulated by a Variable Frequency Drive (VFD). The VFD modulates the motor to
maintain the duct static pressure set point of 1.5" w.c.
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Return Air
The return air is either re -circulated by the AHU as required by the system or exhausted
from the building by Exhaust Fan 6 (EF-6). EF-6 is a constant volume, 310 cfm fan with a
rated static pressure of 0.375" w.c. at a speed of 1,050 RPM. The exhaust fan motor is
rated at fractional horse power, 120 volts, single phase, and has a calculated brake horse
power of 0.021 hp.
AHU-6 Baseline Development
In order to obtain the baseline energy use for AHU-6, measurements were taken on the
following points (Table 10). The data was obtained on 15-minute intervals between
December 12th, 2009 and January 4th, 2010. The measured data was used to calculate
the correlation between the central plant heating load (MBH) and outside air
temperature and time of the day.
Table 10
List of Trended variables_ AMU-6
Measurement Location
Units
Outside air temperature
Temp °
Outside air relative humidity
RH %
Mixed air temperature
°
Mixed air relative humidity
—Temp
RH %
Supply air temperature
Temp °
Supply air relative humidity
RH %
Supply fanspeed
Seed °%
The electric load from AHU-6 comes from the variable flow supply air fan and the
constant volume exhaust fan. The electric load for the supply fan was calculated using
Equation 16, Equation 17, and Equation 26 through Equation 28.
A plot of supply fan power use was then plotted for corresponding values of outside air
temperature. A linear equation was used to fit to the resulting plot (Figure 29). Equation
37 illustrates the correlation.
Siemens Industry, Inc. - 40 Proprietary & Confidential
June 2011
Alaska Sea Life Center
-. d .' u. 1. i H.
10
8
3
a
6
9
4
Y
2
0
0
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Total Fan Elee Load (kW)
a 10 15 20 25 30 3s 40 45
OAT; F
Figure 29 AHU-6 Supply Fan Power vs. OAT, Occupied
Equation 37
FanPower,4HU6 = 4.25
so
The load on the central plant from AHU-6 comes from the heating coil. The heating coil
load (MBH) was calculated using Equation 38.
Equation 38
HCA6Load =1.08 x SupplyAkflow:;H16 x (TS„ pply,.b-—T.f.d4 , )
The calculated load for AHU-6 was plotted against outside air temperature for the
corresponding 15 minute trend interval. A linear equation was used to fit to the resulting
plot. The load to the central plant from the heating coil and the heating coil is illustrated
in Figure 30.
Meat load Btu
400.000
320,000
Y
y 240.000
160,000
Y
80,000
0
S 10 15 20 25 30 35 40 45 so
OAT;F
Figure 30 AHU-6 Heat Load to Central Plant
The resulting heat load profile as a function of outdoor air temperature is illustrated in
Equation 39.
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.—�.
AHU-7
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Equation 39
HCA6Load = —5,652 x Tou ,dmj,. + 287,941
General
The Air Handling Unit 7 (AHU-7) serves areas located on the first floor that is primarily
used for curatorial. The system is a 100% outside air, single duct, variable volume unit. It
is located in the South Penthouse.
-----
OA L.......
..••;.••.....•,�
�1�
First Floor Level
Rm :67 •�
s
�.....—
Lj j'
AHU-7
-...-.
I Second Floor
1......... l -�
leve
Supply Fan
VAV —6400 cfm
Rms. 260, 261
First Floor Level EA
r...-..... Rm.187
HC-A7
First Floor Levei -*,!EA
Rm.177 `J
i' •�
Second Floor
�
•••• Level
i Rm. 236
F rst Floor Level -0-O
Rm 182
Figure 31 AHU-7
Occupancy
Hours of operation are 24 hours a day, 7 days a week.
Heating
The system is designed to deliver 557 temperature supply air. The heating coil valve is
modulated to maintain the set point. When heat needs to be added to the air stream it is
done through a hot water coil that has a rated capacity of 488 MBH.
Cooling
There is no cooling coil.
Ventilation
The supply fan is a 6,000 cfm fan with a rated static pressure of 2.8" w.c. at a speed of
1,138 RPM. The supply fan motor is rated at 5 hp, 460 volts, and 3 phase. It is modulated
by a Variable Frequency Drive (VFD). The VFD modulates the motor to maintain the duct
static pressure set point of 1.5" w.c.
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& ENERGY SERVICES PROPOSAL
Reheat Coils
There are no reheat coils.
Return Air
There is no return air.
AHU-7 Baseline Development
In order to obtain the baseline energy use for the AHU-7 measurements were taken on
the following points (Table 11). The data was obtained on 15-minute intervals between
December 12th, 2009 and January 4th, 2010. The measured data was used to calculate
the correlation between the load (MBH and kW) and outside air temperature and time of
the day.
Table 11
List of Trended Variables_ AHU-7
Measurement Location
Units
Outside air temperature
Temp "
Outside air relative humidity
RH %
Supply air temperature
Temp "
Supply air relative humidity
Supply fanspeed
I Seed %
The electric load from AHU-7 comes from the variable flow supply air fan. The electric
load for the supply fan was calculated using Equation 16, Equation 17, and Equation 26
through Equation 28.
A plot of supply fan power use was then plotted for corresponding values of outside air
temperature. A linear equation was used to fit to the resulting plot. Equation 40
illustrates the correlation.
150
125
3 1.00
Y_
9
B 0.75
W 050
025
0.00
0
Total Fan Elec Load (kW)
5 10 15 20 25 30 35 40 45 50
OAT;F
Figure 32 AHU 7 Supply Fan Power vs. OAT, Occupied
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& ENERGY SERVICES PROPOSAL
Equation 40
SupplyFanPoiver,4HU7 = 0.0008 x To„wdmir + 0.6104
The load on the central plant from AHU-7 comes from the heating coil. The heating coil
load (MBH) was calculated using Equation 41.
Equation 41
HCA7Load =1.08 x SupplyAirflow wu" x (TS„pph,,g,r-TournaeAir )
The calculated load for AHU-7 was plotted against outside air temperature for the
corresponding 15 minute trend interval. A linear equation was used to fit to the resulting
plot. The load to the central plant from the heating coil and the heating coil is illustrated
in Figure 33.
350000
300000
Z 250000
-� 200000
150000
n
= 100000
50000 -
Heat Load (Otuh)
=-1757
x+2501
3
Rz =
556
0
0 5 10 15 20 25 30 35 40 45 50
OAT; F
Figure 33 AHU-7 Heat Load to Central Plant
The resulting heat load profile as a function of outdoor air temperature is illustrated in
Equation 42.
Equation 42
HCAUoad = -1,757 xTouudeA;r - 250,193
AHU-8
General
The Air Handling Unit 8 (AHU-8) serves areas located in the basement that are primarily
used for offices and mechanical spaces. The system is a mixed air, single duct, constant
volume unit with reheat coils. It is located in the basement.
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OA ..... 0
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
....................
i
AHU-8
AHU-8
Supply Fan
CV —9 000 dm
HC-AB
Figure 34 AH U-8
Occupancy
Hours of operation are 24 hours a day, 7 days a week.
Basement Level Plenum
H7Basement Level
North Half
Rms 007 - 009
HC-22
Basement Leve
B-111.North
Helf
Rm 006
..
I
HC-23
�
H-00.Base__�
North Half
Ep,
Rm 00' - 005
HC-24
Heating
The system is designed to deliver 55F temperature supply air. A mixed air damper is
modulated along with the heating coil valve to maintain the set point. When heat needs
to be added to the air stream it is done through a hot water coil that has a rated capacity
of 244 MBH.
Cooling
There is no cooling.
Ventilation
The supply fan is a 9,000 cfm fan with a rated static pressure of 1.5 w.c. at a speed of
635 RPM. The supply fan motor is rated at 5 hp, 460 volts, and 3 phase.
Reheat Coils
Reheat Coils (RHC) are used to raise the air temperature of the discharge air provided by
AHU-8 at the point of distribution to the zones. There are three different capacities of
coils. Heating Coil 22 (HC-22) serves the basement office area and has a rated heating
capacity of 13.8 MBH at a flow of 1.0 gpm and an entering air temperature of 55°F.
Heating Coil 23 (HC-23) serves the basement shop area and has a rated heating capacity
of 17.8 MBH at a flow of 1.3 gpm and an entering air temperature of 55*F. Heating Coil
23 (HC-23) serves the basement storage and janitorial area and has a rated heating
capacity of 14.5 MBH at a flow of 1.0 gpm and an entering airtemperature of 55°F.
Return Air
The return air is either re -circulated by the AHU as required by the system or exhausted
from the building.
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June 2011
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Alaska SeaLife Center
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
AHU-8 Baseline Development
In order to obtain the baseline energy use for the AHU-8 measurements were taken on
the following points (Table 12). The data was obtained on 15-minute intervals between
December 12th, 2009 and January 4th, 2010. The measured data was used to calculate
the correlation between the central plant heating load (MBH) and outside air
temperature and time of the day.
Table 12
List of Trended Variables, AHU-8
Measurement Location
Units
Outside air temperature
Temp °
Outside air relative humidity
RH %
Retum air temperature
Temp °
Return air relative humid'
RH %
Mixed air temperature
Tem °
Mixed air relative humidity
RH %
Supply air temperature
Temp °
Supply air relative humidity
RH %
The electric load from AHU-8 comes from the constant flow supply air fan. The electric
load forthe supply fan was calculated using Equation 16 and Equation 17.
The supply fan power was calculated to be a constant 2.13 M
The load on the central plant from AHU-8 comes from the heating coil. The heating coil
load (Btuh) was calculated using Equation 43.
Equation 43
HCABLoad =1.08 x Supp1yAirflow,4HU8 x (Ts„PPryAj.—T1lixedfir)
The calculated load for AHU-8 was plotted against outside air temperature for the
corresponding 15 minute trend interval. An average was taken of the data. The load to
the central plant from the heating coil is illustrated in Figure 35.
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Heat Load (Btuh)
300000
250000--__....,. -------------- - _- f
200000 100000
�
S0000 E
0
0 S 10 35 20 25 30 35 40 4S 50
OAT; F
Figure 35 AHU-8 Heat Load to Central Plant
The average heating load at AHU-8 is 165 MBH.
AHU-9
General
The Air Handling Unit 9 (AHU-9) serves areas located in the basement that are primarily
used for offices and shops. The system is a mixed air, single duct, and constant volume
unit. It is located in the basement.
I
I
OA i........ ..
-
AHU 9
r...... .
�
Basement Level
�••� South Half
Rms. 012 - 021
AHU-9
Supply Fan
Cv —1,750 cfm
Basement Level Plenum
r
HC-A9
r
r
�
r
r
r
•..........................................�
Figure 36 AHU-9
Occupancy
Hours of operation are 24 hours a day, 7 days a week.
Heating
The system is designed to deliver 55°F temperature supply air. A mixed air damper is
modulated along with the heating coil valve to maintain the set point. When heat needs
to be added to the air stream it is done through a hot water coil that has a rated capacity
of 55 MBH.
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Cooling
There is no cooling.
DETAILED INVESTMENT GRADE AUDIT
& ENERGY SERVICES PROPOSAL
Ventilation
The supply fan is a 1,750 cfm fan with a rated static pressure of 1.5" w.c. at a speed of
1,454 RPM. The supply fan motor is rated at 1.5 hp, 460 volts, and 3 phase.
Reheat Coils
There are no reheat coils.
Return Air
The return air is either re -circulated by the AHU as required by the system or exhausted
from the building.
AHU-9 Baseline Development
In order to obtain the baseline energy use for the AHU-9, measurements were taken on
the following points (Table 13). The data was obtained on 15-minute intervals between
December 12th, 2009 and January 4th, 2010. The measured data was used to calculate
the correlation between the central plant heating load (MBH) and outside air
temperature and time of the day.
Table 13
Trended Variables, AHU-9
Measurement Location
Units
Outside air temperature
Temp °
Outside air relative humidity
RH %
Supply air temperature
Temp °
Supply air relative humidity
RH %
The electric load from AHU-9 comes from the constant flow supply air fan. The electric
load for the supply fan was calculated using Equation 16 and Equation 17.
The supply fan power was calculated to be a constant 0.49 W.
The load on the central plant from AHU-9 comes from the heating coil. The heating coil
load (MBH) was calculated using Equation 44.
Equation 44
HCASILoad=1-08xSupplyAirflowA1i/9 x (TS„nrl,A+r—TO.id,Iir)
The calculated load for AHU-9 was plotted against outside air temperature for the
corresponding 15 minute trend interval. A linear equation was used to fit to the resulting
plot. The load to the central plant from the heating coil and the heating coil is illustrated
in Figure 37.
Siemens Industry, Inc.
June 201'
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s.^1
Alaska 5eaLife Center DETAILED INVESTMENT GRADE AUDIT
' SIEMENS
& ENERGY SERVICES PROPOSAL
Heat Load (Btuh)
150000
120000
m 90000
e
m 60�0 y w-1833.7a1. 126491
30000
0
0 5 10 t5 20 25 30 35 40 45 50
OAT;F
Figure 37 AHU-9 Heat Load to Central Punt
The resulting heat load profile as a function of outdoor air temperature is illustrated in
Equation 45.
Equation 45
HCA9Load =—1,833.7 x To,,.d Aj, + 126,491
Life Support System
General
There is a system of pumps and filters that make
-up the- -Life Suppod-Systm 45S - The system is
used to maintain the different habitats for the
animals at the center. There are three primary
habitat pools: Birds, Seals, and Sea Lions.
Constant volume pumps are used to pump water
out of the tanks and thru a parallel filter bank.
Flow is controlled through the filters by a set of
valves that modulate to maintain a specific flow
set point (Figure 38). After three days the filters
are backwashed to remove the waste that has
collected in the filters from the tanks. The process then repeats.
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Habitat Pool I Total Flow
Meter
Valve 1 Fitter 1
Flow Meter
Filter 1
Valve 2 Filler 2
Flow Meter
Pump 1ACN Filter 2
Pump 2 Valve 3 Fitter 3
Flow Meter
d.
Filter 3
Filter
Valve 4 4
F1ow Meter
Filter 4
Figure 38 LSS Filtration System
Pumps
Each filtration system has two primary habitat recirculation pumps that run continuously
to maintain the specific flows as required by each pool. The pumps are constant volume
with the specifications shown in Table 14. The motors that drive the pumps are 460
volts, 3 phase.
Table 14
Pumas Snarifiratinnc fnr Filtration Svctam
Pump
Name
Habitat
Total Flow
(gpm)
Pressure
(feet)
Power
(bhp)
Speed
(RPM)
Impeller Diameter
(inches)
LSS 19&20
Seals
760
75
10
1770
8.75
LSS 21 &22
1 Sea Lions
1350
1 75
1 17.1
1 1770
9.5
LSS 27&28
Marine Birds
1670
75
22.1
1775
9.375
Filters
Each filtration system has four sand filters to filter the waste from the recirculation flows.
The pressure drop across the filters increases as they remove waste from the recirculation
flow. Once the differential pressure for the clean filter has increased by 10 psi the filter
should be cleaned by back washing it. This increase in pressure can be related to a
specific run time which is considered to be 3 days for the pools.
Occupancy
Hours of operation are 24 hours a day, 7 days a week.
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June 2011
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DETAILED INVESTMENT GRADE AUDIT S1 F FNC,
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Life Support System Baseline Development
To calculate the baseline energy use for the LSS, manufacturer's data was obtained for
the pumps in use.
The electric load from the LSS comes from the constant volume pumps. The brake horse
power, bhp was obtained from the manufacturer's pump curves for each pump.
Full load power was then calculated by using the motor efficiency, see Equation 46.
Equation 46
FLkW _ bhp x 0.746
P`°"�O1e� — MotorEfciency
The constant volume pumping power is shown in Table 15.
Table 15
Baseline pumping power for each habitat
Pum Name
Habitat
Total Full Load Power k
LSS 19&20
Seals
16.7
LSS 21&22
Sea Lions
28
LSS 27&28
Marine Birds
36.2
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Alaska SeaLife Center
DETAILED INVESTMENT GRADE AUDIT SIEMENS
& ENERGY SERVICES PROPOSAL
Section III — Facility Improvement Measures
FIM 1.00 Lighting Upgrades
Electric Savings:
66,995 kWh
51 kW annual
$4,963
Fuel Oil Savings:
0 Gallons
$0
Operational $ Savings:
$3,500
Total $ Savings:
$8,463
AREAS INCLUDED UNDER THIS MEASURE:
• Areas of the entire facility.
EXISTING CONDITION:
The Alaska SeaLife Center building is of relatively new construction and has a typical
modern lighting system. The building consists of three major areas: Offices, Laboratories
and Public Gallery/Display Areas. The Office and Laboratories are almost exclusively 1st
Generation T8 Fluorescent fixtures with electronic ballasts. Many of these fixtures are
vapor tight and suspended Directlindirect models. The Public Gallery/Display Areas are
quite a bit different. The Aquarium and SeaLife Display Areas utilize a number of
specialized HID fixtures which are not slated for retrofit. The rest of these Public
Gallery/Display Areas utilize a large number of incandescent and compact fluorescent
track and can lighting to illuminate information and educational wall displays. The
exterior lighting consists of 150 W and 400 W Metal Halide fixtures and 70 W and 1,000
W High Pressure Sodium fixtures.
PROPOSED FACWT MEASURE:
In the Office and Laboratory Areas, install new lamps and ballasts in all existing 4 ft. T8
fixtures. The new 3rd generation T8 lights and electronic ballast combination will have a
reduced wattage while maintaining similar light levels to the existing. The electronic
ballasts will have a low ballast factor. Install new Pulse Start Metal Halide kits in the
exterior HID fixtures. SIEMENS will provide all of the lamps, ballasts, and fixtures.
ASSUMPTIONS:
In addition to a reduction in annual kWh's, a lighting upgrade will provide a well -lit work
environment which is critical to the productivity, comfort, health, and safety of all
occupants. To promote comfort and productivity, the proposed upgrade designs
specifies the appropriate fixture, lamp, and ballast combination to provide the
appropriate lighting color, density, and disbursement while minimizing glare. An
integrated, whole -system approach to lighting design maximizes quality, energy
efficiency, esthetics, maintainability, and life -cycle costs.
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DETAILED INVESTMENT GRADE AUDIT SIEMENS
D. CAIEW-2V Crn\/IPre nnnnnc'nI
Measurements were taken on the following seven lighting circuits (Table 16). The
measured data characterize the power consumption of the most prevalent lamp types.
During the post retrofit M&V phase of the project, electrical circuit measurements will be
taken at the same exact locations to quantify the electrical demand savings due to
lighting upgrades.
Table 16
List of Pre and Post Retrofit Locationc
Reading #
Ro#om
#
Panel Location
Type
PrivatePanel
Private
Corridor 002 / ILC
1
009
Office
BHD From J Box
101
Mechanical
Corridor 002 / ILC
2
010
Room
BHD From J Box
101
Mechanical
Corridor 002 / ILC
3
010
Room
I BHD From J Box
101
Open
4
219
Office
ZH B Zone 25
Corridor 220 / LP 207
5
236
Gallery
2LG1 29
Corridor 227 / LP 208
6
1 236
Gallery
2LG1 31
Corridor 227 / LP 208
7 1
236
Gallery
2LG1 30
Corridor 227 / LP 208
SIEMENS takes into account many factors when considering any lighting retrofit project
including:
• Illumination purpose: The requirements of lighting systems vary with different
applications. SIEMENS has proven experience redesigning task, accent, high -bay,
decorative, historical and general lighting schemes.
• Color rendering: The interaction of artifical and natural lighting is important for
both visual clarity and aesthetics. Color rendering of independent luminaries is
important as well as the combined effect of different lighting sources within
defined areas.
• Efficiency: Improving the efficiency of a lighting system is not limited to lamps
and ballasts. New fixtures designed for maximum light output, reflector kit
retrofits, manipulating ballast factors, and tandem -wiring of ballasts are a few
ways in which maximum light output can be attained with minimum energy
input.
• Controllability: While attention is focused on increasing the efficiency of lighting
systems, an equally important dimension to lighting management is
controllability. Ideally, lighting systems will be energized only at those times as
required by its illumination purpose. Often times, occupancy patterns are not
predictable, and those control systems that permit flexibility in scheduling or
automated on/off control provide the greatest benefit. There are certain
instances in which there are opportunities to interface HVAC systems, as well as
lighting circuits, to occupancy sensors for additional benefit.
• Maintainability: This refers to the degree of ease in which the collective lighting
systems of a building or group of buildings are maintained. Fixture and
component life, fixture height and the effort required for cleaning and repairing
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Alaska seaLlfe Center, DETAILED INVESTMENT GRADE AUDIT SIEMENS
sea & ENERGY SERVICES PROPOSAL
fixtures, quantity of lamps and ballasts, and the amount of unique repair parts
(i.e. lamps, ballasts, lens, and sockets) are all vital components when determining
system maintainability.
Heating Penalty and Cooling Savings calculations are based on the total kWh reduction
calculated for the lighting retrofit project. It is assumed that all the lighting energy to be
saved occurs within the conditioned space.
SAVINGS CALCULATIONS:
Energy savings from each retrofit will be based on a statistically developed number of
runtime hours for specific area types and the areas wattage reduction. The wattage
reduction will be based upon the pre and post retrofit wattages.
Stipulated runtimes were derived from measured data collected from a statistically valid
sampling of various use types. The logger data was analyzed and divided into specific
space types and then averaged to develop the Stipulated Runtime Hours for each of the
space types.
Cost savings will be realized by decreasing power requirements to the respective lighting
systems resulting in a decrease in annual electrical energy usage (kWh). Lighting system
inventory requirements will be streamlined by standardizing lamp, ballast, and
component manufacturer's for the buildings. New lighting systems will provide
operational savings in the form of reduced ballast and lamp replacement costs.
HEATING VENTILATION AND AIR CONDITIONING (HVAC) INTERACTION
CALCULATION:
The installation of a more efficient lighting system will reduce internal heat gains. The
impact of the lighting improvement measure and other measures relating to building
heat loss: have been evaluated using a heat loss study. A calculation of the interaction
between lighting wattage reduction and heating loads was done.
FIM 1.01 Lighting Controls
Electric Savings: 23,941 kWh
0 kW
$1,559
Fuel Oil Savings: 0 Gallons
$0
Total $ Savings: $1,559
FACILITIES INCLUDED UNDER THIS MEASURE:
e Areas of the entire facility.
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Alaska 5eaLife Center
� rr
"-- -
DETAILED INVESTMENT GRADE AUDIT
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EXISTING CONDITION:
Currently operation of the lights is provided by the Triatek lighting control system.
PROPOSED FACILITY IMPROVEMENT MEASURE:
Upgrade the existing Triatek lighting control system so that it can be controlled directly
by a new SIEMENS APOGEE Insight energy management control system.
ASSUMPTIONS:
Heating Penalty calculations are based on the total kWh reduction calculated for the
lighting retrofit project. The areas labeled for the exterior of the building were not
included in the Heating Penalty calculations.
The current annual burn hours and the retrofit annual burn hours due to lighting
controls, by space type, is identified in Table 17.
Table 17
Annual Burn Hours Rv Some Tvoe
Codes
Area Type
Current Annual Hours
Retrofit Annual Hours
BR
Break room
2600
1300
CL
Classroom
3244
2433
DH
Dining Hall
3244
2433
EX
Exits
8760
8760
I KN I Kitchen 1 3244 1 2433 1
' LO I Lobb 3244 1 32" '
ME I Mech/Elec. Room 1 8760 1 1752
MR Meeting Room 1 1026 1 616 1
00 Open Office 2600 2600
I PO 1 Private Office 1768 1503 1
' WA I Work Area 1 7236 1 806
DAL Direct Aquarium Lighting 32" 3244
PHW Private Corridor 3588 3014
STR
SAVINGS CALCULATIONS:
Energy Savings calculations for this measure are based on reduction in lighting burn
hours and post implementation of FIM 1.00 — Lighting Retrofit, and use all post retrofit
lighting power consumptions included in FIM 1.00 as the existing conditions for this
measure. Runtime reduction hours from installing lighting controls were statistically
developed based on a result of occupancy logging at 10 locations which represent
specific area types namely: conference room, corridor, laboratory, mechanical room,
private office, public restroom, and staff restroom. The reduction in the number of burn
hours per year was calculated based on the data collected by the Watt Stoppers. This
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kr�' Alaska Sea Life Center DETAILED INVESTMENT GRADE AUDIT
& ENERGY SERVICES PROPOSAL
!—
reduction in burn hours was applied to the different area types to calculate annual
savings. Table 18 identifies the location of the 10 spaces where Watt Stoppers were
installed.
Table 18
Watt Stopper Installation Locations
Sensor#
Area Type
Room #
1
Conference Room
270
2
Corridor
002
3
Corridor
220
4 Laboratory
159
5 Laboratory
152
6 Mechanical Room
010
7 Private Office
207
8
Private Office
234
9
Public Restroom
211
10
Staff Restroom
217
HVAC INTERACTION CALCULATION:
Reduction in lighting burn hours will reduce the internal heat gain. The reduction in
internal heat gain was used to calculate the increase in the facility heating load.
F1M 2.00 Water Conservation
Electric Savings: 0 kWh
$0
Water/Sewer Savings 456,000 Gallons
$2,945
Total $ Savings: $2,945
FACILITIES INCLUDED UNDER THIS MEASURE:
• Entire facility.
EXISTING CONDITION:
Currently the water fixtures such as water closets, urinals and lavatories utilized at the
Alaska SeaLife Center are not low volume, low flow devices. Presently the water closets
require 3.5 gallons of water per flush and the lavatories have a flow rate of 1 gallon per
minute.
PROPOSED FACILITY IMPROVEMENT MEASURE:
Change out fixture or fixture components to bring them in line with current low flow
standards. This upgrade will include replacing 35 water closets, 6 urinals and installing
low flow aerators for 28 lavatories. The new water closets will use 1.6 gallons of water
per flush and the new lavatories will use 0.5 gallons of water per minute.
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DETAILED INVESTMENT GRADE AUDIT SI FF F
& ENERGY SERVICES PROPOSAL
ASSUMPTIONS:
Values used to calculate stipulated savings were arrived to and agreed upon by SIEMENS
and Alaska SeaLife Center. Annual use is shown in Table 19. The number of uses comes
from a combination of visitor and staff estimates. Numbers for visitor use is based on
2009 visitor statistics, one flush and two hand washes per visitor. Staff calculations are
2.5 flushes for 90 employees for 200 working days per year and twice as many hand
washes. Use for the lavatory assumes 30 seconds of washing at a flow rate of 1 gpm to
be reduced 0.5 gpm.
Table 19
Fixture Type and Annual Use
Fixture Type
Pre -Water Volume per
Use al
Post -Water Volume per
Use al
Number of Uses
Annual
Use al
Toilets
3.5
1.6
200,000
380,000
Lavatories
0.50
0.25
400,000
100,000
SAVINGS CALCULATIONS:
Energy savings for water conservation are based on the difference between the baseline
water use and the retrofit water use. The difference between the gallons per flush for the
toilets and the gallons per minute for the lavatories is applied to the baseline number of
flushes and the number of hand washes. The baseline water usage is modeled using data
collected during the site survey and discussions with Alaska SeaLife Center personnel.
The post retrofit water usage is modeled using the baseline data and the new volumes
and flows agreed upon by SIEMENS and Alaska SeaLife Center.
FIM 4.00 Building Automation System Upgrade
Total Electric and Fuel Oil Savings are broken out below as part of Building
Automation System FIMs 4.03, 4.04, and 4.06.
FACILITIES INCLUDED UNDER THIS MEASURE:
Entire facility.
EXISTING CONDITION:
The Alaska SeaLife Center has been struggling with the existing obsolete building
automation system for years. Outdated and unsupported hardware and software have
resulted in much of the facilities existing control system being overridden and operated
in a manual fashion. This has enabled the facility operators keep the building somewhat
comfortable, but ultimately this FIM will capture the tremendous efficiencies possible
with a functional and properly programmed building automation system.
In addition, several different types of controls systems are currently installed throughout
the ASLC facility. The control systems operate in a stand-alone fashion and do not
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& ENERGY SERVICES PROPOSAL
communicate with each other. Therefore the facility is not functioning as an interactive
whole — for example the boiler systems and air -handler systems operate autonomously at
this time.
Also the motor controls for select fans are currently being operated through the obsolete
Cutler -Hammer IMPACC electrical system. The existing control system must interface
with IMPACC system to control major fan motors. This is intended to be achieved
through "smart" Advantage starters. These starters fail intermittently and the 1C9
interface has never communicated correctly with the motor starter system. The IMPACC
hardware and software are now difficult, if not impossible, to maintain and operate so
many motor starters are overridden and run continuously.
PROPOSED FACILITY IMPROVEMENT MEASURE:
A new master Siemens APOGEE Insight building automation system (BAS) will be
provided. This system is intended to allow operators complete supervisory control and
monitoring capabilities of the HVAC systems. In addition, this will integrate many of the
disparate systems together, reuse what is salvageable, and replace the control
components that cannot be incorporated into the APOGEE system.
This measure will include replacing the two existing NCM field panels in the control room
with a new PXCM controller that will integrate to the existing JCI N2 unitary controllers
currently networked through this panel. This will enable the ASLC to monitor and control
all existing N2 devices from the new Insight BAS server. As part of this upgrade Siemens
will reuse all existing N2 controllers and their associated control devices. It is Siemens'
intent to reuse all temperature sensors, valves, dampers actuators, relays, etc.
Siemens will also provide a new server and operator workstation for the new graphical
APOGEE Insight Advanced software with APOGEE Go and RENO options, and a laptop for
remotely accessing the system. Two concurrent site licenses will be provided. Normally
this would completely replace the JCI Metasys server, however ASLC can elect to have
this old user interface remain if it is their only access point for other 3rd party equipment.
This upgrade will add the ability to monitor seven life support relays that currently alarm
locally at abasement wall cabinet. Four new CO2 sensors for outside air reset of two air -
handling units will be provided and one new outside air CO2 sensor to be mounted in the
outside air intake of an air -handler (preferably opposite the ocean). Also a total of four
new uninterrupted power supplies will be added — one for each new PXCM field panel
and desktop computer.
In order to better control ASLC's slab heating, new BAS controls will be added to
automate one zone of slab heat that is currently running wildly. Siemens will add a new
strap -on return water temperature sensor for each of the existing 10 slab heat zones.
The new sensors will be wired to spare slots on the each zone's respective existing N2
controller. A new exterior rain & snow sensor will be provided to control operation of all
slab heat to reduce the heating run time of the system. The goal is to engage the BAS to
maximize efficiencies lost by running slab heating manually.
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Alaska 5eaLife Center
rrrs,
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DETAILED INVESTMENT GRADE AUDITS
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Siemens APOGEE will replace the existing Reliable control system currently controlling
the central heat plant equipment. Where the system has been bypassed, Siemens will
reestablish connections to the BAS for efficient control of these heating systems. All end
devices except analog temperature sensors will be reused. This upgrade will also replace
the existing electric control devices currently controlling the domestic hot water
equipment with BAS system compatible components to reestablish connections for
efficient control of this system.
During this BAS upgrade, Siemens will optimize the HVAC system's sequence of operation
wherever possible to utilize day/night setbacks, outside air and supply temperature
resets, motor scheduling, and other measures described by FIMs 4.03, 4.04 and 4.06
below. Siemens will include 40 hours of on -site customer training.
Lastly, in order to fully control the ASLC`s ventilation system, Siemens will need to replace
the motor controls for select fans currently connected to the obsolete Cutler -Hammer
IMPACC electrical system. Siemens APOGEE BAS will need to control these motors
directly if they are to be controlled efficiently. This FIM would require that eleven of the
existing Advantage starters be replaced with external motor starters that can be easily
controlled by the Siemens BAS via a low voltage contactor. Each starter will be wired to a
spare digital output (DO) on an existing N2 controller nearby.
In addition to the benefits of a functional BAS, this FIM will include a water and air
balance of the current HVAC system. The airside ventilation system has never been
balanced correctly and does not operate well. There is evidence that some of the system
inefficiencies could be due to insufficient air flow in some areas of the facility. A water
balance will ensure that the zone hydronic heaters have full design flow through their
heating elements. Balancing the HVAC system will help ensure it operates in a manner
closer to the original design intent.
ASSUMPTIONS:
This scope of work is based on the existing JCI drawings dated 516/98, Reliable drawings
dated 814103, original electrical and mechanical schedules, and multiple site visits during
the last year. We assume that all mechanical systems are in good working order prior to
this scope of work being initiated. ASLC personnel have agreed to correct any known or
discovered deficiencies that would prevent the optimal operation of the new BAS system
in a prompt manner. In addition, Siemens assumes that existing variable frequency
drives (manufactured by Cutler -Hammer and JCI) are fully operational so they can be
reconfigured to be controlled by the Siemens BAS.
This scope excludes work with the other existing buildings systems such as the Card Key
access control system, Notifier fire alarm system, and CCTV system. These systems will
remain separated from the BAS and remain accessible via their current operator
interfaces. No upgrades will be performed on these systems underthis FIM.
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DETAILED INVESTMENT GRADE AUDIT SI EMI EN!
& ENERGY SERVICES PROPOSAL
In addition all work associated with existing abandoned humidifiers is excluded and
Siemens plans on reusing all of the existing control dampers andlor smoke/fire dampers.
Existing control valves will be reused where practical. All motors receiving new motor
starters will be reused.
This FIM does not include formal, third -party commissioning. Instead all system start-up
and point-to-point check-out procedures will be completed per Siemens standard check-
list methodology.
SAVINGS CALCULATIONS:
For details on energy savings calculations, see individual Building Automation System
FIMs 4.03, 4.04, and 4.06.
FIM 4.03 Night Setback Control
Electric Savings: 252,892 kWh
0 kW
$16,463
Fuel Oil Savings: 0 Gallons
$0
Total $ Savings: $16,463
AREAS INCLUDED UNDER THIS MEASURE:
• Lobby 103
• Pre/Post Op 146
• Necropsy 147
• Surgery 145
• Food Prep 143
• Dry Lab 144
• Dry Lab 152
• Special Lab 155
• Special Lab 156
• Chemical Storage 157
• Dark Room 158
• Central Dry Lab 159
• Corridor 141
• Dry Lab 162
• Dry Lab 163
• Office 201
• Gallery 222
EXISTING CONDITION:
Currently the system operates 24 hours daily and 7 days a week to maintain a
temperature set point of 70°F during heating season. Even though the building has _a
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_ & ENERGY SERVICES PROPOSAL
BAS, it is not being actively used to manage space temperature set points. The space
temperatures can be set back to a lower temperature setting between the hours of
6:00pm to 6:00am, seven days a week.
PROPOSED FACILITY IMPROVEMENT MEASURE:
Program the proposed new DDC system to implement Night Temperature Setback during
heating period. The operating costs will be reduced by lowering the set point for heating
(setback) to 60°F during unoccupied times. We are proposing night setback strategy for
the following AHUs' reheat coils: 2A, 2B, 4, & 5.
ASSUMPTIONS:
The spaces included in the proposed night setback are assumed to be areas that can be
setback. Currently the unoccupied and occupied space temperatures are the same and
assumed to be 70OF as observed from return air temperature trends.
A temperature for outside air of 550F was used as the point when no heating would be
needed from the reheat coils. This was determined from the mechanical schedules and
the load profiles. ASHRAE Heating Design Temperature for Seward, AK is 7.1°F and was
used to derive a linear equation for the required heat load with respect to outside air
temperature.
Heating capacities for each reheat coil were taken from the provided mechanical
schedules and are shown in Table 20 below:
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r& ENERGY SERVICES PROPOSAL
'4:
Table 20
Reheat rnilc that ara nrnnncarl fnr ninht catharkc
Coil
Designation
AHU Air
Stream
Location Served
Heating
Capacity
(MBH)
Air Flow (CFM)
Air Temperature
F
Max
Min
In
Out
HC-6
2A28
Pre/Post Op 146
8.1
300
55
80
HC-7
2A2B
Necropsy 147
21.6
800
55
80
HC-8
2A/2B
Surgery 145
35.4
1310
55
80
HC-9
4
Food Prep. 143
6.8
250
55
80
HC-10
4
Dry Lab 144
22.8
844
55
80
HCA 1
4
Dry Lab 152
22.8
844
55
80
HC-17
4
Corridor 141
17.8
660
55
80
HC-18
4
Dry Lab 162
22.8
844
55
80
HC-19
4
Dry Lab 163
22.8
844
55
80
HC-12
4
Special Lab 155
227
840
55
80
HC-13
4
Special Lab 156
4.9
180
55
80
HC-14
4
Chemical Storage 157
4.1
150
55
80
HCA5
4
Dark Room 158
4.9
180
55
80
HC-16
4
Central Dry Lab 159
33.8
1250
55
80
HCA
5
Lobby 103
170
7000
5250
55
80
HC-20
5
Office 201
11.9
880
440
55
80
HC-21
5
Gallery 222
18.4
2100 1050
1 55
80
Current space temperature set -points applied in the savings calculation are listed in Table
21.
Table 21
Current Snare Temnerature Set -point (OF)
Heating _
Occupied
Cooling
Occupied
Cooling
Unoccupied
Unoccu ied
70
70
1 N•A
NIA
The following space temperature setup and setback are applied to the energy savings
calculations (Table 22).
Table 22
Proposed Soace Temnerature Set -point (°F)
Heating
Occupied
Heating
Unoccupied
Cooling
Occupied
Cooling
Unoccupied
70
60
NIA
WA
The following space occupancy schedules will be applied to the energy savings
calculations (Table 23).
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0 & ENERGY SERVICES PROPOSAL
Table 23
Occu anc Schedules
Occupied
Unoccupied
6:OOAM - 6:OOPM
6:OOPM 6:OOAM
SAVINGS CALCULATIONS:
Night setback saving were calculated based on the outside air heating design point, the
outside air temperature at which no heating is required, and the occupied and
unoccupied space temperatures. The percent temperature difference was determined
and then applied as a reduction to the linear equation determined for the heating load
with respect to outside air temperature.
FIM 4.04 Demand Control Ventilation
Electric Savings: 65,892 kWh
70 kW
$5,109
Fuel Oil Savings: 0 Gallons
$0
Total $ Savings: $5,109
FACILITIES INCLUDED UNDER THIS MEASURE:
• AHU-5
• AHU-6
EXISTING CONDITION:
AHU-5 is a single duct, variable air volume system serving office and exhibit areas.
-- - - -Currently f#reunit opeiates and- mwklesA0*to-6096outside- ventilation -
regardless of the occupancy level. Supply air temperature was kept between 560F and
64'F during data logging.
AHU-6 is a single duct, variable air volume system serving office and exhibit areas.
Currently the unit operates continuously and provides 50% to 75% outside air ventilation
regardless of the occupancy level. Supply air temperature was kept between 46OF and
60OF during data logging.
PROPOSED FACILITY IMPROVEMENT MEASURE:
Implement Demand Control Ventilation strategy to AHU-5 and AHU-6. Demand Control
Ventilation (DCV) is a control strategy that adjusts the amount of supply outside air based
on the ventilation demands of the occupants. The ventilation airflow is determined by
comparing the CO2 concentration of return air and the outside air. Return air CO2
concentration will be measured at two locations for each of the AHUs: one at office area
common return and the other at visitor area common return. The ventilation airflow will
be modulated to keep the difference between outside air CO2 concentration and higher
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of the two return air CO2 concentration (office or visitor area) to less than or equal to 700
ppm. This will provide just the right amount of ventilation to the occupied space thus
reducing the energy consumption and improve the indoor air quality.
ASSUMPTIONS:
Required ventilation rate was estimated based on the maximum number of occupants in
each of the AHU service area. Number of occupants in the building was gathered from
facility survey (Table 24).
Table 24
Maximum Hourly Number of Occupants in Office and Visitor Areas
Office Workers
Visitors Summer
Visitors Winter
35
220
25
All of the office and visitor exhibit area is served by AHU-5 and AHU-6. Number of
occupants in each unit service area was estimated based on the square footage covered
by each of the AHUs (Table 25).
Table 25
Number of Occuoants in AHU-5 and AHU-6 Service Area
Ratio of Scqlare Footage
Maximum Number of Occupants
AHU-6
AHU-6
AHU-6
AHU-6
Office Area
85%
15%
30
5
Visitor Area -Summer
57%
I
43%
126
94
Visitor Area - Winter
14
11
Occupancy schedules of office workers and visitors were given by facility staff and listed
in Table 26.
Table 26
OccuDancv Schedule
Office 1 8:00 AM - 6.00 PM
Visitor - Summer Ma 1 - October 1 8:30 AM - 6:30 PM
Visitor - Winter 10:00 AM - 5:00 PM
The hourly occupancy level profile for each AHU service area was generated based on the
above assumptions and listed in Table 27. The proposed ventilation rate was estimated
based on the number of the occupants in the space and 20 cfm of ventilation per person.
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Table 27
Hourly Occupanev Level (Number of Occupants)
Office
Visitors Summer
Visitors Winter
Hour
AHU-6
AHU-6
AHU-5
AHU-6
AHU5
AHU-6
0
0
0
0
0
0
0
1
0
0
0
0
0
0
2
0
0
0
0
0
0
3
0
0
0
0
0
0
4
0
0
0
0
0
0
5
0
0
0
0
0
0
6
3
1
0
0
0
0
7
9
2
0
0
0
0
8
30
5
63
47
0
0
9
30
5
101
75
0
0
10
1 30
5
126
94
7
6
11
30
5
126
94
14
11
12
30
5
126
94
14
11
13
30
5
126
94
14
11
14
30
5
126
94
14
11
15
30
5
126
94
14
11
16
30
5
126
94
14
11
17
30
5
126
94
0
0
18
9
2
63
47
0
0
19
0
0
0
0
0
0
20
0
0
0
0
0
0
21
0
0
0
0
0
0
22
0
0
0
0
0
0
23
0
0
1 0
0
0
0
SAVINGS CALCULATIONS:
Energy savings from this measure is calculated by applying the proposed ventilation cfm
schedules to the individual AHU energy models. Mixed air temperature was calculated
based on the outside air ventilation rate, outside air temperature, and return air
temperature. Supply fan airflow was calculated based on the supply fan electrical load
profile created. Supply airflow, mixed air temperature, and observed supply air
temperatures were used to calculate the post retrofit heating load by each of the unit.
The load was shifted from the Boilers to the Sea Water Heat Pumps during the baseline
modification.
FIM 4.06 Slab Heat Control Optimization
Electric Savings: 389,237 kWh
0 kW
$25,339
Fuel Oil Savings: 0 Gallons
$0
Total $ Savings: $25,339
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AREAS INCLUDED UNDERTHIS MEASURE:
• Slab Heat
EXISTING CONDITION:
Currently the slab heat is manually enabled when the weather changes to winter
conditions. Once it is turned on the system operates 24 hours daily and 7 days a week.
Once the weather conditions become favorable the slab heat is manually disabled.
PROPOSED FACILITY IMPROVEMENT MEASURE:
Program the proposed new DDC system to operate the slab heat when weather
conditions call for it. The operating costs will be reduced by limiting the time that the
slab heat operates to times when the outside air temperature is equal to or below 320F
and the outside air relative humidity is above 80%. Upon being enabled the slab heat will
operate a minimum of 6 hours.
ASSUMPTIONS:
The baseline year weather data was used to calculate the number of hours that the slab
heat would operate. Outside air temperature should be equal to or less then 32°F and the
relative humidity should be equal to or greater than 80%for the slab heat to be activated.
It is assumed that the slab heat will operate for a minimum of 6 hours upon being
activated.
SAVINGS CALCULATIONS:
Slab heat control optimization savings for fuel oil and electricity were calculated by
determining the hours that the outside air temperature and relative humidity meet the
requirements for operation. The load profile for slab heat and outside air temperature
was then used to determine the load for the operable hours. Pumping power calculated
for the constant volume circulation pump was then applied to the operable hours.
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FIMs Considered for Recommendation but Excluded
During the project development other Facility Improvement Measures were considered
but because of the economic impact determined from the energy analysis and
implementation costs they are not recommended as part of this study. These included
the following:
• LED Lighting Upgrades
• Optimization of Existing Air Handler - Air to Air Heat Exchanger
• Installation of Heat Recovery on Air Handlers 1, 2A1B, 4 & 7
• Upgrade Existing Boiler Combustion Controls
• Installation of Oxygen Trim to Existing Boiler Controls
• Installation of VFDs on Six Circulating Pumps for the Life Support Pools
• Hydronic Flush of Heating System
• Security System Upgrade
• Fire Alarm System Upgrade
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Section IV - Measurement and Verification
Facility energy savings are determined by comparing the energy use before and after the
installation of energy conservation measures. The "before" case is called the baseline; the
"after" case is referred to as the post -installation or performance period. Proper
determination of savings includes adjusting for changes that affect energy use but that
are not caused by the conservation measures. Such adjustments may account for
differences in weather and occupancy conditions between the baseline and performance
periods. In general, baseline and post -installation energy use can be determined using
the methods associated with several different M&V approaches. These approaches are
termed M&V Options A, B, C, and D. A range of options is available to provide suitable
techniques for a variety of applications.
Measurement and Verification Options
There are four guarantee options to measure and verify savings:
Option A — Measured Capacity
Option B — Measured Consumption
Option C — Main Meter Comparison
Option D — Designated based on Simulation or Calculation
Option A — Measured Capacity. This approach is intended for Facility Improvement
Measures where, with a one-time measurement for specific equipment or system's
instantaneous Baseline energy use, and a one-time measurement for specific equipment
or system's instantaneous post -implementation, (Post) energy use can be measured.
Baseline and Post energy consumption is calculated by multiplying the measured end use
instantaneous capacity (i.e. kW, Gallhr, BTUIhr) by estimated hours of operation for each
mode of operation (i.e. hours, week, month).
Option B — Measured Consumption. This approach is intended for Facility Improvement
Measures where continuous periodic measurements for specific equipment or system's
baseline energy use, and continuous periodic measurements for that equipment or
systems post -implementation (Post) energy use can be measured. Periodic inspections
and consumption measurements of the equipment or systems will be necessary to verify
the on -going efficient operation of the equipment and saving attainment.
Option C — Main Meter Comparison. This approach is intended for measurements of the
whole -facility or specific meter baseline energy use, and measurements of whole -facility
or specific meter post -implementation (Post) energy use can be measured. Periodic
inspections of baseline energy usage, operating practices, and facility and equipment,
and meter measurements of the will be necessary to verify the on -going efficient
operation of the equipment, systems, practices and facility, and saving attainment.
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Option D — Designated based on Simulation or Calculation. This approach is intended
for Facility Improvement Measures where the end use capacity or operational efficiency,
demand, energy consumption or power level or manufacturer's measurements, industry
standard efficiencies or operating hours are known in advance, and used in a calculation
or analysis method that will estimate the outcome. Both CLIENT and SIEMENS agree to
the estimate inputs and outcome(s) of the analysis methodology. Based on the
established analytical methodology, the savings estimated will be achieved upon
completion of the Facility Improvement Measures Work and that no further
measurements or calculations will need to be performed. The methodology and
calculations to establish savings value will be defined in this Measurement and
Verification Section.
Measurement and Verification Plan
Table 28 summarizes the Measurement and Verification options for each of the proposed
FIMs.
Table 28
Measurement and Verification Options by FIMs
FIM#
FIM Description
M&V
Option
1.00
Lighting Upgrades
A
1.01
Lighting Controls
A
2.00
Water Conservation
A
4.03
Night Setback Control
B
4.04
Demand Control ventilation
B
4.06
1 Slab Heat Control Optimization
I B
Option -A — Measured Capacity
FIM 1.00 Lighting Upgrades
During the pre -installation, study measurements were taken on 7 lighting circuits to
characterize the power consumption of various lamp types. In order to optimize the
amount of data measured, the most prevalent fixture types were measured. Table 29
identifies the locations of those 7 circuits and their respective physical locations. During
the post retrofit M&V phase of the project, electrical circuit measurements will be taken
at the exact same locations. This will quantify the electrical demand savings due to
lighting upgrades.
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Table 29
Location of Pre and Post Retrofit
Reading #
Room #
Room Type
Panel #
Panel Location
1
009
Private Office
BHD From J Box
Corridor 002 / ILC 101
2
010
Mechanical Room
BHD From J Box
Corridor 002 / ILC 101
3
010
Mechanical Room
BHD From J Box
Corridor= / ILC 101
4
219
Open Office
ZHB one 25
Corridor 220 / LP 207
5
236
Gallery
2LG1 29
Corridor 227 / LP 208
6
236
Gallery
2LG1 31
Corridor 227 / LP 208
7
236
Gallery
2LG1 30
Corridor 227 / LP 208
FIM 1.01 Lighting Controls
During the pre -installation study Watt Stopper data loggers were installed in 10 different
locations for a period greater than 7 days to identify the savings associated with lighting
controls. The 10 locations represent different space types namely: conference room,
corridor, laboratory, mechanical room, private office, public restroom, and staff
restroom. The reduction in the number of burn hours per year was calculated based on
the data collected by the Watt Stoppers. This reduction in burn hours was applied to the
different area types to calculate annual savings. Table 30 identifies the location of the 10
spaces where Watt Stoppers were installed.
Table 30
Watt Stopper Installation Locations
Sensor #
Area Type
Room #
1
Conference Room
270
2
Corridor
002
3
Corridor
220
159
_ _
4 i Laboratory
5
Laboratory
152
S
Ailechanical-Ro=
AID
7
Private Office
207
8
Private Office
234
9
Public Restroom
211
10
Staff Restroom
217
This FIM does not require any additional monitoring during the post installation M&V
phase because the reduction in the number of hours of operation remain the same as
calculated during the pre installation measurement. The reduction in the number of
hours due to lighting controls, by space type, is identified in Table 31,
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Table 31
Reduction in the Number of Hours
Codes
Area Type
Current Annual Hours
Reduction in Annual Hours
BR
Break room
2600
1300
CL
Classroom
3244
811
DH
Dining Hall
3244
811
EX
Exits
8760
0
EXT
Exterior
4380
3285
HW
Hallway/Corridors
8760
6745
KN
Kitchen
3244
811
LO
Lobby
3244
0
ME
Mech/Elec. Room
8760
7008
MISC
Miscellaneous
3244
811
MR
Meeting Room
1026
410
00
Open Office
2600
0
PO
Private Office
1768
265
RR
Restroom
8760
7
ST
Storage Closet
500
400
WA
Work Area
7236
6430
DAL
Direct Aquarium
LightingUghting
3244
0
PHW
Private Corridor
3588
574
PRR
Private Restroom
1352
703
STR
Stairwell
8760
6570
FIM 2.00 Water Conservation
Alaska Sea Life Center has water fixtures such as water closets, urinals, and lavatories that
are not low volume, low flow devices. Values used to calculate stipulated savings were
arrived to and agreed upon by SIEMENS and Alaska SeaLife Center. Annual use is shown
in Table 32.
Table 32
Fixture TVDe and Annual Use
Fixture Type I Pre -Water Volume per
Use al
Post -Water Volume per
Use al
Number of Uses
Annual
Use I
Toilets
3.5
1.6
200,000
380,000
Lavatories 0.50
0.25
400,000
100,000
There will not be any post installation measurements completed on the water fixtures.
Post installation usage will be based on Manufacturer's specifications. In addition to the
required commissioning of the project a visual verification will be done of 10% of the
replacements to insure that replacements have occurred.
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Option-B — Measured Consumption
FIM 4.03 Night Setback Control
The building presently has a constant space temperature set point of 70°F. It is proposed
that the space set points will be adjusted during the heating season as represented in
Table 33.
Table 33
Proposed Space Temperature Set points
Occupied Hours
Temperature Set -Points
6:00 am to 6:00 pm
70"F
6:00 pm to 6:00 am
60°F
Energy savings associated with the implementation of this FIM will be verified by
trending the space temperatures, and space temperature setpoints for the following
zones served by AHU-2, AHU-4 and AHU-5. Table 34 lists the 17 space temperature and
17 space temperature set points will be trended and recorded on a15-minute interval.
The recorded space temperatures will be reviewed to verify correct operation and proper
ongoing setbacks.
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Table 34
FIM 4.01 M&V Points List
Heating Coil Serving Space
M&V Point
Variable
HC-1
1
Lobby 103 — Temp set point
HCA
2
Lobby 103 —Space Temp
HC-6
3
Pre/Post OP 146 — Temp set point
HC-6
4
Pre/Post OP 146 — Space Temp
HC-7
5
Necropsy 147—Temp set point
HC-7
6
Necropsy 147 — Space Temp
HC-8
7
Surgery 145 —Temp set point
HC-8
8
Surgery 145 — Space Temp
HC-9
9
Food Prep 143 — Temp set point
HC-9
10
Food Prep 143 — Space Temp
HC-10
11
Dry Lab 144 — Temp set point
HCA 0
12
Dry Lab 144 — Space Temp
HCA 1
13
Dry Lab 152 — Temp set point
HCA 1
14
Dry Lab 152 — Space Temp
HC-12
15
Special Lab 155 — Temp set point
HC-12
16
Special Lab 155 — Space Temp
HC-13
17
Special Lab 156 — Temp set point
HC-13
18
Special Lab 156 — Space Temp
HC-14
19
Chemical Storage 157 — Temp set point
HC-14
20
Chemical Storage 157 — Space Temp
HC-15
21
Dark Room 158—Temp set point
HCA 5
22
Dark Room 158 — Space Temp
HC-16
23
Central Dry Lab 159 — Temp set point
HC-16
24
Central Dry Lab 159 — Space Temp
HC-17
25
Corridor 141 — Temp set point
HC-17
26
Corridor 141 — Space Temp
HO-18
27
Dry Lab 162 — Temp set point
MC-1-8
28 — -- —
-Off Lab, 462 —£peee Temp,
HC-19
29
Dry Lab 163 — Temp set point
HC-19
30
Dry Lab 163 — Space Temp
HC-20
31
Office 201 — Temp set point
HC-20
32
Office 201 — Space Temp
HC-21
33
Gallery 222 — Temp set point
HC-21
34
Gallery 222 — Space Temp
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FIM 4.04 Demand Control Ventilation
The operation of Demand Control Ventilation will be verified by monitoring variables
controlling the % outdoor air for AHU-5 and AHU-6. The ventilation control of the units
will be verified by trending the supply fan motor current, outside air temperature, return
air temperature, mixed air temperature, supply air temperature after the main AHU
heating coil and CO2 concentration (ppm) in outside air and interior air on a
continuous15-minute interval. The temperature measurements will be used to calculate
the percentage of outside air based on Equation 47.
OA% =
Equation 47
TAfixedArr—TReturnAir
Toutstde4ir — TRretumd r
The COa concentration difference between the outside air and return air shall be kept at
700 ppm during occupied hours.
Table 35 lists the 14 variables that will be monitored and trended every 15 minutes to
calculate savings.
Table 35
FIM 4.04 M&V Points List
M&V Point
Variable
1
Outside air temperature
2
Outside air CO2 concentration
3
AHU-5 Supply fan motor current
4
AHU5 Return air temperature
5
AHU-5 Mixed air temperature
6
AHU-5 Supply air temperature after heating coil
7
AHU-iirderfor air CO2 concerif rabo n -in ofte areas
8
AHU-5 interior air CO2 concentration in public areas
9
AHU-6 Supply fan motor current
10
AHU-6 Return air temperature
11
AHU-6 Mixed air temperature
12
AHU-6 Supply air temperature after heating coil
13
AHU-6 interior air CO2 concentration in office areas
14
AHU-6 interior air CO2 concentration in public areas
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FIM 4.06 Slab Heat Control Optimization
Energy savings associated with the implementation of this FIM will be verified by
monitoring of the supply and return water temperatures, the circulating pump motor
amperage, outside air temperature, outside air relative humidity, and all corresponding
set points on a continous15-minute interval. A onetime measurement of the true RMS
power consumption by the constant volume circulating pumps motor will be measured
for use in the measurement and verification calculations.
The yearly electrical consumption will be calculated by determining the number of hours
that the pump operates and multiplying by the measured pumping power.
The flow rate will be established based on the pump curves provided by the facility and is
pegged at 90 gpm for the slab heat. The supply and return temperatures, and the flow
will be used to calculate the radiant heating load (Equation 48).
Equation 48
BTUH = 500 x FlowL.,p x \Tsupply—TRehirn
The outside air temperature and outside air relative humidity will be used to verify that
the system is operating as intended and with respect to specified set points for initiation
of the systems as well as appropriate shut down. Table 36 lists the 4 variables that will be
monitored and trended every 15 minutes to calculate savings.
Table 36
FIM 4.06 M&V Points List
M&V Point
Variable
1
Outside Air Temperature
2
Outside Relative Humidity
3
Supply Water Temperature
4
Return Water Temperature
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Appendix I - Methodology / Utility Summary
A. Study Approach
In conducting a technical energy audit as a basis for a performance contract, it is
essential that the existing conditions be precisely established as a baseline for the
evaluation of any potential system improvements. Relevant factors were identified and
assessed through a systems approach in an effort to develop potential energy
improvement measures. The factors are outlined below:
1. Review of Facility Layout and Facilities
The initial step in the study entailed familiarization with the facility layouts as well as
a review of available drawings, and meetings with building operations personnel. The
HVAC, building characteristics, and plumbing systems were investigated.
2. Review of Systems Operation/Usage through System Trending
Since energy usage is dependent on how the facility is operated, it was necessary to
collect data on operating hours and utilization. The HVAC systems were data logged
between 12/1212009 and 01/04/2010 to aid in establishing the baseline energy
consumption. The monitored system includes the air handlers, hot water loops, and
boilers.
HVAC operating parameters, such as operation hours and ventilation airflows were
determined through investigation of the monitored data, sequence of operations,
and facility staff. The calculation methodologies for the determination of the
operating parameters are detailed in Section 11— Facility Descriptions.
3. Review of Systems Operation/Usage through Facility Personnel Survey
Other parameters that were used to define the baseline energy consumption include
the, 4�tpa cy sc4ecMes, equipment schecl le&, went sizes, -a d -space
temperatures based on the data logger analysis, the average space temperatures
were defined for occupied and unoccupied hours: the observed occupied hour
average space temperature is 70°F, and unoccupied hour average space temperature
is 707. The equipment sizes are listed in Section II — Existing Building Conditions.
4. Development of Facility Improvement Measures
Based on the field surveys, metered data and related calculations, the Facility
Improvement Measures (FIMs) were developed. The measures were analyzed to
determine their effect on the overall base energy consumption of each system
impacted. Additionally, each measure was reviewed in a costibenefit analysis.
5. Energy Usage Characteristics
The most recent energy consumption data available for Alaska SeaLife Center covers
October 2008 through September 2009 for electricity and fuel oil consumption. The
utility information was provided by Alaska SeaLife Center. Baseline energy
consumption is summarized in part D. Baseline Energy Consumption.
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B. Utilities Supply Description
Electricity, water, and sewer are provided by The City Seward. Fuel oil is provided by
Shoreside Petroleum, Inc.
C. Logger Data Analysis
Current operating conditions for the facility were studied through data logging of
different mechanical equipment. The results of the analysis are shown in Section II —
Facility Descriptions.
D. Baseline Energy Consumption
The Base Year for this project is defined as the period from October 1, 2008 through
September 30, 2009. The monthly consumptions for electricity, fuel oil, and water are
outlined in Table 37. Fuel oil consumption was normalized to monthly usage based on
the fuel oil delivery amount and date.
Table 37
Baseline Energy Consumption
(Fleetrieitv_ Fuel Oil_ and Water)
Electric
Consumption
Electric Demand
Fuel Oil
Water
MON YR
kWh
kW
Gallons
Gallons
Oct-08
301,799
514
9,055
434,300
Nov-08
304,327
492
11,211
211,200
Dec-08
345,540
492
12,425
302,710
Jan-09
255,589
448
14,277
242,523
Feb-09
316,432
492
12,357
393,600
Mar-09
1 303,638
463
9,761
300,665
420,812
934
8 428
178,800
—Apr-09
M -09
293,988
809
0
317 226
Jun-09
472,644
sm
0
W m
JU-09
427,200
941
0
356,542
-09
439,887
802
0
869,600
�Se'-0
4436,254
864
0
1,173,097
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The hourly energy model was created to match the actual utility data by applying the
current facility operations, occupancy hours, and the actual outside air temperature data
for Seward Airport for the period of October 1, 2008 through September 30, 2009. The
energy model was tuned by making adjustments to match the fuel oil and electrical
consumption and demand profiles obtained from the utility bills Figure 39 through
Figure 41.
Gallons
16,000
14,000
12,000
10,000
8,000
6,000
4,000
2,000
0
Actual lgal) ii; Calculated lGal) `
Jan Feb Mar Apr May Jun Jul Aug Sep Oct Nov Dec
Figure 39 Fuel Oil Consumption Profile Match for Alaska Sea Life Center.
KW h Actual Calculated —•- Adjusted -HP Final -HP and FIMs
600,000
200,000 -
100,000
0
Jan Feb Mar Apr May Jun Jul Aug Sep Oct Nov Dec
Figure 40 Electrical Consumption Profile Match for Alaska Sea Life Center.
Please note: Actual KWh data shown is based on billing months, which have a varying
number of days from 27 to 36 per month.
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kW Calculated -Actual
1,000
S00 -
600
400
200
-A Adjusted -HP Final -HP and FIMs
0
Jan Feb Mar Apr May Jun Jul Aug Sep Oct Nov Dec
Figure 41 Electrical Demand Profile Match for Alaska SeaLife Center.
FIMs were calculated in an interactive manner for the facility. The savings for each FIM
was then determined by calculating the difference between each energy model for each
FIM.
E. Operational Baseline Costs
There are minimal savings to the Operational Baseline Costs which have been identified.
According to the ALSC facilities personnel, no reduction in staff would result from these
upgrades so no labor savings have been accounted for. The cash flow models apply
$3,500 in operational savings and this value was provided by the ASLC. This is intended
to account for the reduction in material costs associated with replacing old lighting
ballasts and lamps.
These savings will be continued through the first 3 years of this proposal to account for
the 3-year new lamp warranty period. After that time, the savings will be reduced to
reflect ballast material savings during years 4 and 5. After year 5 the ballasts will also be
out of warranty and so no operational savings are incorporated after that year.
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F. Unit Energy Costs and Annual Percentage Increase
Utility costs used for savings calculations will be based on the utility rate in effect for the
predominant bill or the utility rate in effect for the corresponding period of the Baseline
period, whichever is greater. The rate, in effect during the Baseline period, will be
designated the floor price.
An escalation rate of 5% per annual period will be applied to the floor rates. The
escalated floor rate will be compared to the utility rate in effect in each future annual
period, and the greater of the two will be applied to the actual utility savings occurring in
that annual period.
Electric Rate
Service Provider: City of Seward
Charges: Energy Rate: $0.0081 per kWh
CEA Fuel Adjustment Surcharge: $0.057 per kWh
Demand Rate: $11.69 per kW*
* Minimum demand charges are included in the ASLC industrial rate contract with the
City. These reoccurring monthly charges will not be modified by this energy proposal
and SIEMENS calculated electrical savings have been adjusted to account for this
limitation.
Fuel Oil
Service Provider:
Charges:
Water Rate
Service Provider:
C haxges-:
Sewer Rate
Service Provider:
Charges:
Shoreside Petroleum, Inc.
$2.851Gallon
City of Seward
$0.0036671Galion -
City of Seward
$0.002451Gallon
Siemens Industry, Inc. - 80 - Proprietary & Confidential
June 2011
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