15/10/2014

1

Energy Efficiency in BuildingActive Design Part II

Presented by: CK Tang

BSEEP Component 4 ManagerVeritas Enviornment Sdn Bhd

ck.tang@veritas.com.my

Air Conditioning System

System Sizing

15/10/2014

2

Current Industry Practice

• Use rule of thumb to size Air-Conditioning?

– 200 ~ 220 Watt/m2, 80 ~ 90 Btu/ft2

• Use manual spreadsheet?

– Compute solar gain, etc?

• Use a Computer Software

– Trane software

– Carrier E-20

– Etc.

EVAPORATOR

CONDENSER COOLING TOWER

CHW

PUMP

CCW

PUMP

COOLING

COIL

FAN

FILTER

O/A INTAKE

DAMPER

SPILL AIR

DAMPER

RECYCLE

AIR

DAMPER

COMPRESSOR

Space Load

Cooling Coil Load

Chiller Load Heat Rejection Load

15/10/2014

3

Space

Cooling

Load

Cooling

Coil Load

Chiller

Load

Heat

Rejection

Load

1. Internal

Gain

2. External

Gain

3. Fan Power

4. Fresh Air

Intake

5. Duct

Conduction

Heat Gain

6. Chilled Water

Pump Power

7. Pipe

Conduction

Heat Gain

8. Chiller Power

9. Condenser

Water Pump

Power

LOAD

HEAT

Space Cooling Load

Internal Heat Gain

15/10/2014

4

People Heat Gain

Degree of Activity Sensible Heat (W/person)

Latent Heat (W/person)

Seated at theater, night 70 35

Seated, very light work 70 45

Moderately active office work 75 55

Standing, light work; walking (Department store; retail store)

75 55

Bowling 170 255

Taken from Ashrae Fundamentals @ 24°C

Lighting Heat Gain

Type/space

Type of Usage

Max. lighting power

density

W/m2

Offices 15

Supermarkets/ Department

Stores/ Shops 25

Stores/ Warehouses/ Stairs/

Corridors/ Lavatories 10

MS 1525 (2007)

Actual Installed Lighting Power Density to be used!

9.8 W/m2

8.2 W/m2

5.0 W/m2

15/10/2014

5

Equipment Heat Gain

Load Density of

OfficeLoad Factor

W/m²

Descriptions

Light 5.4

Assumes 15.5 m²/workstation (6.5 workstations per 100m²) with

computer and monitor at each plus printer and fax. Computer monitor

and fax diversity 0.67, printer diversity 0.33.

Medium 10.8

Assumes 11.6 m²/workstation (8.5 workstations per 100m²) ²) with

computer and monitor at each plus printer and fax. Computer monitor

and fax diversity 0.75, printer diversity 0.50.

Medium/Heav

y16.1

Assumes 9.3 m²/workstation (11 workstations per 100m²) with

computer and monitor at each plus printer and fax. Computer monitor

and fax diversity 0.75, printer diversity 0.50.

Heavy 21.5

Assumes 7.8 m²/workstation (13 workstations per 100m²) with

computer and monitor at each plus printer and fax. Computer monitor

and fax diversity 1, printer diversity 0.50.

Ashrae Fundamentals

External Heat Gain

Space Cooling Load

15/10/2014

6

Space

Cooling

Load

Cooling

Coil Load

Chiller

Load

Heat

Rejection

Load

1. Internal

Gain

2. External

Gain

3. Fan Power

(blow through)

4. Fresh Air

Intake

5. Duct

Conduction

Heat Gain

6. Chilled Water

Pump Power

7. Pipe

Conduction

Heat Gain

8. Chiller Power

9. Condenser

Water Pump

Power

LOAD

HEAT

Computer Compute

• Solar Gain

• Conduction Gain

• Design Weather DataDescriptions Ashrae design

weather

database v4.0

for KL

MS 1525

Recomme

nded

Test Reference

Year @ peak dry

bulb temperature

Test Reference

Year @ peak

enthalpy

Dry Bulb Temperature (°C) 35.1 33.3 35.6 30.9

Wet Bulb Temperature

(°C)26.3 27.2 25.9 28.4

15/10/2014

7

Building Envelope Properties

• Used actual building properties!

• Ask for the Solar Heat Gain Coefficient of Glazing

• Ask for the U-value of wall and roof.

• Input the Thermal Capacity of material to model thermal mass

• Have faith in Science and in the 1st Law of Thermodynamic.

Infiltration heat gain

• A measured result of 10 government office buildings in 2010 by JKR indicates– Average total fresh air in building is ~ 1 ach. – Measured highest fresh air in building is ~ 2 ach.

• Based on occupant density of 10 m2/person and 4 m of height of office spaces. – ~ 0.5 ach.

• This indicates that on average buildings have an additional infiltration of 0.5 ach.

15/10/2014

8

Exfiltration ~ 0.5 ach

Cooling Coil Load

15/10/2014

9

Space

Cooling

Load

Cooling

Coil

Load

Chiller

Load

Heat

Rejection

Load

1. Internal

Gain

2. External

Gain

3. Fan Power

4. Fresh Air

Intake

5. Duct

Conduction

Heat Gain

6. Chilled Water

Pump Power

7. Pipe

Conduction

Heat Gain

8. Chiller Power

9. Condenser

Water Pump

Power

LOAD

HEAT

15/10/2014

10

Fan Power Heat Gain

• Where

• 𝑊𝑓 = 𝐹𝑎𝑛 𝑃𝑜𝑤𝑒𝑟 (𝑊𝑎𝑡𝑡)

• 𝑄 = 𝑉𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝐴𝑖𝑟 𝐹𝑙𝑜𝑤 𝑅𝑎𝑡𝑒 (𝑚3/𝑠)

• ∆𝑃𝑡 = 𝑇𝑜𝑡𝑎𝑙 𝐹𝑎𝑛 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒, (𝑃𝑎)

• 𝜇𝑓 = 𝑇𝑜𝑡𝑎𝑙 𝐹𝑎𝑛 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 (%)

𝑾𝒇 =𝑸 ∆𝑷𝒕𝝁𝒇

15/10/2014

11

Total Fan Pressure

𝛥𝑃𝑡 = 𝑆𝑃𝑑 + 𝑃𝐷𝑎𝑓 + 𝑃𝐷𝑐 + 𝐷𝑝

Where,

• 𝛥𝑃𝑡 = 𝐹𝑎𝑛 𝑇𝑜𝑡𝑎𝑙 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 (𝑃𝑎)• 𝑆𝑃𝑑 = 𝐷𝑢𝑐𝑡 𝑇𝑜𝑡𝑎𝑙 𝑆𝑡𝑎𝑡𝑖𝑐 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 (𝑃𝑎)• 𝑃𝐷𝑎𝑓 = 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐷𝑟𝑜𝑝 𝑖𝑛 𝐴𝑖𝑟 𝐹𝑖𝑙𝑡𝑒𝑟 (𝑃𝑎)

• 𝑃𝐷𝑐 = 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐷𝑟𝑜𝑝 𝑖𝑛 𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝐶𝑜𝑖𝑙 (𝑃𝑎)

• 𝐷𝑝 = 𝐷𝑦𝑛𝑎𝑚𝑖𝑐 𝐴𝑖𝑟 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 =1

2𝜌𝑉2

• 𝜌 = 𝑎𝑖𝑟 𝑑𝑒𝑛𝑠𝑖𝑡𝑦 (1.2 𝑘𝑔/𝑚3)• 𝑉 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑎𝑡 𝑓𝑎𝑛 𝑒𝑥𝑖𝑡 (𝑚/𝑠)

Total Fan Efficiency

𝑭𝑬𝒕 = 𝑭𝒆𝒙𝑴𝒆𝒙𝑩𝒆

• Where,• 𝐹𝐸𝑡 = 𝐹𝑎𝑛 𝑇𝑜𝑡𝑎𝑙 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 (%)• 𝐹𝑒 = 𝐹𝑎𝑛 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 (%)• 𝑀𝑒 = 𝑀𝑜𝑡𝑜𝑟 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 (%)• 𝐵𝑒 = 𝐹𝑎𝑛 𝐵𝑒𝑙𝑡 & 𝑃𝑢𝑙𝑙𝑒𝑦 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 (%)• Where,• 𝐵𝑒 =100%, 𝑖𝑓 𝑓𝑎𝑛 𝑖𝑠 𝑑𝑖𝑟𝑒𝑐𝑡 𝑑𝑟𝑖𝑣𝑒𝑛 𝑏𝑦 𝑡ℎ𝑒 𝑚𝑜𝑡𝑜𝑟

15/10/2014

12

CONDUCTION HEAT GAIN FROM DUCT

Chiller Load

15/10/2014

13

Space

Cooling

Load

Cooling

Coil Load

Chiller

Load

Heat

Rejection

Load

1. Internal

Gain

2. External

Gain

3. Fan Power

(blow through)

4. Fresh Air

Intake

5. Duct

Conduction

Heat Gain

6. Chilled Water

Pump Power

7. Pipe

Conduction

Heat Gain

8. Chiller Power

9. Condenser

Water Pump

Power

LOAD

HEAT

Chilled Water Pump Power

http://activechilledbeam.com/chilled_beam_questions.asp

Where did the pump energy go to?

~90% of pump energy ends up in water

15/10/2014

14

Pump Power Input parameters

1. Design ΔT (temperature differences) of design supply and return chilled water temperature.

2. Total Pump Efficiency

3. Total Pump Head

H = Pump Head

• A factor of the followings

– Flow Rate (~ fixed by building cooling load & Design ΔT)

– Pipe Size (~ designed by consultants)

– Number and types of bends (~ proposed by contractor)

– Valves and Fittings (~ proposed by contractor/supplier)

– Chiller Heat Exchanger (~ chiller selection)

15/10/2014

15

Chilled Water Pipe Heat Gain

http://www.allredmechanical.com

To be of concern if chilled water pipe is running outdoor.

Heat Rejection Load

15/10/2014

16

Space

Cooling

Load

Cooling

Coil Load

Chiller

Load

Heat

Rejection

Load

1. Internal

Gain

2. External

Gain

3. Fan Power

(blow through)

4. Fresh Air

Intake

5. Duct

Conduction

Heat Gain

6. Chilled Water

Pump Power

7. Pipe

Conduction

Heat Gain

8. Chiller Power

9. Condenser

Water Pump

Power

LOAD

HEAT

Chiller Power consumption

http://engfac.cooper.edu/melody/411

Open Drive or Hermetic Drive.

Open drive has an electric motor that is air cooled by the ambient air.

A hermetic drive has an electric motor that is hermetically sealed and cooled with refrigerant.

15/10/2014

17

Chiller Efficiency

𝐶𝑂𝑃 =𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑃𝑟𝑜𝑣𝑖𝑑𝑒𝑑 (𝑘𝑊𝑐𝑜𝑜𝑙𝑖𝑛𝑔)

𝐸𝑙𝑒𝑐𝑡𝑟𝑖𝑐𝑖𝑡𝑦 𝐶𝑜𝑛𝑠𝑢𝑚𝑒𝑑 𝑏𝑦 𝐶ℎ𝑖𝑙𝑙𝑒𝑟 (𝑘𝑊𝑒)

𝑘𝑤 𝑝𝑒𝑟 𝑡𝑜𝑛 =12

𝐶𝑂𝑃 𝑋 3.412

Condenser Pump Power

http://www.alabamapower.com/business/save-money-energy/energy-know-how/chillers/free-cooling.asp

Also take note of direct sunlight heating up the condenser pipe!

15/10/2014

18

Pump Power Input parameters

1. Design ΔT (temperature differences) of design supply and return chilled water temperature.

2. Total Pump Efficiency

3. Total Pump Head

Energy Efficiency 1st Estimates

Simulation Studies Based on an

Office Building Scenario

17 Floors

15/10/2014

19

AIR SIDE Optimization

Energy Efficiency Estimates

Air Side Optimization

6 Items to Optimize

1. AHU Flow Rate (CAV vs. VAV)

2. AHU Total Fan Efficiency

3. AHU Total Pressure Loss

4. Optimal Design Off-coil Temperature

5. Active control of Fresh Air Intake

6. Heat Recovery Wheel and Infiltration Rate

15/10/2014

20

CAV Design ΔT Optimization

Reduced flow rate CAV System @ Part Load

Fine Tuning it based on Actual Condition can reduce significant amount of energy!

15/10/2014

21

VAV Design ΔT Optimization

CAV Vs. VAV @ Full Load

Descriptions BEI Units

CAV (at 11°C off-coil) 165.6 kWh/m².year

VAV (at 11°C off-coil) 158.6 kWh/m².year

BEI VAV improvement 7.1 kWh/m².year

% VAV improvement 4.3% Percentage

15/10/2014

22

CAV Vs. VAV @ Part Load

45% Reduction in Occupancy BEI Units

VAV at design flow rate 130.4 kWh/m².year

CAV at reduced flow rate 126.4 kWh/m².year

BEI CAV improvement 4.0 kWh/m².year

% CAV improvement 3.1% Percentage

Fan Pressure & Efficiency

15/10/2014

23

Fan Pressure & BEI

Options for Reduction of Fan Total Pressure

• Larger Ducts, Less Bends

• Selection of Fittings

15/10/2014

24

Air Filter Pressure drop

Camfil – Closed Pleat Pressure Drop Curve

Cooling Coil Pressure Drop

http://www.lytron.com/Tools-and-Technical-Reference/Application-Notes/Selecting-a-Heat-Exchanger

15/10/2014

25

Face Velocity Reduction

• 2.5 m/s down to 2.0 m/s (or lower)

Fan Efficiency & BEI

15/10/2014

26

http://www.ziehl-abegg.com/au/press-release-165.html

CO2 Sensor

Demand Controlled Fresh Air

15/10/2014

27

BEI & Actual Building Occupancy

CO2 Level Set Point

15/10/2014

28

Heat Recovery

toilets toilets

15/10/2014

29

Heat Recovery

Using toilet exhaust for fresh air intake

15/10/2014

30

WATER SIDE

Water-Side Optimization

4 Items to Optimize

1. Chilled Water Distribution Energy Efficiency

2. Chiller Energy Efficiency

3. Condenser Water Distribution Energy Efficiency

4. Cooling Tower Energy Efficiency

15/10/2014

31

Chilled Water Distribution

Options Studied

1. System Selection

• Primary Constant Flow

• Primary Constant/Secondary Variable Flow

• Primary Variable Flow

2. High ΔT Chilled Water Distribution

3. Low Pump Head

4. High Pump Efficiency

Base

-5.0

-3.7-3.3

-2.8-2.3

152

153

154

155

156

157

158

159

160

161

PrimaryConstant

Primary Variable PrimarySecondary

PrimarySecondary

(pump poweradd 10%)

PrimarySecondary

(pump poweradd 20%)

PrimarySecondary

(pump poweradd 30%)

BEI

(kW

h/m

2.y

ear)

Chilled Water Distribution System @ Specific Pump Power of 545 W per l/s

15/10/2014

32

High ΔT Chilled Water distribution

𝐻 = 1.16 𝑄 ∆𝑇Where,H = heat load (kW) (building cooling load)Q = water volume flow rate (m3/h)ΔT = temperature difference (oC)

Rewriting,

𝑄 =𝐻

1.16 ∆𝑇

Issues to consider for high ΔT Design option

• Pipe Sizes:– Reduction in sizes, reduces capital cost,

while maintaining the same pump head. Or, – Maintain pipe sizes, while reducing pump

head, increasing efficiency.

• Chilled Water Supply Temperature:– Reduced temperature, reduces chiller

efficiency, i.e. • 6.67°C to 5.56°C (44°F to 42°F)

• Chilled Water Return Temperature:– Increased ΔT, increases cooling coil sizes in

AHU, increasing capital cost.

15/10/2014

33

Base

-1.2

-2.0-2.7

-1.9

Base-0.4 -0.7 -0.9 -0.6

150

152

154

156

158

160

DT 12F (44/56F) DT 14F (44/58F) DT 16F (44/60F) DT 18F (44/62F) DT 16F (42/58F)

BEI

(kW

h/m

2/ye

ar)

Chilled Water Temperature Different

Pump Head Constant (~Pipe Size Reduced)

Primary Constant Primary Variable

Base-0.4 -0.7 -0.9 -0.6

Base

-1.1-1.7

-2.1-1.6

150

152

154

156

158

160

DT 12F(44/56F)

DT 14F(44/58F)

DT 16F(44/60F)

DT 18F(44/62F)

DT 16F(42/58F)

BEI

(kW

h/m

2.ye

ar)

Chilled Water Temperature Different

Primary Variable System

Pump Head Constant Pump Head Reduced

Pipe Sized Down, Maintaining Pressure

Pipe Size Maintained, Reducing Pressure

15/10/2014

34

Pump head and efficiency

Pump power Equation

𝑷𝒉 =𝒒 𝝆 𝒈 𝒉

𝟑. 𝟔𝒙𝟏𝟎𝟔 𝒙 𝝁

𝜌 = 𝑓𝑙𝑢𝑖𝑑 𝑑𝑒𝑛𝑠𝑖𝑡𝑦 (𝑊𝑎𝑡𝑒𝑟 = 1,000 𝑘𝑔/𝑚3)

𝑔 = 𝑔𝑟𝑎𝑣𝑖𝑡𝑦 (9.81 𝑚2/𝑠)

ℎ = 𝑃𝑢𝑚𝑝 𝑇𝑜𝑡𝑎𝑙 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 (𝑚 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟)

𝜇 = 𝑃𝑢𝑚𝑝 𝑇𝑜𝑡𝑎𝑙 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 (%)

𝑃ℎ = 𝑃𝑢𝑚𝑝 𝑃𝑜𝑤𝑒𝑟 (𝑘𝑊)

𝑞 = 𝐹𝑙𝑜𝑤 𝐶𝑎𝑝𝑎𝑐𝑖𝑡𝑦 (𝑚3/ℎ)

15/10/2014

35

Specific pump power

Rewriting it… into

Specific Pump Power

𝑃 =𝜌 𝑔 ℎ

𝜇 𝑥 1000= 9.81 ℎ

𝜇

𝑃 = Specific Pump Power (W per l/s)

𝜌 = 𝑓𝑙𝑢𝑖𝑑 𝑑𝑒𝑛𝑠𝑖𝑡𝑦 (𝑊𝑎𝑡𝑒𝑟 = 1,000 𝑘𝑔/𝑚3)

𝑔 = 𝑔𝑟𝑎𝑣𝑖𝑡𝑦 (9.81 𝑚2/𝑠)

ℎ = 𝑃𝑢𝑚𝑝 𝑇𝑜𝑡𝑎𝑙 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 (𝑚 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟)

𝜇 = 𝑃𝑢𝑚𝑝 𝑇𝑜𝑡𝑎𝑙 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 (%)

15/10/2014

36

y = 0.0059x + 151.93R² = 0.9998

152

153

154

155

156

157

158

100 200 300 400 500 600 700 800

BEI

(kW

h/m

2.y

er)

Specific Pump Power (W per l/s)

Chilled Water Pump Efficiency @ ΔT 6.67°C (44/56°F)Primary Variable System

Reducing Specific Pump Power by 100 W per l/s, reduces BEI by100 x 0.0059 = 0.6 kWh/m2.year

Pump Head Optimization

• A factor of the followings

– Flow Rate (~ fixed by building cooling load & Design ΔT)

– Pipe Size (~ designed by consultants)

– Number and types of bends (~ proposed by contractor)

– Valves and Fittings (~ proposed by contractor/supplier)

– Chiller Heat Exchanger (~ chiller selection)

15/10/2014

37

Priorities

1. Specific Pump Power Reduction

– Pump Head

– Pump Efficiency

2. Primary Variable Flow or Primary/Secondary Flow

3. High ΔT & Maintain pipe size.

Chiller Efficiency

15/10/2014

38

Chiller Efficiency

𝐶𝑂𝑃 =𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑃𝑟𝑜𝑣𝑖𝑑𝑒𝑑 (𝑘𝑊𝑐𝑜𝑜𝑙𝑖𝑛𝑔)

𝐸𝑙𝑒𝑐𝑡𝑟𝑖𝑐𝑖𝑡𝑦 𝐶𝑜𝑛𝑠𝑢𝑚𝑒𝑑 𝑏𝑦 𝐶ℎ𝑖𝑙𝑙𝑒𝑟 (𝑘𝑊𝑒)

𝑘𝑤 𝑝𝑒𝑟 𝑡𝑜𝑛 =12

𝐶𝑂𝑃 𝑋 3.412

15/10/2014

39

Caution on chiller study

• DOE-2 Chillers Performance Curve-Fit– Centrifugal Chiller based on chillers manufactured

around 1975. • Newer centrifugal chiller can be significantly more

efficient at part load.

– Screw Chiller curve-fit was updated recently. • ~ 2006 updated

– VSD Chiller curve-fit is the latest introduction. • ~ 2006 introduced.

• Based on a frictionless centrifugal chiller.

Condenser Pump Efficiency

15/10/2014

40

High ΔT Condenser Flow Rate

• Typical Design: 95/85°F (35/29.44°C)– Flow Rate: 2.4 gpm/ton

• Higher Condenser Flow Rate– Chiller efficiency is better – But, Pump power increases

• Condition Tested:– 93/85°F (33.9/29.4°C) – 3.0 gpm/ton– 95/85°F (35/29.4°C) – 2.4 gpm/ton– 97/85°F (36.1/29.44°C) – 2.0 gpm/ton

@ 2.0 gpm/ton, a reduction of 100 W per l/s, reduces BEI by:100 x 0.0233 = 2.3 kWh/m2.year

15/10/2014

41

Cooling Tower Fan Efficiency

Reduction of 0.01 kWe/HRT = 0.01 x 146.92 = ~ 1.5 kWh/m2.year reduction

Variable Speed Fan Cooling Tower @ Different Set Point Water Leaving Temperature.

15/10/2014

42

Cooling Tower summary

Bridging Design and Actual Operation Performance

15/10/2014

43

Common Installation Issues

Install It Right!

Air Leakages

• Main Doors

• Missing Partition above false ceiling

– Porous walls

• Duct leakages

• Missing dampers in smoke ventilation ducts

• No seals between windows frame and wall

15/10/2014

44

Piping and Ducting Layout

What is wrong with this picture?

http://sustainability.csusb.edu/Projects/centralCoolingSystemUpgrades.html

Straight length of pipe before pump suction inlet

Note the Flat Top Eccentric Reducer used to avoid air pocket at suction inlet.

15/10/2014

45

15/10/2014

46

Appoint Building Energy Manager

• Need to appoint someone to take charge.

Commissioning vs. TAB

• TAB = Testing, Adjusting and Balancing• Commissioning = Professional Service for Energy

Efficiency in Building– Owner’s Project Requirement– Design Intent Commissioning Plan– Basis of Design– Commissioning Specifications– Contract Review– Submittal Review– TAB before handing over– Handing Over– Periodic Testing Plan– Training of Facility Manager

15/10/2014

47

Fine-Tuning

• Match building to actual occupants’ requirements while optimizing efficiency. – Lighting schedule

– Air-Conditioning schedule

– Sensors Calibration

– Temperature Set-Point

– Air Rebalancing

– Computer & Equipment Settings

– Occupant’s Awareness Campaign

Continuous Monitoring

1. Sub-meters

2. Energy Management System

15/10/2014

48

Energy Management System

• Line Charts

• Bar Charts

• Daily• Weekly• Monthly• Yearly

The End