37. Driving Mechanisms for Infiltration
Stack effect ‐ Air density differences due to indoor and outdoor
air temperatures
Wind pressure
Building cracks and openings
38. Realistic Infiltration Estimate Method
Actually occurs at the perimeter façade
Practical calculation ‐ based on façade area & expected air‐
tightness (Typical facade air‐tightness values 0.6 – 1.4 L/s.m² facade area at 50 Pa)
In reality, occurs at all times and can be positive or negative
depending on wind conditions; generally an average value is
used
Can be suppressed to some extent by pressurization of the
building
39. Estimating Infiltration
Maximum Average Air Infiltration rates in Air Changes per hour (AC/h)
CIBSE Guide A –
Table ref.
Building ‘Leaky’ building
Moderately
‘tight’ building
Table 4.15 Office : Air conditioned, 2000–8000m2 0.60 0.20
Table 4.16
Office : Air conditioned HQ‐type building, 4000–
20000 m2 0.65 0.25
Table 4.17 Factories, Warehouses, Halls 0.65 0.25
Table 4.18 Schools 0.70 0.25
Table 4.19 Hospitals and Health Care buildings 0.60 0.25
Table 4.20 Hotels 0.85 0.30
Table 4.21
Dwellings – 1 floor 1.15 0.40
Dwellings – 2 floors 1.00 0.35
Apartments – 1 to 5 floors 1.00 0.50
Apartments – 6 to 10 floors 1.60 0.55
48. Dynamic Thermal Model
o Thermal templates are created and assigned to the room spaces and zones.
o Incorporate internal heat gain data specific to the space.
50. Dynamic Thermal Model
Dynamic thermal model utilizes profiles for internal gains
Peak loads of different zones do not occur at corresponding times
When considering peak coincidental load, many of the variable peaks do
not occur at corresponding times
In static load calculations, these variable peaks are summated
0
500
1,000
1,500
2,000
2,500
3,000
Internal gain
(kW)
Solar gain (kW) External
conduction gain
(kW)
Infiltration gain
(kW)
Sensible Cooling
Load (kW)
Total Cooling
Load (kW)
1,723
280 371 259
2,213
2,633
1,253
245 346 244
1,868
2,025
100% Static Model
Profiled Dynamic Model
51. Fresh (Outdoor) Air Management
Fresh air treatment (tempering) can constitute 30 ‐ 40% of the total
cooling load
1.0 m³/sec of fresh air = 40 kW / 11.5 TR cooling energy with energy
recovery devices
1.0 m³/sec of fresh air = 72 kW / 20.5 TR cooling energy without energy
recovery devices
Fresh air distribution sizing will be based upon 100% zonal requirements
but they will not necessarily occur simultaneously
To minimize impact on plant capacity & operating cost:
Use energy recovery devices (Heat wheel, Run‐around‐coil, Heat pipe, etc.)
Variable volume fresh air distribution system (VFD fans)
Demand controlled fresh air (Use of CO2 sensors)
Occupancy profiles for the respective spaces (Timed operation)
52. Design Margins
Cooling loads ‐ 10% on sensible load; 5% on latent load
Flows ‐ 5% on calculated value
Pressure ‐ 10% on calculated value
Terminal equipment ‐ 5 to 10% over zone cooling load
On site cooling plant ‐ 10% over coincidental cooling load
District cooling service ‐ 0% on coincidental cooling load
(even slightly under‐subscribing DC service is in order)
53. 0.90 1.10 1.60 1.40 1.80
District cooling
system
Water cooled
chiller system
Air cooled chiller
system
Air cooled VRF
system
Split AC system
kW/TR
Costs ‐ Cooling Systems
‐
2,000
4,000
6,000
8,000
10,000
12,000
14,000
16,000
District cooling
system
Water cooled chiller
system
Air cooled chiller
system
Air cooled VRF
system
Split AC system
QAR/TR
District cooling system
Water cooled chiller system
Air cooled chiller system
Air cooled VRF system
Split AC system
58. 58
Design Principles ‐ Recap
o Use correct external and internal design temperatures
o Select right fenestration materials
o Design heat resistant external walls and roof
o Select energy efficient lighting luminaires
o Adopt correct dynamic occupancy & activity levels
o Use established equipment heat gains
o Allow infiltration based on façade area & expected air‐tightness
o Undertake dynamic thermal modeling