IAQ, Total Energy Recovery,
Passive Dehumidification and
Chilled Beam Technologies
Corporate History
Founded in 1963, we are a
world-wide supplier of air
distribution, noise abatement,
and desiccant wheel products,
employing over 400 people in 5
manufacturing facilities in the
United States.
SEMCO was Acquired by the
FläktWoods Group in 2007
making the group the world’s
largest total energy recovery
systems manufacturer.
© SEMCO Incorporated 2
A Fläkt Woods Company
SEMCO is a FläktWoods Company
FläktWoods is a $1 Billion Global company
 We are the largest manufacturer of energy recovery systems
worldwide
 Every 5 minutes of every workday, an energy recovery system or
AHU is shipped globally
 Our energy recovery systems have saved our customers more than
$9 billion US over the past 20 years
 More than 840 trillion BTUs have been recovered
 Carbon emissions reduced by 48 million tons globally
 Every minute one of our fans is delivered
 More than 3,000,000 chilled beams and air diffusers are shipped
each year
© SEMCO Incorporated 3
A Fläkt Woods Company
SEMCO Commitment to R&D
 Ten major US patents involving desiccant wheels and systems
 Two ASHRAE Journal articles and eight ASHRAE papers
 Nine major research reports for the Department of Energy and twelve
major conference technical papers
 Over 30 laboratory TVOC or SF6 field commissioning reports
completed
 Managed largest indoor air quality investigation every completed on
school facilities
 Four major research studies investigating
desiccant carry-over in total energy wheels
 Chilled Beam and Pinnacle design guide
SEMCO 3A wheel media prior to face coating
© SEMCO Incorporated 4
A Fläkt Woods Company
Certified Air Test Laboratory
SEMCO is the only US manufacturer with an air test facility
certified to be in accordance with the ASHRAE 84 test standard
© SEMCO Incorporated 5
A Fläkt Woods Company
IAQ Research Data: What Engineers
Need to Know About Indoor
Environments
Why IAQ Is Often At Odds With Energy
Efficiency:
Adequate Continuous
Ventilation (IAQ)
Advanced
Dedicated
Outdoor Air
Systems (All)
Green Buildings
LEED Certification
Healthy Buildings
Proper
Humidity
Control
(Comfort, IAQ)
Energy Efficient,
Economical Operation
(IAQ, Greenhouse Gasses)
© SEMCO Incorporated 7
A Fläkt Woods Company
Department of Energy Sponsored IAQ
and Humidity Control Research Study
of School Facilities
- Largest school IAQ study
- Two year duration (1998 – 2000)
- Ten Schools Investigated
- Continuous monitoring
- Research Team
Dr. Charlene Bayer - Branch Head - The Georgia
Tech Research Institute
•
Dr. Sid Crow - Branch Head of Biology - Georgia
State University
•
Joby Schilling - Past Director of Facilities Fulton
County Schools
•
•
© SEMCO Incorporated 8
John Fischer - Director R&D SEMCO Inc.
A Fläkt Woods Company
School IAQ Deserves Special Attention:



Children’s bodies are still developing and are
more likely to be effected by indoor pollutants
 Asthma among children is up 49% since
1982
 Children are 3 times more likely to get colds
than adults
School facilities are more densely populated
than most other facilities, making it difficult for
HVAC systems to maintain a desirable IAQ
1996 GAO survey reports that 20% of all
schools reported IAQ problems
© SEMCO Incorporated 9
A Fläkt Woods Company
Schools Investigation



Breakdown:
 5 elementary Schools, 3 middle schools, 2 high
schools – all located in Georgia
Mechanical Design:
 5 conventional systems
 5 with dedicated outdoor air systems (DOAS),
providing continuous ventilation as per ASHRAE 62
and controlling space humidity
Equipment:
 Conventional: chilled water, DX, WS heat pumps
 3 schools with SEMCO dual wheel systems, 2 with
Active desiccant systems
© SEMCO Incorporated 10
A Fläkt Woods Company
Research Report: Summary of Available
School IAQ Research

Key Findings:
 Both continuous outdoor air ventilation and humidity control
required to avoid the majority of IAQ problems
 Humidity control is a key factor in many of the problems
experienced by schools
 Humidity linked to microbial problems
 Microbial growth linked to chemical contaminants

Paper available on the Web:
 www.ornl.gov/ORNL/BTC/iaq.pdf
 Or just ask SEMCO
© SEMCO Incorporated 11
A Fläkt Woods Company
Key Research Findings:
 Schools considered for the investigation were reported
to be the best schools in a given county
 All schools were thought to be designed and operated in
accordance with ASHRAE 62
 Only 30% of these schools actually complied with
ASHRAE 62 despite the fact that the county paid for a
system that would comply
 Only 10% of the conventional systems (i.e. fan coils and
heat pumps) were providing any outdoor air to the
school facilities (most had outdoor air dampers shut off)
 Comfort first – IAQ second!
© SEMCO Incorporated 12
A Fläkt Woods Company
Classroom Relative Humidity Recorded for
Conventional System (Typical)
100
Relative Humidity (%)
90
80
Potential
Microbial Growth
Above this Level
70
ASHRAE
Recommended
Maximum
60
50
TER Providing 15 CFM/Student
Continuously
40
12 AM
6 AM
12 PM
6 PM
12 AM
Time of Day
© SEMCO Incorporated 13
A Fläkt Woods Company
Excess Sensible Capacity Results in
Short Cycle Time and High Space
Humidity
Off-Cycle Cooling Coil Performance
Latent & Sensible Capacity (1000 Btu/h)
10
Cooling Coil Acts
as an Evaporative
Cooler
5
0
-5
Compressor
-10
0
10
20
30
40
50
Time (min)
Source: Hugh Henderson, 1998 ASHRAE IAQ 98 Paper
© SEMCO Incorporated 14
A Fläkt Woods Company
ASHRAE Standard 62 Ventilation
Recommendations:
 Recommends adequate outdoor air ventilation rates to be provided on
a continuous basis for occupied spaces.
 For schools this is a minimum of 10 cfm/person plus .12 cfm/sqft
of classroom (approximately 14 cfm/person)
 Must be increased to reflect ventilation effectiveness of the
distribution system (i.e. VAV, warm air supplied at ceiling, etc.)
 Recommends that space relative humidity be maintained below 65%
RH even during peak outdoor air dewpoint conditions.
 Results of IAQ investigation suggest that ASHRAE ventilation
recommendations are a bit too low.
© SEMCO Incorporated 15
A Fläkt Woods Company
Adequate and Continuous Ventilation is
Important for Healthy Buildings:
200
3500
3000
180
Conventional: Formaldehyde
5
2500
4
Desiccant Systems: TVOC
160
Desiccant Systems: Formaldehyde
140
Baseline "Sick" School: TVOC
5
2000
120
"Sick" School: Formaldehyde
5 CFM/Person of Outdoor Air
1500
6
9
80
6
6
TVOC Guideline
1000
100
60
10
16
40
16 13
500
Formaldehyde (ug/M3)
Concentration TVOC (ug/M3)
Conventional Systems: TVOC
20
Formaldehyde Guideline
0
0
X
E
A
P
Y
M
G
J
U
L
R
Schools Investigated
© SEMCO Incorporated 16
A Fläkt Woods Company
Formaldehyde is Suspected Carcinogen
© SEMCO Incorporated 17
A Fläkt Woods Company
Adequate and Continuous Ventilation is
Important to Productivity:
Ventilation Rates
Productivity Increase at Task Investigated
(CFM/Person)
Addition Problems
Typing
Proof reading
7.5 increased to 20
5%
5%
5%
7.5 increased to 60
7.5%
7.5%
7.5%
Source: Wargocki et.al., ASHRAE Indoor Air 2002
© SEMCO Incorporated 18
A Fläkt Woods Company
So Proper Ventilation Could Impact SAT
Scores:
 Georgia schools scored lowest in the nation,
yet.....
 The difference between lowest and the
national average is only about 5%!
© SEMCO Incorporated 19
A Fläkt Woods Company
Relative Cost to U.S. Business
Clear Economic Justification for
Providing Good IAQ
Employee Compensation
Total Health Expenditure
Private Health Insurance
Building Energy Cost
Source: Lawrence Berkeley National Laboratory Investigation
© SEMCO Incorporated 20
A Fläkt Woods Company
Key Research Findings: Limitations of
Demand Control Ventilation
 Challenge is that the most problematic pollutants are not
the bioeffluents generated by people in schools but
chemicals from markers, building products, cleaning
solutions, etc.
 CO2 generation from children much lower than adults
so control parameters must be changed (CO2 delta
lowered)
 Challenge to deliver correct quantity of outdoor air to
each zone with VAV system – ASHRAE requires
increase in outdoor air to AHU to address this but it is
often ignored
 With effective recovery, a simple time clock is effective
© SEMCO Incorporated 21
A Fläkt Woods Company
Research Provides CO2 Factors for
Accurately Determining Ventilation
Rate:
Vo = 8,800/(Cs – Co) (elementary/middle)
or
Vo = 11,500/(Cs – Co) (high school)
Where:
 Vo = outdoor airflow rate in CFM per student
 Cs = steady state CO2 concentration in space (PPM)
 Co = steady state CO2 concentration in outdoor air (PPM)
© SEMCO Incorporated 22
A Fläkt Woods Company
Key Research Findings:
 Outdoor air ventilation key to IAQ, comfort and thereby
the learning process (chemical and
microbial/bacteriological contaminants)
 Filter maintenance kills IAQ with conventional systems,
compromises outdoor air cfm/student. Simplifying filter
maintenance is critical.
 Air balancing and classroom over-crowding (common)
further compromises OA cfm/student
 Often only 8-10 cfm/student is recognized despite a
design for 15 cfm/student
© SEMCO Incorporated 23
A Fläkt Woods Company
Key Research Findings: Humidity
 Many hours with high latent and low sensible loads
(part load conditions) creates problems for
conventional approaches
 More latent that previously thought based on
research (12-20 grain delta on outdoor air volume)
 Space humidity spikes in morning and afternoon as
students enter and leave the building (increased
infiltration)
 Many teachers set thermostats low (ie. 68-70
degrees) since “students feel & learn better”
© SEMCO Incorporated 24
A Fläkt Woods Company
Humidity Control and Microbial Activity:
 ASHRAE 62 recommends that indoor relative humidity
levels be maintained below 65% to avoid potential
microbial problems
 Research has shown that microbial growth emits
VOCs and toxins
 Microbial problems can cause serious health problems
(asthma) and extremely costly to fix
 ASHRAE 55 Comfort Standard
© SEMCO Incorporated 25
A Fläkt Woods Company
Humidity Control is Important for Comfortable
and Healthy Buildings:
Control School Humidity
Levels to Limit:
Recommend Space Humidity Range
(Relative Humidity)
Source
10% 20% 30% 40% 50% 60% 70% 80% 90%
Respiratory Infections
Mold and Fungi Problems
Infectivity of Bacteria and Viruses
Formaldehyde Off-gassing
Asthma and Allergic Reactions
Comfort Complains
Perceived Air Quality Complaints
Book Damage in Libraries
Warpping of Hardwood Floors
4,6,7
2,8
2,5,8
1
8
3
3
9
9
(Gymnasium)
ASHRAE Recommend Range
(Standard 62-1999)
30% - 60% Relative Humidity
2
Source: May 2003 ASHRAE Journal Article “Report Card on Humidity Control”
© SEMCO Incorporated 26
A Fläkt Woods Company
Humidity Control Improved: Microbial
Problem Resolved
85.0
A103 Before
B101 Before
B301 Before
A103 After
B101 After
B301 After
80.0
Space Relative Humidity
75.0
70.0
65.0
60.0
55.0
50.0
45.0
40.0
35.0
12:00 AM
12:00 AM
12:00 AM
12:00 AM
12:00 AM
12:00 AM
12:00 AM
Time of day
© SEMCO Incorporated 27
A Fläkt Woods Company
130
120
ASHRAE Standard 55 Comfort Zone
110
100
68oF WB
90
80%
80
70%
70
60%
60
50%
50
40%
40
30%
30
Relative Humidity
66
68
(1)
Comfort Zone Suggested by Berglund
70
72
74
76
78
Dry Bulb Temperature (oF)
80
20
82
Humidity Ratio - Grains of Moisture Per Pound of Dry Air
Humidity Control is Important for Comfortable
and Healthy Buildings:
 Comfort influenced by both
temperature and humidity
 Two year school investigation
findings: 72.5o/64% vs. 75o/53%
 Trend shows to achieve comfort,
the supply temperature will be
dropped .65o/Degree dew-point
or .2 degrees/% RH
 Trend agrees well with ASHRAE
Humidity Handbook
Berglund ASHRAE article: Conditions for 90% thermal acceptability
Average cooling season space conditions from DOE investigation
for schools using conventional (non-desiccant) systems
Average cooling season space conditions from DOE investigation
for schools using non-conventional (desiccant) systems
Source: May 2003 ASHRAE Journal Article “Report Card on Humidity Control”
© SEMCO Incorporated 28
A Fläkt Woods Company
Solving Humidity Problem Resulted in Higher
Thermostat Settings by Occupants:
Typical Space Temperatures Before and Afer Revolution System Retrofit
(controlled by teachers vis thermostat in each room)
76.0
A103 Before
B101 Before
B301 Before
A103 After
B101 After
B301 After
75.0
Space Temperature
74.0
73.0
Average Space
Temperature
72.0
After Retrofit
72.8 degrees
71.0
Before Retrofit
70.4 degrees
70.0
69.0
68.0
12:00 AM
12:00 PM
12:00 AM
12:00 PM
12:00 AM
12:00 PM
12:00 AM
Time of day
Before (October) and After (May) with similar outdoor air temperature levels
© SEMCO Incorporated 29
A Fläkt Woods Company
35%
30%
25%
25
20
15
10
5
15%
10%
5%
Baltimore
Atlanta
Miami
0%
74
73
72
Therm ostat Setting
(Degrees F)
© SEMCO Incorporated 30
30
0
20%
71
70
ing)
Cooling Energy Increase
(with Drop in Thermostat Setting)
Typical School Facility:
(165,000 SqFt., 32% Outdoor Air)
Cooling Energy Increa
(with Drop in Thermostat S
Higher Thermostat Settings Result in Lower
Operating Costs:
45
40
A Fläkt Woods Company
Key Research Findings: Operation
 Supplying low dewpoint air (< 50 degrees) is required
to maintain space humidity with a DOAS – lower if
airflow is reduced from 15 cfm/student
 Unoccupied mode to control humidity is essential due
to high percentage of unoccupied hours
 SEMCO dual wheel system was found to provide the
best IAQ, humidity control and energy efficiency.
 DOE field test data on 2 year old system agreed well
with published data
© SEMCO Incorporated 31
A Fläkt Woods Company
Pinnacle System Addresses All Issues
Identified
© SEMCO Incorporated 32
A Fläkt Woods Company
Total Energy Recovery: What
Engineers Need to Know About
Desiccant Wheel Technologies
Dedicated Outdoor Air Systems (DOAS)
Economics:
Life Cycle Analysis: Dedicated Outdoor Air Systems
Packaged DX Indirect Gas Reheat
Chilled Water Hot Water Reheat
DX Cooling Condenser Reheat
Active Desiccant Cooling
2008 Energy Costs
($.085/KWH, $9.5/MM BTU)
Energy Wheel Cooling then Reheat
2005 Energy Costs
($.07/KWH, $7.5/MM BTU)
EPD Dual Wheel Recovery System
2001 Energy Costs
($.06/KWH, $4.5/MM BTU)
SEMCO Pinnacle System
$0
$200,000
$400,000
$600,000
$800,000 $1,000,000 $1,200,000
Life Cycle Operating Cost (20 Years)
© SEMCO Incorporated 34
A Fläkt Woods Company
SEMCO Primary Total Recovery Wheel
Markets









Research
Hospitals
Casinos
Large offices
Aircraft and
automotive painting
Schools and
Universities
Breweries
Pharmaceutical
Manufacturing
© SEMCO Incorporated 35
A Fläkt Woods Company
Technology Leader
 First to use molecular sieve desiccants to address
contaminant carry-over and serve laboratory market
 First to develop and offer a dual wheel energy
recovery system (SEMCO EPD)
 First to develop corrosion resistant, antimicrobial and
anti-stick wheel face coatings
 First to optimize energy recovery and low dew point
delivery - passive dehumidification wheel (Pinnacle)
 First to address purge efficiency in VAV
applications (Health and Safety Monitor)
 Many other patents and patents pending
© SEMCO Incorporated 36
A Fläkt Woods Company
How an Energy Wheel Works:
(cooling mode)
3. Outdoor Air
to Building
(Cooled and
Dehumidified)
4.
1. Fresh Outdoor
Air (Hot and Humid)
Exhaust Air
from Building
(Cool and
Dry)
6. Exhaust Air to Outdoors
(Heated and Humidified)
© SEMCO Incorporated 37
A Fläkt Woods Company
Big Differences in Total Energy Wheels
Fluted aluminum wheel with
molecular sieve coating
Plastic ribbons with silica gel
© SEMCO Incorporated 38
A Fläkt Woods Company
Key Features Important for Successful
Installations
 Ability to limit the transfer of exhaust air contaminants (chemicals
and particulate) from the exhaust to the supply airstream (crosscontamination)
 Fluted, laminar, self-cleaning transfer media to reduce maintenance
and to maintain a low pressure loss
 Permanent transfer media and maintenance-free institutional design
– not a replaceable “throw away” item
 Documented, consistent high total recovery performance over time.
 High latent capacity to reduce chiller capacity and avoid frost
formation
© SEMCO Incorporated 39
A Fläkt Woods Company
SEMCO Total Energy Recovery Wheel
(Substantially different from traditional commercial energy wheels)
•
3 angstrom molecular sieve wheel
technology for 20 years and has been
successfully applied to some of the
worlds most prestigious LEED,
hospitals and research facilities
•
3 angstrom molecular sieve coating has
the unique ability to transfer moisture
(dehumidify outdoor air) without
transferring a significant amount of
airborne chemical or biological
contaminants
•
Fluted wheel media structure allows
particulate to pass through without
plugging and media surface is treated
with an effective anti-stick coating
Wheel Transfer Media
3A Molecular Sieve Coating (10,000 X)
© SEMCO Incorporated 40
A Fläkt Woods Company
Georgia Tech Research Institute
Pollutant Carry-over Independent Research
 Desiccant materials other than a 3A molecular sieve have been
shown to transfer up to 50% of the airborne pollutants back to the
space – dramatically reducing the ventilation effectiveness
 SEMCO’s 3 angstrom molecular sieve coating was shown to limit
contaminant carry-over in in this research. Supporting independent
findings from previous laboratory studies and numerous
independent field investigations
 Limiting contaminant carry-over in energy wheels is important for all
applications since the transferred contaminants requires significantly
more outdoor air to reach the same indoor air quality as a system
using a wheel that does not transfer contaminants
© SEMCO Incorporated 41
A Fläkt Woods Company
Importance of the 3Å Molecular Sieve
(key to required ventilation effectiveness)
Acetaldehyde
Methanol
Silica Gel Wheel
Isopropyl Alcohol
MIBK
Acetaldehyde
Methanol
4A Molecular Sieve
Wheel
Isopropyl Alcohol
MIBK
Acetaldehyde
Methanol
SEMCO 3 Angstrom
Wheel
Isopropyl Alcohol
MIBK
0
10
20
30
40
50
60
70
Contaminant Transfer (%)
Source: Independent Georgia Tech Research Institute Investigation 1993, 1999
© SEMCO Incorporated 42
A Fläkt Woods Company
Contaminant Carryover Due to the Wrong
Desiccant Requires Far More Outdoor
Airflow to Reach ASHRAE 62 Compliance
3.5
ppm concentration
3.0
2.5
2.0
1.5
1.0
0.5
222
CFM
222
CFM
222
CFM
285
CFM
383
CFM
0.0
No Recovery
(outdoor air)
3Å wheel
Silica gel wheel
Silica gel wheel
Silica gel wheel
Source: DOE Sponsored Research Investigation
© SEMCO Incorporated 43
A Fläkt Woods Company
Limiting Cross-Contamination is
Both Healthier and Good Business
Sample Analysis:
Project location - St. Louis, Mo.
Airflow quantities - as per case 1 or 2
Energy costs - $.06/KWH electricity
$.45/therm gas
Hours of operation - continuous
Supply conditions - 55 deg. cooling
65 deg. heating
Cost per year to condition - $20,085
outdoor air without recovery
Case 1
Wheel efficiency
Case 1: SEMCO 3A Wheel, No Cross-Contamination
Exhaust Air 10,000 cfm
Contaminant Concentration
X
Supply Air 10,000 cfm
Contaminant Concentration
Space at
Contaminant
Concentration
X
0
Case 2
Case 2: Recovery Wheel with 15% Cross-Contamination
77%
75%
Wheel Pressure Loss
.77 inwg
.94 inwg
Energy Savings/Yr.
$13,484
Exhaust Air 11,800 cfm
Contaminant Concentration
$12,167
X
Energy cost of added
fan horsepower reqd.*
$1,418
$2,945
Net Energy Savings
$12,066
$9,222
Supply Air 11,800 cfm
Contaminant Concentration
Space at
Contaminant
Concentration
X
.1X
Annual energy Savings
Case #1 over Case #2
+31%
* Note that the energy for fan horsepower in Case 2 reflects
both the increased pressure drop and the increased airflow
© SEMCO Incorporated 44
A Fläkt Woods Company
An effective adjustable purge section
Supply
Air
Outside
Air
© SEMCO Incorporated 45
A portion of
the outside air
stream is
used to flush
out the
contaminated
return air still
contained in
the flutes of
the wheel
A Fläkt Woods Company
High Latent Recovery Key to Avoiding Frost
Formation and Providing Maximum Heating
Recovery
Frost Set Point Limits Recovery when Most
Needed Due to Unequal Sensible & Latent Performance
(84% sensible, 73% latent)
Full Recovery with SEMCO
Due to Equal Sensible & Latent Performance
(78% sensible, 78% latent)
52 Gr.
43 Gr.
31 Gr.
10 Gr.
15 deg.
Supply and exhaust conditions
with unequal latent and sensible
© SEMCO Incorporated 46
39
51
62
75 deg.
Supply and exhaust conditions
with equal latent and sensible
A Fläkt Woods Company
Active Chilled Beams
What are they?
How do they work?
Why use them?
LEED Program a Primary Driver
 Very energy efficient
 40-70% less primary air
 50-70% of the sensible cooling
delivered by water




Smaller AHU
Smaller fan
Improved Chiller COP
Great geothermal partner
 LEED/GSA/Funding
requirements
© SEMCO Incorporated 48
A Fläkt Woods Company
Chilled Beam Benefits
 Chilled Beams have been applied in Europe for more than 30 years
 Energy costs are significantly reduced over conventional systems
 Excellent ventilation air distribution (good IAQ), no condensate drain
 Smaller duct size when compared to VAV systems, reducing
interstitial space and overall building height
 Smaller air handling units, smaller plant rooms and overall motor
horsepower is reduced when compared to conventional systems
 Low sound power levels – meets stringent ANSI Standard S12.60
requiring background noise levels to be maintained below 35 decibels
 Higher temperature chilled water – increased chiller efficiency
 Allows the engineer to decouple latent and sensible loads effectively
– simultaneous temperature and humidity control
© SEMCO Incorporated 49
A Fläkt Woods Company
Fan Coil Units vs. Chilled Beams
 Require electrical connections and
high service cost
 Fans are inefficient and require
maintenance – high noise
 Filter maintenance – Carrier
recommends monthly filter
changes – at each unit
 Deep coils required to handle
latent load in space
 Condensate management and
microbial challenge
 Low cost but high maintenance
and energy consumption
 Helped significantly by Pinnacle
preconditioning
© SEMCO Incorporated 50
A Fläkt Woods Company
Types of Chilled Beams
Passive Beam
© SEMCO Incorporated 51
Active Beam
A Fläkt Woods Company
Active Chilled Beams
 Utilizes primary air (ideally all
outdoor air), through slots to
induce room air through coil
 Typical 1:2 to 1:5 induction
airflow ratio
 Low discharge velocity (40-80
fpm) eliminating occupant
draft due to the Coandă
effect
 Temperature regulation
accomplished by the change
in water flow and modification
of the induction rate
 Control is by Zone or Room
© SEMCO Incorporated 52
A Fläkt Woods Company
Active Chilled Beam Installation Methods
Primary air and chilled water connection
In drop ceiling grid
© SEMCO Incorporated 53
Exposed to room
Combination
A Fläkt Woods Company
Benefits Provided by SEMCO Chilled Beams
Flow Pattern Control (FPC)
• Vanes adjustable in 4
increments of 0/15/30/45°
• Unique combination of
Comfort Control and FPC
0/15/30/45°
© SEMCO Incorporated 54
A Fläkt Woods Company
Benefits Provided by SEMCO Chilled Beams
Flow Pattern Control (FPC)
15
15
15
15
15
15
• When higher air flows are needed
• Flow pattern can be adjusted
• Best comfort can be achieved
© SEMCO Incorporated 55
A Fläkt Woods Company
Comfort Control – Capacity Adjustment
• Field adjustable cooling
capacity output
• Easy adjustment lever
• Integrated airflow gauge
• NO TOOLS REQUIRED
© SEMCO Incorporated 56
A Fläkt Woods Company
Comfort Control – Flexible Air Distribution
• One/two way distribution
• Easy to change
5 l/s/m
15 l/s/m
50%
80%
© SEMCO Incorporated 57
20%
50%
0%
100%
A Fläkt Woods Company
Chilled Beam Risks
 Condensation
 Requires proper humidity control – lower than normal
supply air dew point conditions
 Condensate sensors employed to turn off chilled water if
condensation conditions are reached
 Drip or drain pans can be fitted to some beams
 Over-cooling space with primary air
 Need to consider both minimum and maximum cooling load
 Best to avoid the use of cold (< about 60 degF) primary air
especially if moderate supply dew points are used – be
careful with “High Capacity Beam” sales pitch
© SEMCO Incorporated 58
A Fläkt Woods Company
Avoid Primary Air Over-cooing (example)
Peak Sensible Condition: Typical Classroom
Option:1
Conventional
Option:2
Pinnacle
Lighting Sensible Load (BTU/hr)
People Peak Sensible Load (BTU/hr)
Envelope Peak Sensible Load (BTU/hr)
3585
7020
6632
3585
7020
6632
Total Peak Sensible Load (BTU/hr)
17236
17236
Space Latent Load (BTU/hr)
6240
6240
390
612
57 DegF
58 grains
390
353
65 Degf
47 Grains
11893
5344
3812
13425
Outdoor air Required (CFM)
Primary Air Required to Beams (CFM)
Primary air temperature
Primary air humidity
Primary air sensible provided (BTU/hr)
Beam sensible cooling provided (BTU/hr)
© SEMCO Incorporated 59
Comments
1.5 KW/Sqft
25 students and teacher
25 students, modest infiltration
Airflow a function of supply dewpoint
Conventional too much with air
Conventional too little with beam
A Fläkt Woods Company
Avoid Primary Air Over-cooing (example)
Part Load Sensible Condition: Typical Classroom
Option:1
Conventional
Option:2
Pinnacle
Lighting Sensible Load (BTU/hr)
People Peak Sensible Load (BTU/hr)
Envelope Peak Sensible Load (BTU/hr)
3585
270
3316
3585
270
3316
Total Peak Sensible Load (BTU/hr)
7171
7171
Space Latent Load (BTU/hr)
1440
1440
390
612
57 DegF
58 grains
390
353
65 Degf
47 Grains
11893
-4722
3812
3359
Outdoor air Required (CFM)
Primary Air Required to Beams (CFM)
Primary air temperature
Primary air humidity
Primary air sensible provided (BTU/hr)
Beam sensible cooling provided (BTU/hr)
© SEMCO Incorporated 60
Comments
1.5 KW/Sqft
teacher grading paper
teacher, modest infiltration
Airflow a function of supply dewpoint
Conventional caused over-cooling
A Fläkt Woods Company
Importance of Humidity Control
In a Chilled Beam Design
Question: Why have chilled
beams been an accepted
standard for years in
Europe but relatively
new to the US?
The Answer
Two Main Reasons:
1) Europe is way ahead of the US with regard to energy
efficiency
2) Legitimate concerns regarding condensation on the chilled
beam due to the much higher ambient humidity levels in the
US
 In much of Europe the outdoor air humidity is so low that infiltration
actually dehumidifies the space on a cooling design day
 Indoor humidity levels must be estimated correctly, maintained
effectively and lower than normal dew point air must be delivered
to recognize the potential energy savings
 Very significant energy savings are recognized with the
combination of chilled beams and Pinnacle
© SEMCO Incorporated 62
A Fläkt Woods Company
Reasons to Consider Chilled Beams and
Pinnacle for School Facilities
 Schools are built to last for 30+ years so minimizing energy costs
should be a top priority – provides an exceptional ROI
 Some states are mandating public schools attain LEED ratings –
maximum LEED points are obtained with Pinnacle and C Beams
 Ensures outdoor air is delivered to the occupied space (best IAQ)
and maintains ideal humidity control better than all other systems
– further reducing energy consumption
 Significantly reduces maintenance costs:
 No fans, filters or drain pans in the occupied space
 Reliable, low maintenance SEMCO total recovery wheels
 Single location for high efficiency filtration – keep school cleaner
© SEMCO Incorporated 63
A Fläkt Woods Company
Reasons to Consider Chilled Beams and
Pinnacle for School Facilities (2)
 The reduction in cooling tons due to the Pinnacle system means
fewer wells for geothermal systems – this cost reduction often
exceeds the cost of the Pinnacle system
 The integrated DDC controls standard with Pinnacle cost
significantly less than if provided by BAS contractor
 The ANSI Standard S12.6 and ASHRAE recommended
maximum sound power level of 35 dBA can be easily achieved
with the SEMCO chilled beam
 Both estimates and actual project data have shown the Pinnacle
with Chilled Beam combination to have the same or lower first
cost that less efficient conventional systems providing fewer
benefits
© SEMCO Incorporated 64
A Fläkt Woods Company
Decoupling Sensible and Latent Loads
 Chilled Beams are efficient
cooling devices and are designed
to handle the building sensible
load.
Chilled Beams only handle the
space sensible load
 Primary air system designed to
handle the ventilation air sensible
and latent load and, most
importantly, all internal latent loads
The Primary Air Handling Unit
must handle all internal latent
loads!
© SEMCO Incorporated 65
A Fläkt Woods Company
With Chilled Beams the Internal Latent
Loads MUST be Estimated Accurately
The latent load analyses must consider all of the following:
1. People. ASHRAE guidelines range from 105 Btu/h to 1090 Btu/h
per person. Most chilled beam applications will be around 200
Btu/h per person (offices, school classrooms).
2. Building Infiltration and Door Openings. ASHRAE Humidity
Control Design Guide indicates an average building has a
leakage rate of 0.3 cfm/sq. ft. of wind facing facade, (very tight
buildings at .1 cfm/sq.ft.) – door opening impact a function of
application but very high for schools
3. Building Permeance. Analyses have shown that building
permeance is approximately 10% of the infiltration value for a
typical building (small relative to other sources).
© SEMCO Incorporated 66
A Fläkt Woods Company
Latent Load Calculations
© SEMCO Incorporated 67
A Fläkt Woods Company
Chilled Beam Latent Load Analysis Tool
© SEMCO Incorporated 68
A Fläkt Woods Company
Design Conditions - Outdoors
When estimating indoor latent loads, outdoor design conditions
should always be based on ASHRAE 1% dehumidification design,
not the typical summer sensible design condition used to select
condensing units.
Example: Washington DC Cooling Design and Dehumidification Design as
shown in ASHRAE 2009 Fundamentals.
Cooling DB/MCWB
Station
Washington DC Reagan AP
0.4%
Evaporation WB/MCDB
1%
2%
0.4%
Dehumidification WB/MCDB
1%
0.4%
DB
MCWB
DB
MCWB
DB
MCWB WB
MCDB
WB MCWB
DP
94.3
76.0
91.7
75.2
89.2
73.9
89.1
77.5
76.0 136.0 83.3
Lexington, KY 91 74 89 73 86 72
78.6
87.3
HR
1%
MCDB
74 130 83
DP
HR
MCDB
74.8 130.8 82.2
72 124 81
Humidity contrast - 96 grains vs.124 grains – internal loads off by 90%
© SEMCO Incorporated 69
A Fläkt Woods Company
Calculate Primary Airflow
Stockholm Example
•
•
•
•
•
•
•
20,000 Sq. Ft. School Wing with tight construction
450 occupants
Ventilation requirement at 20 cfm per occupant = 9,000 cfm of outside air
Entering chilled water serving beams is 58 deg. F.
Space humidity maximum at 75 deg. F. - 55% RH (73 grains)
Traditional air handler selected to deliver 52 deg. F. (58 grains)
Latent load = 49,600 BTU/hr (peak humidity level is 80 grains)
89,450 BTU/hr = Primary airflow x 0.68 x (73 – 58)
Primary airflow required in Stockholm = 8,770 cfm
Conclusion: Primary airflow needed to control humidity is the same as
that required to ventilate the school in Stockholm
© SEMCO Incorporated 70
A Fläkt Woods Company
Calculate Primary Airflow
Lexington School Example
•
•
•
•
•
•
•
20,000 Sq. Ft. School Wing with tight construction
450 occupants
Ventilation requirement at 15 cfm per occupant = 6,750 cfm of outside air
Entering chilled water serving beams is 58 deg. F.
Space humidity maximum at 75 deg. F. - 55% RH (73 grains)
Traditional air handler selected to deliver 52 deg. F. (58 grains)
Latent load = 170,923 BTU/hr (peak humidity level is 124 grains)
170,923 BTU/hr = Primary airflow x 0.68 x (73 – 58)
Primary airflow required in Lexington Kentucky. = 16,760 cfm
Conclusions:
• Primary airflow is 2.5 times greater than the ventilation requirement.
• Energy efficiency advantage is eroded by increased primary airflow
• Cost savings in fan power, ductwork, and electrical service are lost.
• Over cooling the space is problematic due to the increased airflow
• Parasitic reheat may now be required due to the over cooling issue
© SEMCO Incorporated 71
A Fläkt Woods Company
Calculate Primary Airflow
Lexington School Example
Reducing the Supply Air Dew point
•
•
•
•
•
•
•
20,000 Sq. Ft. School Wing with tight construction
450 occupants
Ventilation requirement at 15 cfm per occupant = 6,750 cfm of outside air
Entering chilled water serving beams is 58 deg. F.
Space humidity maximum at 75 deg. F. - 55% RH (73 grains)
Pinnacle selected to deliver 45 deg. F. dew point (45 grains)
Latent load = 170,923 BTU/hr (peak humidity level is 124 grains)
170,923 BTU/hr = Primary airflow x 0.68 x (73 – 45)
Primary airflow required in Lexington Kentucky. = 8,977 cfm
Conclusions:
• Primary airflow is only 30% greater than the ventilation requirement.
• LEED projects design for 30% more outdoor air to get extra LEED point
• Significant fan energy and cooling ton savings over conventional
approach
© SEMCO Incorporated 72
A Fläkt Woods Company
Primary Air System Options
Primary system options:
(supply dew point is limited by
temperature off of the cooling
coil)
TE-WHEEL
EXHAUST AIR
RETURN AIR
OUTSIDE AIR
 Option 1: Conventional AHU (no
recovery)
SUPPLY AIR
COOLING HEATING
COIL
COIL
 Option 2: AHU with total energy
recovery
 Option 3: Dual wheel (SEMCO
EPD) – free reheat
© SEMCO Incorporated 73
A Fläkt Woods Company
Caution: Supply Dew Points are Limited
with EPD Approach
Big Problem –
condensation results
in humidification
Desired Performance
© SEMCO Incorporated 74
A Fläkt Woods Company
Primary Air System Options: Energy
Equipment Options
Dewpoint
Delivered
Latent Capacity
Delivered
Conventional Cooling
Capacity Required
Reheat
Required
Energy
% Baseline
Packaged Rooftop Gas Reheat
51 oF
42.5 Tons
75.8 Tons
166,100 btu/hr
100%
Chilled Water/Hot Water Reheat
51 oF
42.5 Tons
75.8 Tons
166,100 btu/hr
100%
Customized Package DX
with Condensor Reheat
51 oF
42.5 Tons
75.8 Tons
0 btu/hr
85%
Total Energy Recovery, Chilled
Water with Hot Water Reheat
51 oF
42.5 Tons
37.5 Tons
166,100 btu/hr
57%
Dual Wheel Total Energy
Recovery
51 oF
42.5 Tons
29.5 Tons
0 btu/hr
33%
PDH
Passive Dehumidificaiton System
51 oF
42.5 Tons
24 Tons
0 btu/hr
27%
Notes: Assumes conditioning outdoor air from a design condition of 85 degrees and 130 grains to a delivered condition of 55 grains and 68 degrees.
A return air path is available at a condition of 75 degrees and 50% rh (65 grains).
© SEMCO Incorporated 75
A Fläkt Woods Company
Option 4: Pinnacle System
© SEMCO Incorporated 76
A Fläkt Woods Company
Psychrometric Comparison
Single Wheel or EPD/Twin Wheel
Pinnacle DOAS Approach
2
Cooling
Load
94
Space
Condition
4
Dehumidification
3
4
70
56
132
1
2
Cooling
Load
94
Space
Condition
70.
4
Space
Dehumidification
3
56
44
4
52oF
62oF
75oF
Temperature
85oF
• Supply air is limited by leaving cooling
coil grain level.
• Single wheel unit requires parasitic
reheat.
© SEMCO Incorporated 77
52oF
62oF
75oF
85oF
Temperature
• Dehumidification capacity significantly
increased using Pinnacle
• Free reheat provided with passive
dehumidification wheel.
• 1/2 to 1/3 the primary airflow required
A Fläkt Woods Company
Absolute Humidity (Grains)
1
Absolute Humidity (Grains)
132
Pinnacle System: Unoccupied Mode
© SEMCO Incorporated 78
A Fläkt Woods Company
Pinnacle System: Heating Mode
© SEMCO Incorporated 79
A Fläkt Woods Company
Cooling Efficiency Drops with the Coil
Leaving Air Temperature
De-rate from ARI (Nominal) Tonnage
1.40
Trane TTA 120 10 ton data
1.30
Carrier 044 40 ton data
Log. (Trane TTA 120 10 ton data)
1.20
1.10
1.00
y = -1.485Ln(x) + 6.938
0.90
0.80
45
47
49
51
53
55
57
59
Air Temp Leaving Evaporator Coil
The equation corrects the calculated cooling capacity input for 95 degree ambient and suction temperature
Analyses based on a Heatcraft coil 5EN1205B, 3000 cfm, 80db/67wb entering, 42H x 26W, 396 feet per minute
© SEMCO Incorporated 80
A Fläkt Woods Company
Compressor Fundamentals: Why Pinnacle is
Far More Efficient at Dehumidification
(Copeland data used to analyze recent Ky School Project)
Case 1:
Single wheel
Supply 48 grains
47 oF off coil
40 oF suction T
120 oF condensing T
48
EER - 11.9 BTU/Watt-hr
Case 2:
Pinnacle
Supply 48 grains
55 oF off coil
48 oF suction T
110 oF condensing T
EER – 16.5 BTU/Watt-hr
16.5
© SEMCO Incorporated 81
16.5/11.9 – 39%
More Efficient
A Fläkt Woods Company
130
120
ASHRAE Standard 55 Comfort Zone
110
100
90
68oF WB
80
80%
70%
70
60%
60
50%
50
40
40%
30
30%
Comfort Zone Suggested by Berglund
Relative Humidity
66
68
20
70
72
74
76
78
o
Dry Bulb Temperature ( F)
80
82
Humidity Ratio - Grains of Moisture Per Pound of Dry Air
Schools Data Supports Comfort Research
•
•
•
•
Comfort influenced by temperature
and vapor pressure (dew-point)
Two year school investigation
findings: 72.5o/64% vs. 75o/53%
Trend shows to achieve comfort,
the supply temperature will be
dropped .65o/Degree dew-point or
.2 degrees/% RH
Trend agrees well with ASHRAE
Humidity Handbook
Berglund ASHRAE article: Conditions for 90% therm al acceptability
Av erage cooling season space conditions from DOE investigation
for schools using conventional (non-desiccant) systems
Av erage cooling season space conditions from DOE investigation
for schools using non-conventional (desiccant) systems
o
Source: May 2003 ASHRAE Journal Article “Report Card on Humidity Control”
© SEMCO Incorporated 82
A Fläkt Woods Company
40,000 CFM Pinnacle Energy Recovery System
© SEMCO Incorporated 83
A Fläkt Woods Company
Energy Modeling Example:
Kentucky School Analysis
 Energy analysis completed for the Kentucky Schools facility group
 Modeling completed using the Carrier HAP program and Pinnacle
Hourly Energy Analysis Supplement
 Analysis compares the following system options:
 Ground source heat pumps served by a ground source based DOAS
cooling unit with hot gas reheat incorporating a total energy wheel
 Ground source heat pumps served by a Pinnacle DOAS system
 Chilled beams served by a Pinnacle DOAS system
 Final report prepared using documentation and provided by the
school’s facilities group
© SEMCO Incorporated 84
A Fläkt Woods Company
Energy Modeling Example:
Kentucky School Analysis







Three level High School
Modeled all classrooms,
hallways and media center
Total gross square feet at
138,500
Lexington Kentucky weather
data
ASHRAE 90.1 2004 school
defaults used for hours of
occupancy, lighting
schedule, etc.
Electricity costs at $.07/KWH
Carrier HAP program with
Pinnacle Hourly Energy
Analysis model supplement
© SEMCO Incorporated 85
A Fläkt Woods Company
Energy Modeling Results:
GS Heat Pumps served by Different DOAS
Systems (Single wheel vs. Pinnacle)
Pumps
$80,000
Annual Energy Cost
$70,000
Heating
$60,000
$50,000
Cooling
$40,000
$30,000
$20,000
Air System
Fans
$10,000
$0
Baseline precool
DX/recovery and WS
Heat Pumps
Pinnacle Serving Water
Source Heat Pumps
Design Approach
© SEMCO Incorporated 86
A Fläkt Woods Company
Monthly Energy Results:
GS Heat Pumps served by Different DOAS
Systems (Single wheel vs. Pinnacle)
Table 3: Energy Use by Sub-System by Month
Terminal Unit
Terminal Unit or
or Chilled
Terminal Unit Fan
Chilled Beam
Month
Beam Cooling
Energy
Heating Coil Load
Coil Load
(kBTU)
(kBTU)
(KWh)
Pinnacle
Cooling Coil
Load (1)
Pinnacle
Heating Coil
Load
Pinnacle Fan
Lighting
Electrical
Equipment
(kBTU)
(kBTU)
(KWh)
(KWh)
(KWh)
January
21908
404418
5078
2200
107849
16633
48175
22670
February
28822
340363
4419
0
88029
14463
42193
19855
March
55095
181424
3590
26236
56833
15909
44770
21067
April
212070
22120
5804
139687
17290
15186
46178
21730
May
296942
1447
8806
293452
6646
16633
46524
21891
June
461218
0
12808
483272
246
15186
44429
20907
July
693283
0
13333
0
0
0
48175
22670
August
614026
0
11841
0
0
0
44770
21067
September
298211
321
8968
364342
3867
14463
46178
21730
October
160387
38988
5549
196262
20487
16633
48175
22670
November
52376
148544
3390
39315
46252
15909
42778
20132
December
25842
353003
4586
9874
84198
15186
48175
22670
2,920,180
1,490,628
88,172
1,554,641
431,697
156,202
550,521
259,059
Total
(1) Pinnacle operated to process cooling season internal latent loads (control humidity) under all conditions, baseline systems do not
© SEMCO Incorporated 87
A Fläkt Woods Company
Energy Modeling Results:
GS Heat Pumps with Single Wheel DOAS
Systems vs. Chilled Beam and Pinnacle
Pumps
$80,000
Annual Energy Cost
$70,000
Heating
$60,000
$50,000
Cooling
$40,000
$30,000
$20,000
Air System
Fans
$10,000
$0
Baseline precool
DX/recovery and WS
Heat Pumps
WS Pinnacle Serving
Chilled Beams
Design Approach
© SEMCO Incorporated 88
A Fläkt Woods Company
Monthly Energy Results:
GS Heat Pumps with Single Wheel DOAS
Systems vs. Chilled Beam and Pinnacle
Table 3: Energy Use by Sub-System by Month
Terminal Unit
Terminal Unit or
or Chilled
Terminal Unit Fan
Chilled Beam
Month
Beam Cooling
Energy
Heating Coil Load
Coil Load
(kBTU)
(kBTU)
(KWh)
Pinnacle
Cooling Coil
Load (1)
Pinnacle
Heating Coil
Load
Pinnacle Fan
Lighting
Electrical
Equipment
(kBTU)
(kBTU)
(KWh)
(KWh)
(KWh)
January
19911
443011
0
2767
107849
21847
48175
22670
February
27317
371479
0
284
88029
19241
42193
19855
March
38579
195862
0
36824
56833
21212
44770
21067
April
169465
24487
0
164700
17290
20343
46178
21730
May
232842
1948
0
308718
6646
21847
46524
21891
June
377565
0
0
580306
246
20343
44429
20907
July
639672
0
0
0
0
7227
48175
22670
August
566104
0
0
0
0
7227
44770
21067
September
235351
624
0
432270
3867
19698
46178
21730
October
116465
42905
0
206680
20487
21847
48175
22670
November
22765
160741
0
61539
46252
20979
42778
20132
December
15697
380661
0
13757
84198
20576
48175
22670
2,461,732
1,621,719
0
1,807,845
431,697
222,387
550,521
259,059
Total
(1) Pinnacle operated to process cooling season internal latent loads (control humidity) under all conditions, baseline systems do not
© SEMCO Incorporated 89
A Fläkt Woods Company
Relative Energy Consumption of School
HVAC Systems
Total School
Building Energy
(Kbtu/sf-yr)
ASHRAE 90.1
Lighting and
Equipment
(Kbtu/sf-yr)
HVAC System
Energy
(Kbtu/sf-yr)
Benchmark Average (North Carolina Schools) (1)
68.3
19.9
48.4
VAV with 75% total energy recovery (2)
60.7
19.9
40.8
Fan Coils with 75% total energy recovery (2)
58.2
19.9
38.3
VRF (Reported actual data from field testing) (3)
65.4
19.9
45.5
GS Heat Pumps, GS OA system with 75% total energy
recovery and hot gas reheat (2)
47.4
19.9
27.5
GS Heat Pumps with Pinnacle (2)
43.1
19.9
23.2
Chiller and Boiler feeding Pinnacle and Chilled Beams (2)
40.5
19.9
20.6
GS Heat Recovery Chiller, Pinnacle and Chilled Beams (2)
36.6
19.9
16.7
HVAC System Approach
Note 1: Data from North Carolina Energy Office document "Benchmarks - Ranking Building Energy Intensity"
Note 2: HAP 4.41 modeling, Pinnacle hourly supplement, $.07/KWh electrical cost, ASHRAE 90.1 school defaults, Lexington weather data
Note 3: Average of data reported by VRF manufactuer for school facilities designed with VRF systems and actual data measured at
Kentucky Schools and ASHRAE Headquarters - for comparison purposes only
Note 4: ASHRAE default school hours used, assumes year round school operation, no operation weekends or holidays. If no summer
season operation, KBTU values shown will be considerably less for all systems
© SEMCO Incorporated 90
A Fläkt Woods Company
Office and School Analysis:
Energy Savings Potential
Office Example
HVAC Operating Cost
VAV Total
Recovery
Fan Coils
CB Single
Total
Wheel
Recovery
School Example
CB Dual
Wheel
Chilled
Beams
Pinnacle
VAV Total
Recovery
Fan Coils
Total
Recovery
CB Single
Wheel
CB Dual
Wheel
Chilled
Beams
Pinnacle
Total Annual HVAC cost
Square Footage
$9,469
8500
$8,351
8500
$6,025
8500
$5,619
8500
$4,883
8500
$8,112
8500
$7,126
8500
$6,214
8500
$5,935
8500
$5,137
8500
HVAC Energy Cost/Sq Ft
$1.11
$0.98
$0.71
$0.66
$0.57
$0.95
$0.84
$0.73
$0.70
$0.60
Percent Increase vs. Best
94%
71%
23%
15%
Best
58%
39%
21%
16%
Best
Notes
(1) VAV and fan coil units do not include cooling season humidity (costs would be higher), chilled beams do.
(2) Atlanta weather data used, electricity at $.08/KWHH and gas at $10/MMBtu., conventional building simulation modeling used
(3) Office operated in occupied mode 12 hrs/day, 7 days/wk, School operated in occupied mode 12 hrs/day, 6 days/wk
(4) Cooling season space conditions of 75oF and 50% RH with 78oF setback, heating season at 70oF and 30%RH with a 65oF setback
© SEMCO Incorporated 91
A Fläkt Woods Company
Office and School Analysis:
Installation Cost Comparison
Office Example
Equipment
AHUs, fans and installation
HVAC Electrical
DDC Controls and valves
Chiller Tower and Boiler
Ductwork and installation
Piping and installation
Fan coil units
VAV boxes
Chilled beams
Dampers and diffusers
Other installation/markup
Total cost
Square Footage
Cost/Sq Ft
© SEMCO Incorporated 92
VAV
$41,186
$18,200
$27,000
$30,500
$21,250
$9,800
$12,360
$40,150
$15,500
$14,400
$23,500
$14,875
$50,585
$10,800
School Example
CB Dual
Wheel
CB
Pinnacle
VAV
Fan Coils
$36,350
$7,500
$12,240
$23,500
$12,644
$36,050
$47,350
$8,000
$12,240
$21,200
$12,644
$35,350
$40,500
$5,250
$12,240
$18,200
$9,031
$32,900
$45,071
$19,250
$33,750
$31,500
$19,763
$10,150
$44,000
$17,500
$18,000
$27,500
$16,363
$52,685
$13,500
$19,585
$3,520
$16,349
$19,585
$3,520
$15,789
CB Single
Fan Coils
Wheel
$10,560
$16,586
$10,560
$16,091
$19,585
$3,520
$16,094
$187,441
8500
$196,461
8500
$167,483
8500
$176,238
8500
$22.1
$23.1
$19.7
$20.7
$15,450
CB Single
Wheel
CB Dual
Wheel
CB
Pinnacle
$40,200
$7,750
$14,240
$27,500
$13,908
$38,150
$52,850
$8,250
$14,240
$23,200
$13,908
$36,750
$43,675
$4,950
$14,240
$21,200
$7,907
$34,650
$11,400
$19,015
$11,400
$18,478
$21,762
$3,800
$17,800
$21,762
$3,800
$18,024
$21,762
$3,800
$17,347
$157,016
8500
$205,348
8500
$219,426
8500
$185,110
8500
$192,784
8500
$169,530
8500
$18.5
$24.2
$25.8
$21.8
$22.7
$19.9
A Fläkt Woods Company
Substantial LEED Point Potential
Potential
LEED 2.2
Points
Credit Category
9 (up to)
Potential 38.5% energy reduction with chilled beams/Pinnacle and geothermal heat pump system
2
30% water savings associated with reduced chiller capacity at the cooling tower
2
Increased ventilation air provided and measured by the Pinnacle system
3
Designing for, controlling and verifying thermal comfort with chilled beams and Pinnacle
2
Innovation and design points - chilled beam technology and Pinnacle dedicated outdoor air system
Approximately 33 required for LEED Silver
© SEMCO Incorporated 93
A Fläkt Woods Company
Chilled Beam + Pinnacle Design Guide
© SEMCO Incorporated 94
A Fläkt Woods Company
Conclusions
 Lowering the primary air dewpoint dramatically reduces the amount
of primary air required to satisfy the latent load allowing chilled
beams to be applied to humid climates
 Chilled Beams/Pinnacle significantly reduce building energy
consumption while simultaneously controlling space humidity
 Chilled Beams can reduce first cost by downsizing chilled capacity,
electrical components, ductwork size and controls.
 The internal latent loads must be estimated correctly – challenge
much greater in the US compared to Europe
 Combining chilled beams with Pinnacle can provide the design
consultant and end user with as a many as 16 LEED points.
© SEMCO Incorporated 95
A Fläkt Woods Company