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Seite 1 1
Professor Bjarne W. Olesen, PhD Director
International Centre for Indoor Environment and Energy Department of Civil Engineering Technical University of Denmark
Possibilities and limitations for using water based radiant heating and cooling systems.
International Centre for Indoor Environment and Energy
The 20-20-20 EU policy by 2020
Greenhouse gas levels
Energy consumption
Renewables in energy mix
-20% -20% 100%
20%
8,5%
Comprehensive set of legislation to enhance energy efficiency
l
. Directive for the taxation of energy products and electricity
Revision in 2008 . Energy end-use efficiency and energy services Directive Services
. Directive on the promotion of cogeneration Generation Buildings . Energy performance of buildings Directive (EPBD)
. Directive establishing a framework for the setting of eco-design requirements for energy-using products (implementing directives for e.g. boilers, refrigerators, freezers and ballasts for fluorescent lighting
Eco-Design
. Directives for labelling of e.g. electric ovens, air-conditioners, refrigerators and other domestic appliances . Regulation of Energy Star labelling for office equipment Product Labelling
Taxation 3/14
Energy Performance of Buildings Directive – EPBD (2002/91/EC) l
Requirements - for Member States to specify and implement:
§ An integrated methodology to rate the energy performance of
buildings
§ Minimum energy performance standards for new and for
existing buildings that undergo major renovation
§ Energy performance certificates for buildings
§ Regular inspections of boilers and
air-conditioning systems
4/14
Seite 2 2
EPBD – Energy Performance Certificate lExample for Member States’ room for manoeuvre:
5/14
Achieving Excellence in Indoor Environmental Quality
• Physical factors – Thermal Comfort – Air quality (ventilation) – Noise-Acoustic – Illumination
• Personal factors – Activity – Clothing – Adaptation – Expectation – Exposure time
Energy Efficient Technologies
• Indoor air quality – Pollution sources – Air distribution (contaminant removal) effectiveness – Personal ventilation – Air cleaning
• Thermal comfort – Low Temperature Heating- and High Temperature Cooling Systems – Thermo-Active-Building-Systems (TABS) – Drifting temperatures
No cooling – decreased performance Low energy costs Low operation costs
Full Air-Conditioning Constant temperature Draught, Noise, SBS High energy costs High operation costs
Thermo-Active-Building-Systems Temperature ramps Reasonable energy costs Low operation costs
COMFORT-PERFORMANCE
Seite 3 3
CONCEPTS OF RADIANT HEATING AND COOLING SYSTEMS
• Heating - cooling panels • Surface systems • Embedded systems
HISTORY Frank Lloyd Wright's Usonian Houses 1930’s
A lightweight floor slab was used and the traditional basement was dispensed with. By using steam or hot water piping, it became possible to heat the floor, therefore eliminating the need for radiators. The overall result was heat without a draft or temperature variation of the most comfort - cool head and warm feet.
c. 10,000 B.C., China, the word “kang,” can be traced back to the 11th century B.C. and originally meant, “to dry” before it became known as a heated bed. c. 5,000 B.C., evidence of baked floors are found foreshadowing early forms of “kang” and “dikang” (heated floor) later “ondol” (warm stone) in China and Korea, respectively.
c. 10,000 B.C., China
HISTORY
Hypocausts were used from the third century B.C. in ancient Europe.
c. 1904, Liverpool Cathedral heated with system based on the hypocaust principles.
Suspended cooled ceilings
Seite 4 4
Radiant surface heating!and cooling systems!
Floor! Wall!
Thermo Active Building Systems!
Ceiling!
The image cannot be displayed. Your computer may not have Reinforcement!
Floor!
Concrete! Pipes!
Room!
Room!
Window!
Embedded piping systems
• Free use of space • No cleaning • Safety • Comfort • Energy
6/24/11 Bjarne W. Olesen, ICIEE-DTU 15
Low-Temperature heating High-Temperature Cooling
• Higher efficiency of boilers and chillers • Lower distribution losses • Better use of renewable energy sources • Low energy consumption for circulation • Future flexibility • Low Exergy
THERMAL COMFORT
• -0,5 < PMV < +0,5 ; PPD < 10 %
• Spaces with sedentary work : – Summer clothing 0,5 clo – Winter clothing 1,0 clo – Activity level 1,2 met
• OPERATIVE TEMPERATURE • WINTER 20 °C (68F)< to < 24 °C(75.2F) • SUMMER 23 °C (73.4F) < to < 26 °C (78.8F).
Seite 5 5
OPERATIVE TEMPERATURE
– to = (hcta + hrtr)/(hc + hr) – to = 0.5ta + 0.5tr ( low air velocity)
» ta = Air temperature » tr = Mean radiant temperature » hc = Convective heat exchange coefficient » hr = Radiative heat exchange coefficient
Mean Radiant Temperature
• tr = ΣFp-i tsi – Fp-i = Angle factor from person to surface i – tsi = Surface temperature of surface i – ΣFp-i = 1
Seite 6 6
Angle factor
00,050,10,150,20,250,30,350,40,45
Gulv Loft Vindue Brystning Bagväg SidevägFloor Ceiling Window Out. Wall Back Wall Side Wall
SURFACE HEATING AND COOLING Heat transfer coefficient
8,08,0
6,0
11,011,0
7,0
5,56,5
7,5
8,5
9,5
10,5
11,5
Floor
Ceiling
Wall
W/m2K
Heating Cooling
6/24/11 23
SURFACE HEATING AND COOLING Max. - Min. Surface temperature
40
17
27
17
35
20
29
20
15
20
25
30
35
40
45
Floor
Ceiling Wall
oC
Heating Cooling
Perimeter
6/24/11 24
MAXIMUM HEATING AND COOLING CAPACITY
160
72
42
99
165
42
99
42
020406080100120140160180200
Floor
Ceiling Wall
Heating Cooling
Perimeter
W/m2
Seite 7 7
ISO/TC 205/WG 8 Radiant Heating & Cooling System
ISO/DIS 11855-1 ISO/DIS 11855-2 ISO/DIS 11855-3 (July) ISO/DIS 11855-4 ISO/CD 11855-5 ISO/CD 11855-6 (July)
1. Screed 2. Pipes 3. Plastic foil 4. Insulation 5. Levelling 6. Concrete
ALUMINUM HC device: Floor Heating & Cooling (type B), R=0.01~0.1, T=150 & 300
0
20
40
60
80
100
120
140
160
-15 -10 -5 0 5 10 15 20 25 30Heating/cooling medium differential temperature ΔθH=θH-θi [°C]
Hea
t exc
hang
e [W
/m2]
T=150, R=0.01T=150, R=0.1T=300, R=0.01T=300, R=0.1
Figure 4.17 Heat exchange between the surface (with ceramic tiles, wooden
parquets or carpet R?B=0.1 and no covering R?B=0) and the space when aluminium heat conductive device used
Heating/ cooling capacity, EN1264 and EN 15377
Seite 8 8
Wood constructions
6/24/11 30
Finite Element Method
Radiant Floor Cooling
Radiant Floor Cooling
OPERA HOUSE
SHOPPING CENTER MUSEUM
AIRPORT
Seite 9 9
Slide 33
Opera House in Copenhagen Cooling
• 2,5 MW cooling capacity • 2 systems – 10/15°C and 15/18 °C • Free cooling from sea water • Combined radiant floor heating + radiant
floor cooling • 18 km underfloor cooling tubing • Quiet cooling walls • De-humidification Condensing coils for
ventilation
BBI airport, Berlin, Germany. 76,750 m² to be heated/cooled with floor system
• The in-city airports in Berlin will be closed and replaced by the new BBI
• In future, up to 6,500 persons will be starting or landing at the new airport in a typical hour.
• There will be a floor heating/cooling realized in 2010
Airport Bangkok HEAT LOADS
• Once the heat load to the space had been determined, the conditioning system was being developed.
• The loads for the concourse were 97 W/m2 • The conditioning systems to remove this heat from the
space was divided as follows: – Radiant Floor 80 W/m2 – Ventilation Air 17 W/m2
Seite 10 10
Airport Bangkok Airport Bangkok
VENTILATION
• The outdoor air AHU will supply variable outdoor air quantities at a constant temperature to the zone AHU’s.
• The volume of outdoor air will be varied depending upon the CO2 levels metered in each zone, down to a fixed minimum position
• Each zone AHU can supply air at 16 C to the space via the displacement diffusers
Ta = 16 oC Td = 10 oC
TsupplyW = 13 oC
Seite 11 11
Airport Bangkok TABS Thermo Active Building Systems
Insulation!Floor!
Concrete!
Reinforcement!
Pipe!
Room!
Room!
Window!
Concept of Thermo Active Building Systems
Seite 12 12
The analysed building
West room
Width of the room: 3.6 m
Window portion of the outside wall: 50%
Office building
Slab used in simulation Convegno Internazionale AICARR
Prof. Bjarne W. Olesen, International Centre for Indoor Environment and Energy, DTU
Sun protection
Sun protection: Only during occupation and direct exposure of sunlight and operative temperature above 23 °C, reduction factor 0.5
®VENTILATION RATES
During time of occupancy: 1.5 ach
Outside time of occupancy:1.5 ach
Seite 13 13
CONTROL OF WATERTEMPERATURE • Supply water temperature is a function of outside
temperature according to the equation:
• Average water temperature is a function of outside
temperature according to:
• Average water temperature is constant and equal to: 22°C in summer and 25°C in winter.
• Supply water temperature is a function of outside temperature according to the equation:
( ) )22(*6,12020*52,0sup −−+−= oexternalply ttt °C (case 801)
( ) )22(*6,12020*52,0 −−+−= oexternalaverage ttt °C (case 901)
( ) 1818*35,0sup +−= externalply tt °C summer (case 1401) ( ) 1818*45,0sup +−= externalply tt °C winter (case 1401)
PERFORMANCE EVALUATION
• Range of operative temperature • Pump running time • Energy consumption
Operative temperature range, May to September Different control concepts for water temperature, Time of operation 18:00 - 6:00 Uhr
33
14
54 54 52
38
0
10
20
30
40
50
60
70
80
90
100
Tsup =Tdp
Pump Tsup =F(ext)
Pump Tavg =F(ext)
Pump Tavg =22 °C
Pump Tavg =20 °C
Pump Tavg =18 °C
Pump
Control of water temperature
Ope
rativ
e te
mpe
ratu
re ra
nge
[%]
>27
26-27
25-26
22-25
20-22
Seite 14 14
Comparison with the norm DIN 1946-part 2
19
20
21
22
23
24
25
26
27
28
-12 -10 -8 -6 -4 -2 0 2 4 6 8 10 12 14 16 18 20 22 24 26 28 30 32
Outdoor Temperature [°C]
Indo
or O
pera
tive
Tem
pera
ture
[°C
]
Venezia fall16
Comparison with the norm DIN 1946-part 2
19
20
21
22
23
24
25
26
27
28
-12 -10 -8 -6 -4 -2 0 2 4 6 8 10 12 14 16 18 20 22 24 26 28 30 32
Outdoor Temperature [°C]
Indo
or O
pera
tive
Tem
pera
ture
[°C]
Venezia fall17
Circulation pump on at 18:00 Sunday
Circulation pump on 10:00 Sunday
CONTROL OF WATER TEMPERATURE SUMMER
Operative temperature May to September
Water temperature control. Time of operation 6 pm to 6 am
26 36
26 30 33 39
32 34
0 10 20 30 40 50 60 70 80 90
100
Tsup= f(Ti,Te) Tave= f(Ti,Te) Tave=
22 °C Tsup= f(Te) Tsup= f(Ti,Te) Tave=
f(Ti,Te) Tave= 22 °C Tsup= f(Te) Control methods
Ran
ge o
f ope
rativ
e te
mpe
ratu
re %
>27 26-27 25-26 22-25 20-22
Seite 15 15
ART MUSEUM IN BREGENZ
• Design requirements – Air temperature variations during a day within 4 K – Relative humidity variations less than 6 % during a day. – Seasonal variations between 48 and 58 % – Room temperature in winter 18 oC to 22 oC – Room temperature in summer 22 oC to 26 oC, occasional up to 28 oC
• Design load 250 persons pr. day, 2 hours • Displacement ventilation < 0,2 h-1 • Floor area 2.800 m² , 4 floors • 28.000 m plastic pipes embedded in walls and floor slabs
ART MUSEUM BREGENZ
• 3.750 m² floor area • 4.725 m² embedded pipes
• Condensing boiler
• Ventilation 750 m3/h per floor (first design was 25.000 m3/h
ART MUSEUM IN BREGENZ ART MUSEUM BREGENZ
Seite 16 16
ART MUSEUM BREGENZ
Offices M+W Zander Stuttgart, Germany - TABS –
- in 6.500 m2
MW-Zander Measurements during normal operation
Operative temperature sensor
Air temperature sensor
Transmitters
Seite 17 17
Stuttgart
Stuttgart 24.07. - 28.07, 2000
20
21
22
23
24
25
26
24. J
ul
24. J
ul
25. J
ul
25. J
ul
26. J
ul
26. J
ul
27. J
ul
27. J
ul
28. J
ul
28. J
ul
29. J
ul
Zeit
Tem
pera
tur [
°C]
O1-Operative Büro 4. Stock Fenster-Ost F1-Fläche 4. Stock RucklaufO-Operative Büro 5. Stock Fenster-West O6-Operative Büro 5. Stock Fenster-Ost
Energy concept in BOB.1 Temperatures for one year in BOB.1
Seite 18 18
cooling period in BOB.1 Heating period in BOB.1
0
5000
10000
15000
20000
25000
30000
35000
Heizung Kühlung Lüftung Beleuchtung Pumpen Warmwasser Summe
Yea
rly e
nerg
ie c
osts
[€/m²a
]
BestandBOB.1
Energy efficiency
94 % energy saving compared with conventional cooling
60 % energy saving for lighting by daylight steering
The need of energy for heating, cooling, air-ventilation lighting and warm water is 27,8 kWh/m² per year
Energy costs per m², per year: 2,7 EUR, per month 22,5 Cent
Heat pump
Free Cooling and line up to a reversible Heat Pump, A - free cooling by means of ground coupling (cca 10-25 W/m) B - possibel to obtain much higher cooling
capacity by using reversible heat pump
Seite 19 19
Influence of condensing temperature on COP
0.0
0.5
1.0
1.5
2.0
2.5
3.0
3.5
4.0
4.5
5.0
30 40 50 60Temperature, condenser (°C)
COP
Evaporation - 5°C
Absorption Heat Pump
Cooling by using Absorption Heat Pump supported by Solar Heat, 1 - cooling tower, 2 - control system unit, 3 - Solar collector, 4 - buffer tank, 5 - additional heating, 6 –
absorptive heat pump, 7 - floor heating system
Ground Heat Exchanger
a - ground well (hole), b - , c - gap wall,
d - ground collector, e - plate floor cooler, f- soil cooler
BoilerChiller
Temperature-Humidity
Outsidetemperature
Floor temp.
Supply Limiter
ReturnMixing valve
Shut off valves
Control
Room sensor Control unit
Valve
Manifold
Pump
Control of a combined floor heating-cooling system
with individual room control
Seite 20 20
SELF CONTROL
80W/m?
40W/m?
20W/m?
10W/m?
Heat load
FloortemperatureHeat. level temp. tiles
Heat. level temp. carpet
38,4
29,4
24,922,5
31,9
26,2
23,321,7
27,3
23,922,1
21,12022242628303234363840
C°
Floortemperature at 20 °C RoomtemperaturedegC F18 64,419 66,220 6821 69,822 71,623 73,424 75,225 7726 78,827 80,628 82,429 84,230 86
PRE- FABRICATION
Low Exergy Hydronic Radiant Heating and Cooling Why?
• Water based systems
• Low temperature heating - High temperature cooling • More economical to move heat by water:
– Greater heat capacity than air – Much smaller diameter pipes than air-ducts – Electrical consumption for circulation pump is lower than for fans
• Lower noise level • Less risk for draught • Lower building height • Higher efficiency of energy plant • But
– Reduced capacity? – Acoustic? – Latent load?
Seite 21 21
International Centre for Indoor Environment And Energy
THANK YOU