5.0 Aquasmart Hydronic Energy Studies Customer Presentation
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AQUASMART HYDRONIC SYSTEMS ENERGY STUDIES ENERGY STUDIES
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Transcript of 5.0 Aquasmart Hydronic Energy Studies Customer Presentation
AQUASMART HYDRONIC SYSTEMS ENERGY STUDIESENERGY STUDIES
Aquasmart EVOLUTION 2010
2
AN ENERGY SAVING COMMUNICATING HYDRONIC SYSTEM SOLUTION
Aquasmart EVOLUTION 2010 SYSTEM ENERGY SIMULATION
ApplicationApplicationOffice application 6145m² of surface Location London, United Kingdom HVAC system comprising
4 pipe ducted fan coil system 60Pa ESPCycled fan control
Air cooled chiller(s) Heating system boilerg yFresh air handling unit
Office occupancy hours of 07 00 19 0007:00 – 19:00week only
3
USING HAP (ENERGY SIMULATION TOOLS)
Aquasmart EVOLUTION 2010 System control energy optimisation
CASE ONE CASE TWO
Traditional
Thermostat Schedule NO YES24hr operation 07:00 – 19:00
Cooling T-stat set points Occupied
22.0
22.0
Unoccupied 22.0 26.0
Heating T-stat set points Occupied
20.0
20.0
Unoccupied 20.0 15.0
Terminal fan coil speed control ON Cycled
Chill t l C t t l C t t V lChiller pump control Constant volume Constant Volume
EVALUATE CAREFULLY IN TERMS OF SHUT-IT OFF PROGRAM
5 SYSTEM ENERGY SIMULATION Case study 1 –v- 2
HVAC COMPONENT ENERGY USAGESTUDY ONE
(STAND ALONE controls)
HVAC COMPONENT ENERGY USAGESTUDY TWO
(COMMUNICATING Controls)
1% 5%11% 1% 3%10%
40%40%
43%
46%
40%
AHU System Fans Terminal unit fans (FCU's) Cooling Heating Pumps AHU System Fans Terminal unit fans (FCU's) Cooling Heating Pumps
SYSTEM ENERGY SIMULATION Case study 1 –v- 2
CASE ONE CASE TWOCASE ONE CASE TWO
ComponentAir System Fans TOTAL) 10 474 6 002
Site Energy(kWh)
AHU System Fans 1 942 1 942Terminal unit fans (FCU's) 8 532 4 060Cooling 69 487 68 962Heating 76 307 59 638Pumps 19 215 15 228
CASE ONE CASE TWO
TRADITIONAL AQUASMARTHVAC component consumptionAir System Fans TOTAL) - 43%
HVAC Sub-Total 175 483 149 830
y )
AHU fans - 0%Terminal unit fans (FCU's) - 52%Cooling - 1%Heating - 22%Pumps 21%Pumps - 21%
HVAC Sub-Total - 15%
ENERGY CONSUMPTION SAVINGS WITH AQUASMART OF 15%
Aquasmart EVOLUTION 2010 System control energy optimisation
CASE ONE CASE TWO CASE THREE
Traditional
Thermostat Schedule NO 24hr operation
YES 07:00 – 19:00
YES 07:00 – 19:00
Cooling T-stat set points Occupied
Unoccupied 22.0 22.0
22.0 26.0
22.0 26.0
Heating T-stat set points Occupied
Unoccupied 20.0 20.0
20.0 15.0
20.0 15.0
Terminal fan coil speed control
ON Cycled Cycled control
Chiller pump control Constant volume Constant Volume Variable Volume
7
SYSTEM ENERGY SIMULATION Case study 3
HVAC COMPONENT ENERGY USAGESTUDY THREESTUDY THREE
(COMMUNICATING Controls and Variable flow)
1% 3%5% 1% 3%5%
48%43%
AHU System Fans Terminal unit fans (FCU's) Cooling Heating Pumps
8
AQUASMART SYSTEM PLUS VARIABLE SPEED PUMPS
9 SYSTEM ENERGY SIMULATION Case study 1 –v- 2 –v- 3
CASE ONE CASE TWO CASE THREECASE ONE CASE TWO CASE THREE
ComponentAir System Fans TOTAL) 10 474 6 002 6 002
Site Energy(kWh)
AHU System Fans 1 942 1 942 1 942Terminal unit fans (FCU's) 8 532 4 060 4 060Cooling 69 487 68 962 67 333Heating 76 307 59 638 59 638Pumps 19 215 15 228 6 980
CASE ONE CASE TWO CASE THREE
TRADITIONAL AQUASMART % ECONOMIESHVAC component consumptionAir System Fans TOTAL) - 43% 43%
HVAC Sub-Total 175 483 149 830 139 953
y )
AHU fans - 0% 0%Terminal unit fans (FCU's) - 52% 52%Cooling - 1% 3%Heating - 22% 22%Pumps 21% 64%Pumps - 21% 64%
HVAC Sub-Total - 15% 20%
VARIABLE SPEED PUMPS BRING FURTHER 5% SYSTEM SAVINGS
HYDRONICHYDRONIC HEATING, VENTILATING & AIR CONDITIONING
SOLUTIONSSOLUTIONS
Energy Conservation OpportunitiesEnergy Conservation Opportunities
Tim Ashton LEED™ AP
10
Tim Ashton LEED™ AP Business Development, Systems Marketing & Controls Manager
Agenda
• Introduction to Study objectives • Baseline model definition• Hydronic energy conservation measures • Energy simulation study resultsgy y• Conclusions • Questions & AnswersQuestions & Answers
STUDY OBJECTIVES
• Guide design teams and building owners on the principal energy saving measures available with hydronic systems to reduce the energy impact of buildings on the environment .
Quantify the main energy saving opportunities in terms of• Quantify the main energy-saving opportunities in terms of energy saving potential.
• Evaluate how the impact of energy-saving measures may be ff t d b hi l l ti d h b th thaffected by geographical location and hence by the weather
conditions and hence accordingly provide some guidance as to the optimum solutions.
REDUCE ENERGY IMPACT OF BUILDINGS WHILST MAINTAINING
OCCUPANT COMFORT AND HENCE PRODUCTIVITY
TYPICAL HYDRONIC FAN COIL SYSTEM
Fresh air handling unit
Chillers/Heat pumps
Unit mountedmountedcontrols
Hydronic terminal fan coils
BASELINE BUILDING MODEL Definition• Building g
• 1380m² surface office • Model defined covering all
aspects of building envelope internal loadsenvelope, internal loads, and occupancy schedule.
• HVAC system description • 4-pipe ducted fan coil4 pipe ducted fan coil
system • air-cooled liquid chiller • Space heating water by a
gas boilergas boiler.• A fresh air handling unit
provides tempered outdoor air to serve the occupied spaces.
• Non-communicating controls
BASELINE BUILDING MODEL
BUILDING ENVELOPE INTERNAL LOADS
Definition Structure U = W/m²/K R = m²•K/W
Walls 0.318 3.14
Floor/foundations 0.27 3.7
Occupancy (occupied spaces) 12 m²/person
Main lighting type and power Recessed, vented 12 W/m²
Task lighting (desk lights etc.) 5 W/m²
Electrical loads (PC, printers etc.) 10 W/m² Outdoor air ventilation rates based on office 10 0 l/ /
Roof 0.685 1.46
Glazing 0.385 2.6
Outdoor air ventilation rates based on office requirement 10.0 l/s/person
Activity level office work Sensible
Latent
71.8 W/person 60.1 W/person
Figure 1: Occupancy schedule Figure 2: Lights/electricity scheduleFigure 1: Occupancy schedule Figure 2: Lights/electricity schedule
TYPICAL INSULATION VALUES* WERE USED (*SOURCE EURIMA)( )SCHEDULES WERE BASED ON ASHRAE 90.1-2007
BASELINE BUILDING MODEL 8760 hr cooling & heating load simulation
DESIGN COOLING
COOLING OA DB / WB 26,9 °C / 19,4 °C HEATING OA DB / WB -9,4 °C / -11,0 °C
DESIGN HEATINGCOOLING DATA AT Jun 1600 HEATING DATA AT DES HTG
W/m² W/m²57 44
BASELINE BUILDING MODEL Consumption by system component
Energy Consumption by HVAC System Component
69 668
80 000
Energy Consumption by HVAC System Component(kWhr)
69 668
50 000
60 000
70 000
30 000
40 000
50 000
7 1523 530
20 919
13 567
7 85910 000
20 000
0Air Handling unit
motorsTerminal fan coil
motorsCooling Heating Pumps (Cooling) Pumps (Heating)
Air Handling unit motors Terminal fan coil motors Cooling Heating Pumps (Cooling) Pumps (Heating)
17
ENERGY CONSUMPTION BY HVAC COMPONENT
57%
6%
17%
11%6%
3%
Air Handling unit motors Terminal fan coil motors Cooling
Heating Pumps (Cooling) Pumps (Heating)
Example: Office example of 1 380m² surface with occupancy hours: 07:00–19:00 Ducted fan coil system, air cooled chiller, boiler and fresh air handling
unitunit
BASELINE BUILDING MODEL Simulated for eight european locations
250 000
Total Annual Cooling Plant Load… Total Annual Heating Plant Load… Total Annual Power Consumption…
200 000
100 000
150 000
kWh
50 000
0Athens Rome Madrid Lyon London Brussels Munich Gothenburg
BRUSSELS, BELGIUM SELECTED FOR INDIVIDUAL FOCUSIN STUDY PAPER
ENERGY CONSERVATION MEASURES by system component
HVAC system component Energy-saving opportunities
Pro
duct
ion
(chi
ller /
he
at
pum
ps)
Produces hot or cold water for distribution via a pipe network through the building
Heat pumps/thermodynamic boiler for hot water production Chiller system with integrated free-cooling system and/or integrated heat recovery options
Roo
m
term
inal
s Conditions the air in the occupied space, heating, cooling, filtering and introducing pre-treated fresh/outdoor air quantities in some systems.
Communicating controllers (part of communicating system)Demand Control Ventilation (CO2 sensors) for certain areas (meeting and conference rooms) High-efficiency/low-energy motors (EC/DC)
h ai
r nt
Basic functions include filtering, pre-cooling and/or pre-heating outdoor air to provide neutral impact on
Heat recovery technology (plate heat exchangers, heat wheels) to recover waste heat/cool air from exhaust air to pre-treat entering air.
Fres
hpl
an pre heating outdoor air to provide neutral impact on the occupied space conditions.
recover waste heat/cool air from exhaust air to pre treat entering air. Communicating controls allow strategies such as night-time free cooling to pre-cool buildings before occupied periods.
Pip
ing
istri
butio
n Means by which hot and/or cooled water is provided to the various system components, traditionally using a constant-volume design.
Variable speed pump motor(s)allowing variable water flow to the distribution, offering pump motor energy savings at part load conditions.
diTe
rmin
al
Uni
t co
ntro
ls Unit-mounted controls allowing space occupants to
adjust the temperature set point and control the fan speed according to the terminal type.
Unit fitted with auto-fan mode control that adjusts fan speed to match space load requirements to economise fan motor energy by steps or variable speed.
Non comm nicating or comm nicating that ma be Use comm nicating controllers ith a centralised management s stem
HV
AC
Sys
tem
co
ntro
ls
Non-communicating, or communicating that may be integrated into a Building Management system. Communicating controls offer connectivity with a central management system to adjust unit and system settings and performance to building requirements.
Use communicating controllers with a centralised management system.Benefits include: • management of occupied and unoccupied temperature set points • time scheduling of operating hours to match work days and holidays • monitoring and adjusting equipment operating conditions such as chilled water/hot water to match outdoor conditions and loads.
ENERGY CONSERVATION MEASURES Selected studies
Study Description of energy-saving measure
Baseline Traditional stand-alone system = Terminal fan coil units with non-communication, ‘stand-alone’ controls = manual user fan speed control = single temperature set- point
Study 1 Advanced Fan coil controls and management using communication controls = Terminal fan coil units with Auto fan coil unit fan cycling to meet space load. = Separate temperature set points for both cooling and heating modes = Temperature set point reset according to the building occupancy schedule.
Study 2 Use of heat recovery exchanger (50% efficiency) on the fresh air handling unit= Recovery energy from return air using a plate heat exchanger to reduce pre-heat need.
Study 3 Variable-speed pumps for chilled water distribution. = Variation of chilled water flow according to building load
Study 4 Use of a chilled water free-cooling systemStudy 4 Use of a chilled water free-cooling system= Integration of free cooling to benefit from low outside air temperatures and reduce mechanical ccoling.
Study 5 Replace traditional boiler with thermodynamic heating unit = Thermodynamic heating offering COPS <4.2 versus other fuel sources
Study 6 EC motors fitted to Fan coil units = Higher efficiency motors and reduced unit consumption = Variable air volume control to better match room or zone loads
Study 7 Simultaneous use of the first three energy saving measures described in studies 1, 2 and 3.
ENERGY CONSERVATION MEASURE Study 1
• Advanced Fan coil controls and management using communication controls – Terminal fan coil units with Auto fan coil unit fan cycling to
meet space load. Separate temperature set points for both cooling and– Separate temperature set points for both cooling and heating modes
– Temperature set point reset according to the building occupancy schedule.
ENERGY CONSERVATION MEASURE Communication HVAC system control
• Benefits include energy savings by:
Management of occupied / non
BASELINE STUDY STUDY 1
Traditional
Thermostat Schedule
NO 24hr operation
YES 07:00 – 19:00
– Management of occupied / non-occupied periods
– Separate cooling & heating set- i t
Cooling T-stat set points
Occupied Unoccupied
22.0 22.0
22.0 26.0
Heating T-stat set points
– Holiday and work period schedules
points Occupied
Unoccupied
20.0 20.0
20.0 15.0
Terminal fan coil speed control
ON Cycled
Chiller pump control Constant volume Constant Volume
Aquasmart a standard smallAquasmart - a standard smallhydronic system
Solution for buildings with up to 128 zones128 zones
ENERGY CONSERVATION MEASURE Study 1: FCU management 88,91
86
88
90
r
⇒REDUCED COOLING (1%) & HEATING LOADS (2%) ⇒REDUCED PUMP CONSUMPTION (34%) IN COOLING & (19%) IN HEATING MODES. ⇒REDUCED TERMINAL FAN MOTOR POWER (70%)
81,36
78
80
82
84
kWh/
m²/y
r
122 695
112 270
100 000
120 000
140 00076
Non-EcoSystem
Eco System
69 668 67 959
60 000
80 000
100 000
7 152 7 1523 530 1 061
20 919 20 73213 567
8 976 7 859 6 390
0
20 000
40 000
elin
e
0%
elin
e
-70% elin
e
-1%
elin
e
-2%
elin
e
-34% elin
e
-19% elin
e
-8%
Base
Base -
Base
Base
Base -
Base -
Base
Air Handling Unit Terminal Fans Cooling(NON-ECO SYSTEM)
Cooling(ECO
SYSTEM)
Heating(NON-ECO SYSTEM)
Heating(ECO
SYSTEM)
Pumps(Cooling)
Pumps(Heating)
Non Eco System
Eco System (FCU comfort management)
POTENTIAL SAVINGS OF ~7.5KWH/M²/YEAR OFFERING ANOVERALL SYSTEM REDUCTION OF 8%
ENERGY CONSERVATION MEASURE Study 2
• Use of heat recovery exchanger (50% efficiency) on the fresh air handling unit – Recovery energy from return air using a plate heat
exchanger to reduce pre-heat need.
ENERGY CONSERVATION MEASURE Air handling heat recovery
Air handling units provide fresh air to the occupied spaces. Basic unit‘s include supply & extract sections
d i l d li /h ti il tand may include cooling/heating coils to pre-temper supply air.
Adding heat recovery technology ff b t ti l ican offer substantial economies
ENERGY CONSERVATION MEASURE Study Two: Fresh air heat recovery
= SIGNIFICANT REDUCTIONS IN HEATING LOADS (~60%)88,91
90
100
= SIGNIFICANT REDUCTIONS IN HEATING LOADS ( 60%) = REDUCED ENERGY CONSUMPTION IN COOLING (<1%) = SOME RELATED REDUCED PUMPING ENERGY (~5,4%).
122 695120 000
140 00058,06
40
50
60
70
80
kWh/
m²/y
r
69 668
80 12980 000
100 000
120 000
0
10
20
30
Non-EcoSystem
Eco-System(Heat reclaim)
20 919 20 77927 668
40 000
60 000
7 152 7 1523 530 3 530
20 919 20 77913 567 13 567
7 859 7 433
0
20 000
Base
line
0,0%
Base
line
0,0%
Base
line
-0,7
%
Base
line
-60,
3%
Base
line
0,0%
Base
line
-5,4
%
Base
line
-35%
B B B B B B B
Air Handling Unit Terminal Fans Cooling Heating Pumps(Cooling)
Pumps(Heating)
Non Eco System
Eco System (Heat
POTENTIAL SAVINGS OF ~30.8 KWH/M²/YEAR OFFERING ANOVERALL SYSTEM REDUCTION OF 35%
ENERGY CONSERVATION MEASURE Study Three
• Variable-speed pumps for chilled water distribution. – Variation of chilled water flow according to building load
BEST PRACTICES: CHILLER/HEAT PUMPS Variable flow applications
ENERGY CONSERVATION MEASURE Study Three: Variable flow pumps= REDUCE PUMP ENERGY CONSUMPTION BY 72% 88,9
90
= CONTRIBUTION FROM REDUCED PUMP HEAT, = HENCE REDUCING COOLING PLANT LOAD (>1%)
82
84
86
88
kWh/
m²/y
r
69 668 69 668
122 695111 160
80 000
100 000
120 000
140 00080,6
76
78
80
Non-Eco System Eco-System(VWF)
7 152 7 152 3 530 3 530
20 919 19 172
69 668 69 668
13 5673 779 7 859 7 85920 000
40 000
60 000
80 000 (VWF)
7 152 7 152 3 530 3 530 3 7790
Base
line
0,0%
Base
line
0,0%
Base
line
-8,4
%
Base
line
0,0%
Base
line
-72,
1%
Base
line
0,0%
Base
line
-9,4
%
Air Handling Terminal Fans Cooling Heating Pumps Pumps Non EcoAir Handling Unit
Terminal Fans Cooling Heating Pumps (Cooling)
Pumps (Heating)
Non Eco
System
Eco System (VWF)
POTENTIAL SAVINGS OF ~8,3 KWH/M²/YEAR OFFERING ANOVERALL SYSTEM REDUCTION OF 9,4%
ENERGY CONSERVATION MEASURE Study Four
• Use of a chilled water free-cooling system – Integration of free cooling to benefit from low outside air
temperatures and reduce mechanical ccoling.
ENERGY CONSERVATION MEASUREIntroduction To Free Cooling
• Use of cold outside air to generate chilled water when cooling ischilled water when cooling is required all year around
• BenefitsBenefits • Energy savings reducing compressor
run time • Reduced equipment wear and noise
Average temperatures °C City Oct Nov Dec Jan Feb Mar Ap Amsterdam 10 5.5 4.0 3.0 2.5 5.0 7.5 Berlin 9 3 4 2 1 1 -0 7 0 7 3 7 8 5
• When • Free cooling not restricted to ‘cold’
countries, 5° outside air is sufficient for free cooling
Berlin 9.3 4.2 1.1 -0.7 0.7 3.7 8.5 London 10.9 6.8 4.9 4.1 4.3 6.3 8.2 Milano 13.1 6.9 2.3 1.4 4.2 8.3 12.3 Paris 10.8 6.4 3.7 2.9 4.1 6.6 9.9 Prague 9.1 3.5 0.1 -1.7 -0.3 3.4 8.5 for free-cooling
g
Stockholm 6.8 1.9 -1.4 -3.2 -3.3 -1.0 3.8 Vienna 9.9 4.3 4.0 -1.2 0.6 4.5 9.8 Warsaw 8.2 2.5 -1.7 -3.8 -2.5 1.4 7.6 Zurich 9.1 4.0 0.5 -0.5 1.0 4.5 8.4
ENERGY CONSERVATION MEASURE Traditional –v- Carrier DX free cooling
Traditional free cooling system - Additional dry coolers / cooling towers*
- Outstanding Energy Efficiency EER = <13 - Glycol for winter operation
* For air cooled systems
DX f li tDX free cooling system - Integrated with chiller
- Outstanding Energy Efficiency EER = <13 - No glycolg y
- Reduced Maintenance costs
DIFFERENT SYSTEMS EXIST ACCORDING TO DESIGN AND APPLICATION NEEDSDIFFERENT SYSTEMS EXIST ACCORDING TO DESIGN AND APPLICATION NEEDS
ENERGY CONSERVATION MEASURE Traditional versus DX free cooling
BENEFITS Traditional H²O system DX-FC system
Economical free cooling! ☺ ☺ Reduced noise emission (no compressors) ☺ ☺
Reduced maintenance (reduced compressor use) ☺ ☺( p ) ☺ ☺
FREE COOLING RELATED COSTS Traditional H²O system DX-FC system
Extra pump(s) ☺
Higher pumping cost due to Glycol viscosity ☺
Higher pumping cost due to pressure drop of additional exchanger and control valves
☺
Higher fan power cost due to additional air pressure drop of radiator
☺
Maintenance (time and costs) ☺ SYSTEM DESIGN IMPACT Traditional H²O system DX FC systemSYSTEM DESIGN IMPACT Traditional H²O system DX-FC system
Reduced chiller COP due higher fan power. ☺ Chiller footprint ☺ I f l l i l i d iImpact of glycol on equipment selections and sizes ☺
ENERGY CONSERVATION MEASURE Study Four: Free Cooling
88,9
89
89
90
r
=REDUCED COMPRESSOR OPERATION, FANS AND PUMPS =ONLY REDUCING COMPRESSOR CONSUMPTION. 87,1
87
87
88
88
kWh/
m²/y
r
25,00%
30,00%
CITY
Free-cooling energy savings (%)
86
87
Non-Eco… Eco-System…
10,00%
15,00%
20,00%CITY
over mechanical only system
ATHENSGREECE 0,18%ROMEITALY 0,74%MADRIDSPAIN 2,00%LYON
0,00%
5,00%
ATHENSGREECE
ROMEITALY
MADRIDSPAIN
LYONFRANCE
LONDONUK
BRUSSELSBELGIUM
MUNICHGERMANY
GOTEBURGSWEDEN
OFRANCE 9,09%LONDONUK 7,12%BRUSSELSBELGIUM 11,72%MUNICHGERMANY 20,09%GOTEBURGSWEDEN 26 39%GREECE ITALY SPAIN FRANCE UK BELGIUM GERMANY SWEDEN
Free‐cooling energy savings (%) over mechanical only system
SWEDEN 26,39%
POTENTIAL SAVINGS OF UP TO 26% PER YEAR ON COOLING PRODUCTIONPOTENTIAL SAVINGS OF UP TO 26% PER YEAR ON COOLING PRODUCTION
ENERGY CONSERVATION MEASURE Study five
• Replace traditional boiler with thermodynamic heating unit – Thermodynamic heating offering COPS <4.2 versus other
fuel sources
ENERGY CONSERVATION MEASURE Heating production
Chiller
+Heat P mp
Chiller
Heat Pump
COP <5.9kW (output/input)
Boiler Dedicated heating heat pump
REVERSIBLE CHILLER / HEAT PUMP / DEDICATED THERMODYNAMIC HEAT PUMPTO PROVIDE SPACE COMFORT HEATING
ENERGY CONSERVATION MEASURE Consider heat recovery opportunities
• Providing cooling, chillers extract heat from the system that is often rejected to outside. M li ti ft i h t t f• Many applications often require hot water for sanitary purposes.
• Offices • Industrial..
• Consider HEAT RECOVERY possibilities • Full and partial recovery is possiblep y p• water available up to 60 – 70°C according to
unit and application
RECOVER HEAT FOR PRACTICAL USERECOVER HEAT FOR PRACTICAL USE
ENERGY CONSERVATION MEASURE Study five: Thermodynamic heat pump
88,9
80
90
100
= Thanks to heating COP’s 1.9 at -20°C up to 4.6 at 20°C = Supplying medium temperature temp for space heating (40°C) = Offers significantly reduced heating energy consumption.
53,1
30
40
50
60
70
kWh/
m²/y
r
74%
75%
HEAT PUMP
0
10
20
Non-EcoSystem
Eco-System(Heat reclaim)
69%
70%
71%
72%
73% CITY HEAT PUMP ECONOMYS
ATHENSGREECE 74%ROMEITALY 73%MADRIDSPAIN 71%
66%
67%
68%
69%
Savings %
SPAIN 71%LYONFRANCE 71%LONDONUK 72%BRUSSELSBELGIUM 71%MUNICH
Athens, Greece Rome Italy Madrid Spain Lyon, FranceLondon Heathrow Belgium, Brussels Munich, Germany Goteburg Sweden
MUNICHGERMANY 69%GOTEBURGSWEDEN 69%
OVERALL COMFORT (SPACE) HEATING SAVINGS OF~69-74%( )OVER CONDENSING BOILER
ENERGY CONSERVATION MEASURE Study Six
• EC motors fitted to Fan coil units – Higher efficiency motors and reduced unit consumption – Variable air volume control to better match room or zone
loads
ENERGY CONSERVATION MEASURE Study Six: Fan Coil Units with EC motors
• Reduced energy costs • reduces fan coil consumption by 50% to 75%. • May assist in meeting new energy regulations (w/m²) in
buildingsbuildings.
• Improved comfort • variable fan speed minimizes noise levels at reduced
loads • Maximum fan speed may be fixed to allow limit energy
and sound.
• Maximum flexibility • Auto-fan speed from 0- 100% better matches cooling and
heating loads and hence offers better comfort for the occupant.
• Extended life • brushless motor technology offers lower fan motor gy
temperature and extends operating life.
ENERGY CONSERVATION MEASURE Study Six: Fan Coil Units with EC motors
Fan motor po er sa ings of 44%88,989
90
140 000
= Fan motor power savings of 44%= Corresponding savings in terminal cooling coil load of 1,3% = with a small increase in heating of 0.2%.
87,6
88
88
89
89
kWh/
m²/y
r
122 695 120 919
80 000
100 000
120 000
140 000
87
87
88
NON-ECOSYSTEM
ECOSYSTEM
20 919 20 642
69 668 69 831
40 000
60 000
80 000
7 152 7 152 3 530 1 962
20 919 20 64213 567 13 475
7 859 7 857
0
20 000
Ba
selin
e
0,0
%
Ba
selin
e
-44
,4%
Ba
selin
e
-1,3
%
Ba
selin
e
0,2
%
Ba
selin
e
-0,7
%
Ba
selin
e
0,0
%
Ba
selin
e
-1,4
%
B B B B B B B
Air Handling Unit Terminal Fans Cooling Heating Pumps(Cooling)
Pumps(Heating)
NON-ECOSYSTEM
ECO SYSTEM
POTENTIAL SAVINGS OF ~1,29 KWH/M²/YEAR OFFERING ANOVERALL SYSTEM REDUCTION OF 1,4%
ENERGY CONSERVATION MEASURE Study Seven
• Simulation of an HVAC system incorporating: – Advanced Fan coil controls and management using
communication controlsco u ca o co o s• Terminal fan coil units with Auto fan coil unit fan cycling to meet space
load. • Separate temperature set points for both cooling and heating modes • Temperature set point reset according to the building occupancy
schedule. – Use of heat recovery exchanger (50% efficiency) on the fresh air
handling unithandling unit• Recovery energy from return air using a plate heat exchanger to
reduce pre-heat need – Variable-speed pumps for chilled water distribution.Variable speed pumps for chilled water distribution.
• Variation of chilled water flow according to building load
ENERGY CONSERVATION MEASURE Study Seven: HVAC system
88,9
80
90
100
= Terminal fan savings of 70% = Cooling savings of 33% = Heating savings of 59% = Pumps (cooling of 81% & heating 23%) 122 695
140 000
47,1
30
40
50
60
70
kWh/
m²/y
r
= Pumps (cooling of 81% & heating 23%)
69 66864 995
80 000
100 000
120 000
0
10
20
Non-Eco System
EcoSystem
20 919 19 42528 698
13 567
64 995
20 000
40 000
60 000
7 152 7 152 3 530 1 061
13 5672 572
7 859 6 087
0
20 000
Bas
elin
e
0%
Bas
elin
e
-70%
Bas
elin
e
-7%
Bas
elin
e
-59%
Bas
elin
e
-81%
Bas
elin
e
-23%
Bas
elin
e
-47%
Air Handling Unit Terminal Fans Cooling Heating Pumps(Cooling)
Pumps(Heating)
Non Eco System
Eco System
POTENTIAL SAVINGS OF ~41,8 KWH/M²/YEAR OFFERING ANOVERALL SYSTEM REDUCTION OF 47%
EUROPEAN LOCATION SIMULATIONS
Gothenburg
London
Brussels
Munich
Lyon
Madrid
Athens
SIMULATIONS REPEATED ACROSS EUROPEAN LOCATIONS
Rome
SIMULATIONS REPEATED ACROSS EUROPEAN LOCATIONS
EUROPEAN LOCATION SIMULATIONS Selected study comparisons
Terminals with auto-fan cycling, communicating controls with seperate
l & h t t i t & Fresh Air Handling with heat recovery Combined effect of measures in studys
Study 1 Study 2 Study 3 Study 7
-10,0%
0,0%
cool & heat set-point & occupancy scheduling
Fresh Air Handling with heat recovery exchanger (50% efficiency) Variable speed chilled water pumps
Combined effect of measures in studys 1,2 & 3.
40 0%
-30,0%
-20,0%
-60,0%
-50,0%
-40,0%
-70,0%
ATHENS, GREECE ROME, ITALY MADRID, SPAIN LYON, France
LONDON, UNITED KINGDOM BRUSSELS, BELGIUM MUNICH, GERMANY GOTHENBURG, SWEDEN
COMBINATION OF ENERGY MEASURES RESULTS IN ~38-65% SYSTEM SAVINGS
ENERGY EFFICIENT SOLUTIONS Conclusions
• Require a system carefully q y yselected based upon building & application needs
• Incorporating optimised• Incorporating optimised equipment components at product and system level controls to maximisecontrols to maximise performance and minimise energy consumption.
• Integrate energy conservaition methods
• SERVICE & MAINTAIN!SERVICE & MAINTAIN!
ESSENTIAL STEPS TO ENSURE EFFICIENT PERFORMANCE & COMFORT CONDITIONS FOR OCCUPANTS
HYDRONIC SOLUTION Summary
• Offer a wide range of Energy Conservation Opportunities toOffer a wide range of Energy Conservation Opportunities to minimise building energy consumption.
• Significant economies may be achieved by designing in energy-isaving measures.
• Evaluate savings at the system level. • Communicating controls are fundamental to ensure economicalCommunicating controls are fundamental to ensure economical
occupancy comfort. • Building designs will become more energy-efficient, reducing the
d f h ti d lik l th t f li h til tineed for heating and likely that of cooling, however ventilation systems will become increasing sophisticated and important to integrate from a system approach.
CORRECTLY DESIGNED HYDRONIC SYSTEMS OFFER OCCUPANT COMFORTCORRECTLY DESIGNED HYDRONIC SYSTEMS OFFER OCCUPANT COMFORT AND ENERGY-EFFICIENT BUILDING SOLUTIONS.
BACK-UP SLIDES
HOURLY ANALYSIS PROGRAM (HAP) Load Estimating capabilities and procedures. p• Building loads are calculated for three different purposes in HAP.
– Design cooling conditions to size cooling equipment. – Design heating conditions to size heating equipment. – During the whole year building simulation in the energy analysis portion of HAP.
• Different procedures and considerations are used when computing building loads. – Design Cooling.
• Load profiles are computed for one design cooling day in each month using design weather conditions , design day operating schedules and the ASHRAE-endorsed Transfer Function load calculation method.
– Design weather data uses design temperature data, coincident humidity levels and clear sky solar radiation conditions. – Design day operating schedules represent the variation of internal heat gains for design cooling conditions. – The Transfer Function load method provides accurate estimates of building loads considering the transient nature of heat transfer
processes in the building. – Design Heating
• Loads are computed for a single heating design condition using winter design weather conditions, neglecting all sources of heat gain, and using instantaneous load assumptions for transmission and infiltration load components.
– Design weather data represents the winter design temperature. – Sources of heat gain are neglected so that a worst-case heating load can be calculated. – The instantaneous load procedure assumes transmission and infiltration heat losses are immediately converted to heating loads.
– Energy SimulationsEnergy Simulations• Loads are computed for all 8,760 hours in the year using simulation weather data, operating schedules for the different days
of the week, and the ASHRAE Transfer Function load method. – Actual weather data is used to evaluate how the building's HVAC systems react to real sequences of weather over the course of a
year. This is necessary to generate accurate operating cost estimates. – Operating schedules define how heat gains vary on different days of the week. – The Transfer Function load method provides accurate estimates of building loads considering the transient nature of heat transfer
processes in the building.
HOURLY ANALYSIS PROGRAM (HAP) ASHRAE Transfer Function Method
• HAP uses the ASHRAE Transfer Function Method for load calculations that comprises two calculation stages.
• First stage – uses the Room Transfer Function equations to calculate roomuses the Room Transfer Function equations to calculate room
loads as if cooling is provided 24 hours a day and the room is held precisely at the cooling thermostat set point.
• Second stageg– uses the Space Air Transfer Function (aka Heat Extraction) to
correct first stage results for actual operating conditions which involve less than 24 hours of operation and the fact that room temperature floats within the thermostat throttling range.
• Conclusion HAP performs both first and second stage calculations and– HAP performs both first and second stage calculations and therefore offers results for non-24-hour operation that are more accurate than programs such as Block Load.
ENERGY CASE STUDIES U-values in Europe
Requirements and/or recommendations on component level U-value [W/m²K] Wall Roof Floor
City Country ISO 3166-1 country code low high low high low High City Country code low high low high low High
Bruxelles Belgium BEL 0,6 0,6 0,4 0,4 0,9 1,2 Helsinki Finland FIN 0,25 0,25 0,16 0,16 0,25 0,25 Paris France FRA 0,36 0,36 0,2 0,2 0,27 0,27 München Germany DEU 0,3 0,3 0,2 0,2 0,4 0,4 A h G GRC 0 7 0 7 0 5 0 5 1 9 1 9 Athens Greece GRC 0,7 0,7 0,5 0,5 1,9 1,9 Milano Italy ITA 0,46 0,46 0,43 0,43 0,43 0,43 Oslo Norway NOR 0,18 0,22 0,13 0,18 0,15 0,18 Warsaw Poland POL 0,3 0,5 0,3 0,3 0,6 0,6 Lisboa Portugal PRT 0,5 0,7 0,4 0,5 - - Madrid Spain ESP 0,66 0,66 0,38 0,38 0,66 0,66 Zürich Suisse CHE 0,2 0,3 0,2 0,3 0,2 0,3 Goteborg Sweden SWE 0,18 0,18 0,13 0,13 0,15 0,15 Amsterdam The Netherlands NLD 0,37 0,37 0,37 0,37 0,37 0,37 London United Kingdom GBR 0 25 0 35 0 13 0 2 0 2 0 25 London United Kingdom GBR 0,25 0,35 0,13 0,2 0,2 0,25
EURIMA is the European Mineral Wool Manufacturers Association.
BEST PRACTICES: TERMINAL SOLUTIONS
BEST PRACTICES: TERMINAL SOLUTIONS
Visible Systems (in room)
42WH :High Wall • Cooling 1 2 1 kW
42N Floor Mounted • Cooling 1 7 kW
42GW Cassette • Cooling 1 – 2.1 kW
•Heating 1.8 – 3.2 kW
• Cooling 1 – 7 kW • Heating 2 – 9.8 kW
• Cooling 2 – 11 kW • Heating 4 – 14 kW
WITH CLASSIC SOLUTIONS CONTROL IS MAIN OPPORTUNITY
BEST PRACTICES: TERMINAL SOLUTIONS
D t d S tDucted Systems
ATM 42GR/ ITM 42GM : installation in technical room
cooling 2.8 to 4.1 kW 300Pa (42GR)
ICM 42BJ : installation in the
corridor (false ceiling) li 2 3 4k
ATMOSPHERA 42EM: installation in false
ceilings cooling 4 3 to 11 6 kW 300Pa (42GR)
cooling 2.3 to 4kw
150Pa Variable speed
cooling 4.3 to 11.6 kW 50Pa
HIGH TIER SOLUTIONS OFFERING MORE OPPORTUNITIESHIGH TIER SOLUTIONS OFFERING MORE OPPORTUNITIESVARIABLE SPEED & SERVICE/MAINTENANCE BENEFITS
BEST PRACTICES: FAN COIL SOLUTIONS Demand Control Ventilation (DCV)
• Classical systems deliver aClassical systems deliver a constant amount of fresh air (30m3/h for ex.) Supply Air neuf
Fresh air damper
• DCV uses a CO² sensor to analyze Co2 in the space & regulate fresh air to meet occupied
ATM Return
Sonde
CO2
regulate fresh air to meet occupied demand. – Energy economies result from
d i f h i l t t lCarrier N T
Input Output
concentratio Fresh airreducing fresh air supply to meet real occupancy of the space.
– Variable speed fans adjust precisely to l d d
New Tcconcentration CO2
Fresh air
Main components
load needs Sensor CO2 Air regulator
Electronic control
ADAPT FRESH AIR TO OCCUPATION NEEDS
BEST PRACTICES: FAN COIL SOLUTIONS Demand Control Ventilation (DCV)
2500
3000
3500
m)
CO2 ppm
1500
2000
CO
2 (p
p
Directive française 1300 ppm
0
500
1000
9:12
9:
25
9:37
9:
49
0:01
0:
13
0:25
0:
37
0:49
:0
1 :1
3 :2
5 :3
7 :5
0 2:
23
2:35
2:
47
2:59
3:
11
3:24
3:
36
3:48
4:
00
4:12
4:
28
4:40
4:
52
5:05
5:
17
5:29
5:
41
5:53
6:
05
6:17
6:
29
6:41
C 1300 ppm
09 09 09 09 10 10 10 10 10 11 11 11 11 11 1 2 12 12 12 13 13 13 13 14 14 14 14 14 15 15 15 15 15 16 16 16 16
Time
VARIATION OF CO² CONCENTRATION IN A MEETING ROOM
BEST PRACTICES: TERMINAL SOLUTIONS Chilled beam solution
• Multi service beams – cooling / heating, lighting and sprinkler services
• Applications:• Applications: • Offices with high quality design, low cooling load requirements 60/70W Froid / m2
• High comfort levels • Directionable air flow• Directionable air flow• Low noise level • Hygienic (no condensation.
• Low MaintenanceLow Maintenance• No condensate • No fan or filter
• High System efficiencyHigh System efficiency• Uses higher chilled water temperatures • Compatible applications free-cooling • AHU supplies primary fresh
– double flow (supply/extract) with heat recovery and free cooling possibilities.
OFFICE APPLICATIONS 36CB Chilled beams
BEST PRACTICES: AIR HANDLING UNITS: Optimise selection
• Selection of AHU: – Optimization of different components: – Energy class (Eurovent)Energy class (Eurovent)– Standards EN 13053 and EN 13779
• AHU velocity class • Heat recovery efficiency class y y• Mixing temperature efficiency class • Specific fan power kW/m3/s • Motors with better efficiency (EC, EFF1)
Si i (l i l LCC)• Sizing (larger size lower LCC) • Include Energy features
– Free cooling – Recirculation application with IAQ technology– Use High efficient heat recovery systems
BEST PRACTICES: AIR HANDLING UNITS Consider life cycle cost of AHU for yselection Capital
expenditure5%
Th l
Maintenance cost8%
Thermal energy humidification
17%
Thermal energy cooling
4%
Power consumption fans
52%
P
Thermal energy heating
12% Power consumption
pumps2%
12%
Source: Class V3 unit, 4 m3/s @ 500 Pa, ambient conditions De Bilt (NL), lifetime AHU 15 years, continuous operation
Around 65-85% of life cycle costs of an AHU = operation costs
BEST PRACTICES: CHILLER/HEAT PUMPS Chose Best in Class efficiency productsChose Best in Class efficiency products
EER kW/kW
> 3.10
2.90 - 3.10
2.70 - 2.90
2.50 - 2.70
Innovation L ti t
2.30 - 2.50
2.10 - 2.30
2.10
Low operating costs Low sound
Economical installation Reliability, low maintenance costs
E f ti Ease of operation Minimum environmental impact
And Options to satisfy customer needs
AQUAFORCE IS ONE EXAMPLE
BEST PRACTICES: CHILLER/HEAT PUMPS: DXFC Free cooling solution
• Supply chilled water to system without using compressors at low outdoor air temperature.low outdoor air temperature.– LCWT minus OAT > 6°C
Free Cooling Performances @ 10°C LWT)
70%80%90%
100%
25
30
35
inal
ty
kW)
10%20%30%40%50%60%
10
15
20EER
% o
f Nom
Cap
acit
EER
(kW
/k
Energy Efficiency with 13 kW cooling for 1 kW power* Simple system with pure water no glycol
Only the fans and a pump running, lower noise
0%10%
6 8 10 12 14 16 18 20 22 24 26 28 305
DT (LWT-OAT) - (°K)
Reduced Maintenance costs with less compressor run time
ELIMINATE EXTRA PUMPS, CONTROLS & GLYCOL
BEST PRACTICES: CHILLER/HEAT PUMPS Evaluate chilled water temperatureEvaluate chilled water temperature setting Leaving chilled
water of 7°C
Leaving chilledLeaving chilled water of 10°C
HIGHER TEMPERATURE = ECONOMY ~14% ENERGY CONSUMPTION
Important System Issues • Consider part load • Use smaller zonesUse smaller zones• Measure energy use • Evaluate heat recovery• Evaluate heat recovery• High efficiency filtration
