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Building Energy Saving through Optimization
and Life-cycle Commissioning
– The Approach and Experiences in ICC
CPD Technical Seminar, CIBSE (Hong Kong Branch), ASHRAE
(Hong Kong Chapter) and HKIE (BS division)
17, March 2010, Hong Kong
Shengwei Wang (王盛衛王盛衛王盛衛王盛衛)
Chair Professor of Building Services Engineering
Department of Building Services Engineering
The Hong Kong Polytechnic University
A Simple View of Energy Saving Potentials for Building A Simple View of Energy Saving Potentials for Building A Simple View of Energy Saving Potentials for Building A Simple View of Energy Saving Potentials for Building
HVAC&R Systems in OperationHVAC&R Systems in OperationHVAC&R Systems in OperationHVAC&R Systems in Operation
Building Energy SavingBuilding Energy SavingBuilding Energy SavingBuilding Energy Saving
HVAC&R SystemsEnergy Saving Potential
System, component and BAS
commissioning and diagnosis
20~30%Saving Potential
10~20%Saving Potential
System operation and
Control Optimization
- HVAC, lighting, lift, …
Design: Configuration,
Components selection, etc.
Outline of Presentation
• Introduction to ICC building systems;
• Our roles in ICC project;
• The concept of “commissioning”
• Examples of commissioning efforts at design,
installation, T&C and operation stages;
• Saving Energy through Control Optimization
control strategies implemented
examples of control strategies
• Summary of energy benefits
• Summary of experiences in ICC
International Finance Centre (ICC)International Finance Centre (ICC)
490 m
118 F
Six-star Hotel
High-rank
commercial
office
Commercial center and
basement
Floor Area:
Hotel 70,000 (m2)
Office 286,000 (m2)
Commercial center
67,000 (m2)
Gross 440,000 (m2)
EVAPORATOR EVAPORATOR EVAPORATOR EVAPORATOREVAPORATOR
COOLING
TOWER 2
COOLING
TOWER 4
COOLING
TOWER 3
COOLING
TOWER 6COOLING
TOWER 5
COOLING
TOWER 8COOLING
TOWER 7
COOLING
TOWER 1
COOLING
TOWER 11COOLING
TOWER 9
COOLING
TOWER 10
EVAPORAROR
WCC-06a-01
(2040 Ton)
PCHWP-06-01
FROM OFFICCE FLOORS(7-41)
TO OFFICE FLOORS(7-41)
HX HX HX HX HX HX HX
PCHWP-06-02 PCHWP-06-03 PCHWP-06-04 PCHWP-06-05 PCHWP-06-06
WCC-06a-02
(2040 Ton)
WCC-06a-04
(2040 Ton)WCC-06a-03
(2040 Ton)
WCC-06a-05
(2040 Ton)WCC-06a-06
(2040 Ton)
CDWP-06-01 CDWP-06-02 CDWP-06-04CDWP-06-03 CDWP-06-05 CDWP-06-06
CT-06a-01 CT-06a-02 CT-06a-03 CT-06a-04 CT-06a-05 CT-06a-06 CTA-06a-01 CTA-06a-02 CTA-06a-03 CTA-06a-04 CTA-06a-05G
Cooling tower circuit
A
F
D
CA
B
E
B
D
C
E
F
G
Secondary water circuit for Zone 1
Secondary water circuit for Zone 2
Secondary water circuit for Zone
3 and Zone 4
Primary water circuit
Chiller circuit
Cooling water circuit
(S-B)
FROM PODIUM & BASEMENT
TO PODIUM & BASEMENT
HX HX
(S-B)
(S-B)
(S-B)
FROM OFFICE FLOORS (43-77)
TO OFFICE FLOORS (43-77)
(S-B)
CONDENSER CONDENSER CONDENSER CONDENSER CONDENSER CONDENSER
HXHXHX
TO OFFICE FLOORSS (79-98)
FROM OFFICE FLOORS (79-98)
(S-B)
(S-B)
SCHWP-42-01 to 03SCHWP-42-04 to 06
SCHWP-78-01 to 03
PCHWP-78-03PCHWP-78-01 PCHWP-78-02
PCHWP-42-01 PCHWP-42-02 PCHWP-42-03 PCHWP-42-04 PCHWP-42-05 PCHWP-42-06 PCHWP-42-07
SCHWP-06-06 to 09
SCHWP-06-03 to 05
SCHWP-06-01 to 02
SCHWP-06-10 to 12
CTA Towers (without heating coil) CTB Towers (with heating coil)
Our Roles in ICC ProjectOur Roles in ICC ProjectOur Roles in ICC ProjectOur Roles in ICC ProjectOur Roles in ICC ProjectOur Roles in ICC ProjectOur Roles in ICC ProjectOur Roles in ICC Project
� Independent Energy Consultant (Independent Commissioning Agent)
� Developer of HVAC Energy Optimization System (EOS) and Energy Performance Diagnosis System (EPDS)
� Annual electricity consumption of the central
air-conditioning system is about 50,000,000 kWh
Chiller Pump Cooling Tower Fan PAU Fan AHU Fan Total
Number 6 36 11 29 152 234
Rated Power (kW ) 1346 152
Total load (kW ) 8076 4374 1672 513 4600 19235
Percentage 41.99% 22.74% 8.69% 2.67% 23.91%
� Summary of design power load of main HVAC
equipments
Principle of Commissioning Principle of Commissioning
((校核校核校核校核校核校核校核校核//校校校校校校校校校校校校校校校校及及及及及及及及改進改進改進改進改進改進改進改進))
� Commissioning is the process throughout the
whole building lifecycle rather that one-off task.
� Commissioning is a valid means for
improving energy performance of
buildings and HVAC systems
throughout the building life cycle.
Categories of CommissioningCategories of Commissioning
� Initial commissioning: Applied to a production of a new
building and/or an installation of new systems.
� Retro-commissioning: The first time commissioning
implemented in an existing building in which a documented
commissioning was not implemented before.
� Re-commissioning: Implemented after the initial
commissioning or the retro-commissioning when the owner hopes to
verify, improve and document the performance of building systems.
� On-going/continuous commissioning: Conducted
continually for the purposes of maintaining, improving and
optimizing the performance of building systems after the initial
commissioning or the retro-commissioning.
� Commissioning is the process throughout the whole building lifecycle rather that one-off task as conventional “Test and Commissioning”.It is performed regularly throughout the whole building lifecycle from early planning, design, construction and installation to operationfor ensuring that systems are designed, installed, functionally tested and capable of being operated and maintained properly.
LifeLife--CCycle ycle CCommissioningommissioning� The building profession in Northern American and European countries has been promoting the new concept of life-cycle “Commissioning” and role of “Independent Commissioning Agent” over the last few years.
� Commissioning is an effective means for improving energy performance of buildings and HVAC systems throughout the building life cycle.• An average payback period for commissioning of new buildings is 4.8 years in United States.
• Average energy cost saving for periodical commissioning of existing building is 15%.
� Commissioning is the process throughout the whole building lifecycle rather that one-off task as conventional “Test and Commissioning”.It is performed regularly throughout the whole building lifecycle from early planning, design, construction and installation to operationfor ensuring that systems are designed, installed, functionally tested and capable of being operated and maintained properly.
LifeLife--CCycle ycle CCommissioningommissioning� The building profession in Northern American and European countries has been promoting the new concept of life-cycle “Commissioning” and role of “Independent Commissioning Agent” over the last few years.
� Commissioning is an effective means for improving energy performance of buildings and HVAC systems throughout the building life cycle.• An average payback period for commissioning of new buildings is 4.8 years in United States.
• Average energy cost saving for periodical commissioning of existing building is 15%.
ICC project is one of the very first full scale
trial of the new concept of “Commissioning”
and “Independent Commissioning Agent” in
very large and complex building system in
Asia. It is a very attractive contribution to the
IEA Research programme Annex 47.
Commissioning and examples of Commissioning and examples of Commissioning and examples of Commissioning and examples of
efforts at design, installation, T&C efforts at design, installation, T&C efforts at design, installation, T&C efforts at design, installation, T&C
and operation stagesand operation stagesand operation stagesand operation stages
Development of Virtual Building System - Dynamic
simulation platform of the complex HVACR system
Chiller One
TYPE 23
Chiller Four
TYPE 23
Chiller Six
TYPE 23
Chiller Two
TYPE 23
Chiller Three
TYPE 23
Chiller Five
TYPE 23
CTA Three
TYPE 1
CTB One
TYPE 2
CTA Five
TYPE 1
CTA Two
TYPE 1
CTA Four
TYPE 1
CTB Two
TYPE 2
CTA One
TYPE 1
CTB Five
TYPE 2
CTB Four
TYPE 2
CTB Three
TYPE 2
CTA Six
TYPE 1
Cooling tower controller
TYPE 3&54&55
Mixing after chiller condensers
TYPE 4
Mixing after cooling towers
TYPE 5
Data Reader
TYPE 9
Chiller sequence controller
TYPE 50
Mixing & Bypass
TYPE 67
Return pipe
TYPE 31 Supply pipe
TYPE 31
Pump & network
TYPE 12
AHUs
TYPE 63
PID control
TYPE 42
Pump sequence
TYPE 39
HX modeling&mixingTYPE 41
HX sequence
TYPE 39
PID control
TYPE 43
Tao,i
Load & status of AHUs
TYPE 49
Pump & network
TYPE 13
AHUs
TYPE 21
PD optimizerTYPE 7
PID control
TYPE 20
Pump sequence
TYPE 39
PID control
TYPE 43
Tao,i
VPi
PDset
Pump & network
TYPE 14
PID control
TYPE 43
PID control
TYPE 43
Mixing
TYPE 48
Tw,out
HX modeling&mixing TYPE 36
HX sequence
TYPE 39
Pump & network
TYPE 17
AHUs
TYPE 63
PID control
TYPE 42
Pump sequence
TYPE 39
PID control
TYPE 43
Tao,i
Pump & network
TYPE 15
PID control
TYPE 43
PID control
TYPE 43
Mixing & bypassTYPE 19
Tw,o
ut
Load & status of AHUs
TYPE 35
Pump & network
TYPE 18
AHUs
TYPE 63
PID control
TYPE 42
PID control
TYPE 43
Tao,i
HX modeling&mixing TYPE 37
HX sequence
TYPE 39
Pump & network
TYPE 16
PID control
TYPE 43
PID control
TYPE 43
Mixing & bypassTYPE 45
PD optimizerTYPE 6
VPi
PDset
PD optimizerTYPE 8
Pump sequence
TYPE 39
PDset
PD optimizerTYPE 62
PDset
Mixing
TYPE 47
Mixing
TYPE 47
Tw,sup
Mw,i
On/Off
of AHUs
Mw &
PD
mea
s
Npu
Freq
On/Off
of AHUs
Mw,i
Mw &
PD
mea
s
Freq
Npu
Nhx
Tw,sup
Tw,in &Mw
Tw,sup
Mw,set
Mw,measFreq
Mw,i
VPi
Npu
Freq
VPi
Mw,i
Freq
Npu
Mw &
PD
mea
s
Nhx
Mw
Tw,sup&MwMw,set
Mw,measFreqNhx
Load
Nhx
Nhx
Tw,sup
Tw,out
Ma,i&
Ta,in
Ma,i&Ta,inMa,i&Ta,in
On/Off of AHUs
On/Off of AHUsOn/Off of AHUs
Mw & Tw,rtn Mw & Tw,rtn
On/Off of AHUs Ma,i&Ta,in
On/Off
of AHUs
On/Off of AHUs
Load
Tw,sup
Tw,rtn
& M
w
Tw,rtn & Mw
Tw,in
Mw &
Tw,in
Tw,sup & MwMw & Tw,rtn
Nhx
Mw
Mw,&
w,in
Tw,rtn
& M
w
Mw,measFreq
Mw,set
Mw
Nch On/Off On/Off On/Off On/Off On/Off On/Off
Tw,ch,out Tw,ch,out Tw,ch,out Tw,ch,out Tw,ch,out Tw,ch,out
Tsup
Tsu
p
Mw,tot&
Trtn
Nch Tw,cd,out Tw,cd,out Tw,cd,out Tw,cd,out Tw,cd,out Tw,cd,out
Tw,cd,in
Mw,tot&Tw,ct,inTw,cd,outOn/Off,i&Freq,i
Zone 2
Zone 1Zone 3&4
NumberN:
Valve positionVP:
Pressure differentialPD:
FrequencyFreq:
Cooling loadLoad:
Water or air flow rateM:
TemperatureT:
Component type numberTYPE XX:
NumberN:
Valve positionVP:
Pressure differentialPD:
FrequencyFreq:
Cooling loadLoad:
Water or air flow rateM:
TemperatureT:
Component type numberTYPE XX:
Supplysup:Heat exchangerhx:
wb:
ct:
cd:
rtn:
in:
ao:
meas:
w:
Subscript
Wet-bulb
Cooling tower
Condenser
Return
Inlet
Air outlet
Measurement
Water
Set-pointset:
Chillerch:
Dry-bulbdb:
Outletout:
Pumppu:
Totaltot:
Individuali:
Aira:
Supplysup:Heat exchangerhx:
wb:
ct:
cd:
rtn:
in:
ao:
meas:
w:
Subscript
Wet-bulb
Cooling tower
Condenser
Return
Inlet
Air outlet
Measurement
Water
Set-pointset:
Chillerch:
Dry-bulbdb:
Outletout:
Pumppu:
Totaltot:
Individuali:
Aira:
Tw,out & Mw Tw,out & Mw Tw,out & Mw Tw,out & MwTw,out & MwTw,out & MwTw,out & Mw Tw,out & MwTw,out & Mw Tw,out & Mw
Mw,tot&Tw,ct,out
Pump sequence
TYPE 39
NpuMw
Pump sequence
TYPE 39
Npu
Mw
Mixing
TYPE 60
Tw,rtn & Mw,tot
Twb&
Tdb
Tw,out,i
Mixing
TYPE 61
Mw,tot & Tw,rtn
Zone airflow rates
Zone 1Zone 1Zone 1Zone 1
Zone 2Zone 2Zone 2Zone 2Zones 3&4Zones 3&4Zones 3&4Zones 3&4
Development of Virtual Building System - Dynamic
simulation platform of the complex HVACR system
Chiller One
TYPE 23
Chiller Four
TYPE 23
Chiller Six
TYPE 23
Chiller Two
TYPE 23
Chiller Three
TYPE 23
Chiller Five
TYPE 23
CTA Three
TYPE 1
CTB One
TYPE 2
CTA Five
TYPE 1
CTA Two
TYPE 1
CTA Four
TYPE 1
CTB Two
TYPE 2
CTA One
TYPE 1
CTB Five
TYPE 2
CTB Four
TYPE 2
CTB Three
TYPE 2
CTA Six
TYPE 1
Cooling tower controller
TYPE 3&54&55
Mixing after chiller condensers
TYPE 4
Mixing after cooling towers
TYPE 5
Data Reader
TYPE 9
Chiller sequence controller
TYPE 50
Mixing & Bypass
TYPE 67
Return pipe
TYPE 31 Supply pipe
TYPE 31
Pump & network
TYPE 12
AHUs
TYPE 63
PID control
TYPE 42
Pump sequence
TYPE 39
HX modeling&mixingTYPE 41
HX sequence
TYPE 39
PID control
TYPE 43
Tao,i
Load & status of AHUs
TYPE 49
Pump & network
TYPE 13
AHUs
TYPE 21
PD optimizerTYPE 7
PID control
TYPE 20
Pump sequence
TYPE 39
PID control
TYPE 43
Tao,i
VPi
PDset
Pump & network
TYPE 14
PID control
TYPE 43
PID control
TYPE 43
Mixing
TYPE 48
Tw,out
HX modeling&mixing TYPE 36
HX sequence
TYPE 39
Pump & network
TYPE 17
AHUs
TYPE 63
PID control
TYPE 42
Pump sequence
TYPE 39
PID control
TYPE 43
Tao,i
Pump & network
TYPE 15
PID control
TYPE 43
PID control
TYPE 43
Mixing & bypassTYPE 19
Tw,o
ut
Load & status of AHUs
TYPE 35
Pump & network
TYPE 18
AHUs
TYPE 63
PID control
TYPE 42
PID control
TYPE 43
Tao,i
HX modeling&mixing TYPE 37
HX sequence
TYPE 39
Pump & network
TYPE 16
PID control
TYPE 43
PID control
TYPE 43
Mixing & bypassTYPE 45
PD optimizerTYPE 6
VPi
PDset
PD optimizerTYPE 8
Pump sequence
TYPE 39
PDset
PD optimizerTYPE 62
PDset
Mixing
TYPE 47
Mixing
TYPE 47
Tw,sup
Mw,i
On/Off
of AHUs
Mw &
PD
mea
s
Npu
Freq
On/Off
of AHUs
Mw,i
Mw &
PD
mea
s
Freq
Npu
Nhx
Tw,sup
Tw,in &Mw
Tw,sup
Mw,set
Mw,measFreq
Mw,i
VPi
Npu
Freq
VPi
Mw,i
Freq
Npu
Mw &
PD
mea
s
Nhx
Mw
Tw,sup&MwMw,set
Mw,measFreqNhx
Load
Nhx
Nhx
Tw,sup
Tw,out
Ma,i&
Ta,in
Ma,i&Ta,inMa,i&Ta,in
On/Off of AHUs
On/Off of AHUsOn/Off of AHUs
Mw & Tw,rtn Mw & Tw,rtn
On/Off of AHUs Ma,i&Ta,in
On/Off
of AHUs
On/Off of AHUs
Load
Tw,sup
Tw,rtn
& M
w
Tw,rtn & Mw
Tw,in
Mw &
Tw,in
Tw,sup & MwMw & Tw,rtn
Nhx
Mw
Mw,&
w,in
Tw,rtn
& M
w
Mw,measFreq
Mw,set
Mw
Nch On/Off On/Off On/Off On/Off On/Off On/Off
Tw,ch,out Tw,ch,out Tw,ch,out Tw,ch,out Tw,ch,out Tw,ch,out
Tsup
Tsu
p
Mw,tot&
Trtn
Nch Tw,cd,out Tw,cd,out Tw,cd,out Tw,cd,out Tw,cd,out Tw,cd,out
Tw,cd,in
Mw,tot&Tw,ct,inTw,cd,outOn/Off,i&Freq,i
Zone 2
Zone 1Zone 3&4
NumberN:
Valve positionVP:
Pressure differentialPD:
FrequencyFreq:
Cooling loadLoad:
Water or air flow rateM:
TemperatureT:
Component type numberTYPE XX:
NumberN:
Valve positionVP:
Pressure differentialPD:
FrequencyFreq:
Cooling loadLoad:
Water or air flow rateM:
TemperatureT:
Component type numberTYPE XX:
Supplysup:Heat exchangerhx:
wb:
ct:
cd:
rtn:
in:
ao:
meas:
w:
Subscript
Wet-bulb
Cooling tower
Condenser
Return
Inlet
Air outlet
Measurement
Water
Set-pointset:
Chillerch:
Dry-bulbdb:
Outletout:
Pumppu:
Totaltot:
Individuali:
Aira:
Supplysup:Heat exchangerhx:
wb:
ct:
cd:
rtn:
in:
ao:
meas:
w:
Subscript
Wet-bulb
Cooling tower
Condenser
Return
Inlet
Air outlet
Measurement
Water
Set-pointset:
Chillerch:
Dry-bulbdb:
Outletout:
Pumppu:
Totaltot:
Individuali:
Aira:
Tw,out & Mw Tw,out & Mw Tw,out & Mw Tw,out & MwTw,out & MwTw,out & MwTw,out & Mw Tw,out & MwTw,out & Mw Tw,out & Mw
Mw,tot&Tw,ct,out
Pump sequence
TYPE 39
NpuMw
Pump sequence
TYPE 39
Npu
Mw
Mixing
TYPE 60
Tw,rtn & Mw,tot
Twb&
Tdb
Tw,out,i
Mixing
TYPE 61
Mw,tot & Tw,rtn
Zone airflow rates
Zone 1Zone 1Zone 1Zone 1
Zone 2Zone 2Zone 2Zone 2Zones 3&4Zones 3&4Zones 3&4Zones 3&4
Virtual
Building
System
Simulated
(updated throughout
the entire process)
• Verification the system configuration and component selection including the chiller system, water system (primary/secondary system), heat rejection system (cooling towers), fresh air system etc.
• Verification of the metering system for proper local control, and the original proposed control logics at the design stage.
• Proposal of additional metering system for implementing supervisory control strategies and diagnosis strategies and related facilities for implementing these strategies ( This is a typical energy-saving implementation from the earlier design and installation phase)
Design CommissioningDesign CommissioningThe design commissioning mainly concerns the
future operation and control performance of HVAC
systems, and includes:
HX-42 HX-42 HX-42 HX-42 HX-42 HX-42 HX-42
(S-B)
FROM OFFICE FLOORS (43-77)
TO OFFICE FLOORS (43-77)
(S-B)
HX-78HX-78HX-78
TO OFFICE FLOORSS (79-98)
FROM OFFICE FLOORS (79-98)
(S-B)
(S-B)
SCHWP-42-01 to 03SCHWP-42-04 to 06
SCHWP-78-01 to 03
SCHWP-06-06 to 09
To Z
on
e 3&
4
Fro
m Z
one 3
&4
Flow meter
Bypass valve
EVAPORATOR EVAPORATOR EVAPORATOR EVAPORATOREVAPORATOREVAPORAROR
WCC-06a-01
(2040 Ton)
PCHWP-06-01
FROM OFFICCE FLOORS(7-41)
TO OFFICE FLOORS(7-41)
HX-42
PCHWP-06-02 PCHWP-06-03 PCHWP-06-04 PCHWP-06-05 PCHWP-06-06
WCC-06a-02
(2040 Ton)
WCC-06a-04
(2040 Ton)WCC-06a-03
(2040 Ton)
WCC-06a-05
(2040 Ton)WCC-06a-06
(2040 Ton)
CDWP-06-01 CDWP-06-02 CDWP-06-04CDWP-06-03 CDWP-06-05 CDWP-06-06
A
F
D
CA
B
E
B
D
C
E
F
Secondary water circuit for Zone 1
Secondary water circuit for Zone 2
Secondary water circuit for Zone
3 and Zone 4
Primary water circuit
Chiller circuit
Cooling water circuit
(S-B)
FROM PODIUM & BASEMENT
TO PODIUM & BASEMENT
HX-06
(S-B)
(S-B)
(S-B)
FROM OFFICE FLOORS (43-77)
TO OFFICE FLOORS (43-77)
(S-B)
CONDENSER CONDENSER CONDENSER CONDENSER CONDENSER CONDENSER
HX-78HX-78HX-78
TO OFFICE FLOORSS (79-98)
FROM OFFICE FLOORS (79-98)
(S-B)
(S-B)
SCHWP-42-01 to 03SCHWP-42-04 to 06
SCHWP-78-01 to 03
PCHWP-78-03PCHWP-78-01 PCHWP-78-02
PCHWP-42-01 PCHWP-42-02 PCHWP-42-03 PCHWP-42-04 PCHWP-42-05 PCHWP-42-06 PCHWP-42-07
SCHWP-06-06 to 09
SCHWP-06-03 to 05
SCHWP-06-01 to 02
SCHWP-06-10 to 12
To cooling towersFrom cooling towers
HX-42 HX-42 HX-42 HX-42 HX-42 HX-42
HX-06
Original SystemOriginal SystemOriginal SystemOriginal System Revised Revised Revised Revised SystemSystemSystemSystem(operation mode)(operation mode)(operation mode)(operation mode)
System Design VerificationSystem Design Verification --Secondary water loop systems Secondary water loop systems of 3rd and 4of 3rd and 4thth zoneszones
Primary pumps are omitted
Comparison between Two systemsComparison between Two systems
0
200
400
600
800
1000
1200
1400
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
Time (h )
Pump power (
kW)
Original design
Alternative design
Annual Pump Energy Saving is
1M kWh
Typical sunny-
summer day
• A very special cooling tower with large heat rejection capacity and a very large dimension (4*10*9)
• High pressure drop through fill packing and silencer
• Energy consumption is about 3.6 million a year with intended two-stage control
• Energy consumption is about 2.6 million a year with intended VFD control from PolyU
• However, energy consumption will increase greatly to about 5.0 million when single-stage is used
From chiller
To chiller
Pressure drop
300 Pa 50 Pa100 Pa
Silencer
Fill packing
System Design VerificationSystem Design Verification--Cooling tower systemCooling tower system
Annual saving potential of using variable speed
cooling towers is 2.4M compared with that
using constant speed towers. It is 1.4M
compared with that using two speed towers.
Example of CO2 Sensor
Installation
CO2CO2 CO2CO2
CO2CO2CO2CO2
CO2CO2
CO2CO2CO2CO2
CO2CO2
CO2CO2
CO2CO2
CO2CO2
CO2CO2CO2CO2
CO2CO2
CO2CO2CO2CO2
CO2CO2
CO2CO2
AHU
AHU
KaishingIC
BB
Morgan
Stanley
Empty
Empty
EmptyCO2CO2
CO2CO2
Flow stations
200
250
300
350
400
450
500
550
600
650
700
9:00 10:00 11:00 12:00 13:00 14:00 15:00 16:00 17:00 18:00 19:00
Sample time (h)
CO2 concentration (ppm)
Fresh air (Measured) Return air (Measured)
Supply air (Measured) Supply air (Calculated)
After calibration
200
250
300
350
400
450
500
550
600
650
700
9:00 10:00 11:00 12:00 13:00 14:00 15:00 16:00 17:00 18:00 19:00
Simple time (h)
CO2 concentration (ppm)
Fresh air (Measured) Return air (Measured)
Supply air (Measured) Supply air (Calculated)
Measurement accuracy of CO2 sensors directly affects
indoor air quality and energy performance of air side
system, which is therefore essential for implementing
optimal ventilation control strategy.
Before calibration
� CO2 sensor calibration and commissioning
Example of air flow
station Installation
∆P
PAvAQ ∆⋅=⋅= 2
Cooling tower site operation issueCooling tower site operation issue• We suggest all the cooling tower fans are equipped with
VFD for significant energy savings, and the variable frequency range is from 50 Hz to 25 Hz at least.
• At the test stage, the manufacture stated the minimum frequency is 37 Hz for cooling requirement of the inside motor.
• The manufacture finally confirmed the minimum frequency is 20 Hz ensuring the normal operation of the fan.
This low frequency increases the This low frequency increases the This low frequency increases the This low frequency increases the
energy saving potential greatly energy saving potential greatly energy saving potential greatly energy saving potential greatly
at partial load conditions !at partial load conditions !at partial load conditions !at partial load conditions !
Cooling tower site operation issueCooling tower site operation issue• We suggest all the cooling tower fans are equipped with
VFD for significant energy savings, and the variable frequency range is from 50 Hz to 25 Hz at least.
• At the test stage, the manufacture stated the minimum frequency is 37 Hz for cooling requirement of the inside motor.
• The manufacture finally confirmed the minimum frequency is 20 Hz ensuring the normal operation of the fan.
This low frequency increases the This low frequency increases the This low frequency increases the This low frequency increases the
energy saving potential greatly energy saving potential greatly energy saving potential greatly energy saving potential greatly
at partial load conditions !at partial load conditions !at partial load conditions !at partial load conditions !
The savings is about 607,000 kWh , 2.86% of
annual energy consumption of chillers and
cooling towers due to the lower frequency limit.
Low Delta-T Central Plant Syndrome
� The inability to sufficiently
load chillers;
� Excess water flow demand;
� An increase in pump energy;
� Either an increase in chiller
energy or a failure to meet
cooling load; etc.
� Nearly all large primary-secondary chilled water
systems suffer from low chilled water temperature
difference, known as low delta-T central plant
syndrome, resulting in inefficient operation.
� When the low delta-T syndrome exists, a series of
operation problems will be resulted
-500
-400
-300
-200
-100
0
100
200
300
400
500
0 12 24 36 48 60 72 84 96 108 120 132 144 156 168
Sample time (hour)
Water flow rate (L/s)
0
1
2
3
4
5
6
7
8
Chiller number and Temp. difference
Chiller operating number
Water flow
Temp. difference after decouple
Low Delta-T Central Plant Syndrome
� The inability to sufficiently
load chillers;
� Excess water flow demand;
� An increase in pump energy;
� Either an increase in chiller
energy or a failure to meet
cooling load; etc.
� Nearly all large primary-secondary chilled water
systems suffer from low chilled water temperature
difference, known as low delta-T central plant
syndrome, resulting in inefficient operation.
� When the low delta-T syndrome exists, a series of
operation problems will be resulted
-500
-400
-300
-200
-100
0
100
200
300
400
500
0 12 24 36 48 60 72 84 96 108 120 132 144 156 168
Sample time (hour)
Water flow rate (L/s)
0
1
2
3
4
5
6
7
8
Chiller number and Temp. difference
Chiller operating number
Water flow
Temp. difference after decouple
Some causes can be avoided, but some
of them cannot be avoided in some
applications.
Each phase in the life cycle of air-conditioning
systems, including design, equipment selection,
commissioning, operation and maintenance,
may result in low delta-T problems.
� Potential solutions
� The use of variable primary-only systems;
� The use of pressure-independent modulating
control valves;
� The use of bypass check valves;
� Advanced control and operation strategies.
System Improvement by using a Check ValveSystem Improvement by using a Check Valve
� Experimental validation prior to a check valve is really installed
� by using a ‘conceptual’ check valve in the chiller decouple ---- through fully closing down one of the isolation valves in the chiller decouple when the deficit flow was observed.
CHILLER 06CHILLER 06
FM
AHUAHU
Secondary water
circuit for Zone 1
Secondary water
circuit for Zone 2
Secondary water
circuit for Zone 3&4
Primary
pumps 01-06
Secondary
Pumps 01-02
CHILLER 05CHILLER 05
CHILLER 04CHILLER 04
CHILLER 03CHILLER 03
CHILLER 02CHILLER 02
CHILLER 01CHILLER 01
AHUAHU
AHUAHU
AHUAHU
AHUAHU
AHUAHU
Secondary
pumps 03-05Secondary
pumps 06-08
AHUAHU
AHUAHU
AHUAHU
Check valve
� Summary of experimental results
-250
-200
-150
-100
-50
0
50
10:09:59
10:24:58
10:42:56
10:58:57
11:10:59
11:23:01
11:39:01
12:03:03
12:21:03
12:35:00
13:00:01
13:14:04
13:29:01
13:43:58
13:56:59
14:13:58
14:38:58
14:52:04
15:02:58
15:16:57
15:33:04
15:47:59
16:06:59
16:23:01
Time
Deficit flow (L/S)
Closing the valve in
the decouple
Reopen the valve
in the decouple
5.5 °C set-point 5.0 °C set-point
4000
4500
5000
5500
6000
6500
7000
10:17:58
10:36:58
10:51:59
11:06:59
11:19:04
11:32:56
11:54:58
12:14:56
12:29:58
12:48:56
13:07:58
13:24:59
13:37:59
13:50:59
14:08:59
14:34:00
14:44:56
14:58:58
15:10:56
15:29:01
15:39:00
15:57:59
16:15:58
Time
Cooling load of chiller(kW)
Closing the valve
in the decouple
Reopen the valve in
the decouple
Reset supply water
temp. set point from
5.5°C to 5 °C
12
12.5
13
13.5
14
14.5
15
15.5
16
10:00:58
10:17:58
10:36:58
10:51:59
11:06:59
11:19:04
11:32:56
11:54:58
12:14:56
12:29:58
12:48:56
13:07:58
13:24:59
13:37:59
13:50:59
14:08:59
14:34:00
14:44:56
14:58:58
15:10:56
15:29:01
15:39:00
15:57:59
16:15:58
Time
Outlet air temp. of AHU 1 in L15 (°C)
Closing the valve
in the decouple
Reopen the valve in
the decouple
Reset supply water
temp. set point from
5.5°C to 5 °C
0
200
400
600
800
1000
1200
1400
1600
1800
11:19:56
11:30:02
11:42:58
11:52:59
12:05:56
12:16:58
12:32:03
12:46:56
12:57:00
13:07:04
13:17:59
13:31:59
13:48:03
13:56:01
14:09:57
14:28:03
14:39:56
14:48:00
14:57:59
Time
Total power (kW)
Using 'conceptual' check valvewith similar weather condition
by without using the check
valve
Test procedure Cooling energy of chillers
Supply air temperature Energy consumptions
Annual energy saving potential by using the check
valve in ICC is about 325,800 kWh when compared
to that without using the check valve.
Simplified
Models
Optimization
Strategies
Performance
Models
Diagnosis
Strategies
Performance
Prediction
Performance
Prediction
IBmanager
System Control Optimizer
Diagnostic Tool
Communication
Interfa
ces
Virtual Plants
Simulated
Online performance testing of control Online performance testing of control optimizers and diagnostic tools on the optimizers and diagnostic tools on the
simulated virtual systemsimulated virtual systemControl optimizers and diagnostic tools should be tested on the virtual
systems prior to site implementation
Saving Energy through
Control Optimization
Optimization for HVAC&R systems
Optimization allows the of HVAC&R systems
provide expected quality of services (comfort and
health environment) with reduced energy
consumption by means of :
• Optimizing design configuration;
• Optimizing the selection and sizing;
• Optimal operation and control.
Optimal control strategies for central Optimal control strategies for central airair--conditioning systemsconditioning systems
� Chiller sequence, optimal start
Optimal chiller sequence - based on a more accurate cooling load
prediction using data fusion method, and considering demand limiting
Adaptive online strategy for optimal start - based on simplified sub-
system dynamic models
� Ventilation strategy for multi-zone air-conditioning
system
Optimal ventilation control strategy - based on ventilation needs of
individual zones and the energy benefits of fresh air intake
� Peak demand limiting and global electricity cost
management
Optimal control strategies for central Optimal control strategies for central airair--conditioning systems (contconditioning systems (cont’’d)d)
� Chilled water system optimization
Optimal pressure differential set point reset strategy
Optimal pump sequence logic
Optimal heat exchanger sequence logic
Optimal control strategy for pumps in the cold water side of heat
exchangers
Optimal chilled water supply temperature set-point reset strategy
� Cooling water system optimization
Optimal condenser inlet water temperature set point reset strategy
Optimal cooling tower sequence
Optimal control of condenser Optimal control of condenser
cooling water systemscooling water systems
Optimal control of condenser cooling water systemsOptimal control of condenser cooling water systems (cont(cont’’d) d)
� Formulation of the optimal control strategy
• Objective function
++== ∑∑ ∑
== =
CTBch CTA
cdwcdw
N
j
iCTB
N
k
N
i
iCTAkchT
totT
WWWWJ1
,
1 1
,,minminsup,,sup,,
• The overall structure of the optimal control strategyOnline measurements
and control signals
Measurement filter
Simplified chiller
model
Simplified CTA and
CTB tower models
Define the search ranges
for Tw,cd,sup and Nct
Supervisory control strategy
Optimal control settings & cost
(Tw,cd,sup, NCTA , NCTB , Freq , Pch+Pct ) Optimization process
Cost estimation & optimization algorithm
FreqNCTA
Chiller plant control system
(BAS)
Interface
Performance prediction
Twb, Qev, Nch Qev, Nch, Tw,ev,in
Tw,cd,sup
Tw,cd,out
Nch &Twb
Tw,cd,sup& Nct
PchTw,cd,sup, NCTA, NCTB, Ma,, Pct , Freq
NCTB Tw,cd,sup
It consists of :
Performance predictor Performance predictor Performance predictor Performance predictor
Cost estimator Cost estimator Cost estimator Cost estimator
Optimization toolOptimization toolOptimization toolOptimization tool
Supervisory strategySupervisory strategySupervisory strategySupervisory strategy
It is designed using a model-based method
Optimal control of condenser cooling water systemsOptimal control of condenser cooling water systems (cont(cont’’d) d)
• Optimization tool ---HQS (hybrid quick search) method
++=
desev
ev
wb
on
cdwQ
QhThhT
,
210
,
sup,,
TTTTT on
cdwcdw
on
cdw ∆+≤≤∆− .
sup,,sup,,
,
sup,,
Search range
+Δx
-Δx
Low limit Search center (near optimal)
Upper limit
Time
Control setting
• Parameters to be optimized
� The condenser water supply temperature set-point
� The number of CTA towers operating
� The number of CTB towers operating
• Operating constraints
� basic energy and mass balances (i.e., flow, heat, etc.)
� mechanical limitations (i.e., fan speed, temperature, etc.)
• Evaluation of control accuracy and computation performance
Optimal control of condenser cooling water systemsOptimal control of condenser cooling water systems (cont(cont’’d) d)
Seasons Items
Spring Mild-summer Sunny-summer
Typical working conditions
Qload (kW) 25520.11 31213.61 37547.74
Nch 4 5 6
Tw,ev,in (°C) 9.92 9.82 9.83
Tw,ev,out (°C) 5.50 5.50 5.50
Tdb (°C) 22.55 27.76 33.66
Twb (°C) 15.86 20.11 24.99
Mw,cd (L/s) 410.10 410.10 410.10
Items Tools
HQS GA HQS GA HQS GA
Optimization results
Wch (kW) 3628.07 3644.90 5004.21 4994.37 6794.24 6799.59
Wct (kW) 285.74 268.91 386.11 396.08 538.74 533.42
Wch+Wct (kW) 3913.81 3913.81 5390.32 5390.45 7332.98 7333.01
Optimal Tw,cd,sup (°C) 21.85 21.88 26.65 26.64 31.80 31.80
NCTA 6 6 6 6 6 6
NCTB 5 5 5 5 5 5
Freq (Hz) 25.99 25.35 29.33 29.62 33.39 33.26 Computational cost(s) 0.152 3.610 0.144 3.512 0.134 3.589
The computational cost saving is 96.0%
� Performance tests and evaluation
� Comparison between the HQS and GA-based strategies
20.00
23.00
26.00
29.00
32.00
35.00
38.00
0 2 4 6 8 10 12 14 16 18 20 22 24
Time (h )
Temperature (°C)
Dry-bulb Temp.
Wet-bulb Temp.
Optimal Temp. set-point
Near optimal Temp. set-point
Upper limit of set-point
Low limit of set-point
14.00
17.00
20.00
23.00
26.00
29.00
32.00
0 2 4 6 8 10 12 14 16 18 20 22 24
Time (h )
Temperature (
°C)
Dry-bulb Temp.
Wet-bulb Temp.
Optimal Temp. set-point
Near optimal Temp. set-point
Upper limit of set-point
Low limit of set-point
Optimal temperature set-point
Near-optimal temperature set-point
• Evaluation of the Energy Performance
Optimal control of condenser cooling water systemsOptimal control of condenser cooling water systems (cont(cont’’d) d)
� Comparison of condenser water supply temperature set-
points using HQS-based strategy and near optimal strategy
Spring caseSpring caseSpring caseSpring case SunnySunnySunnySunny----summer casesummer casesummer casesummer case
Optimal control of condenser cooling water systemsOptimal control of condenser cooling water systems (cont(cont’’d) d)
� Comparison of the hourly-based power consumptions using
different control methods
-30
-20
-10
0
10
20
30
40
0 2 4 6 8 10 12 14 16 18 20 22 24
Time (h )
Power difference ( k
W)
Optimal strategy
Near optimal strategy
-30
0
30
60
90
120
150
180
210
0 2 4 6 8 10 12 14 16 18 20 22 24
Time (h )Power difference ( k
W)
Optimal strategy
Near optimal strategy
HQS-based strategy
Near optimal strategy
Fixed approach
Spring caseSpring caseSpring caseSpring case SunnySunnySunnySunny----summer casesummer casesummer casesummer case
Fixed
approach
Optimal control of condenser cooling water systemsOptimal control of condenser cooling water systems (cont(cont’’d) d)
� Comparison of daily and annual power consumptions of the
condenser cooling water system using different control methods
Fixed approach Near optimal strategy HQS-based strategy Operation
Strategies Wct+Wch
(kWh)
Wct+Wch
(kWh)
Saving
(kWh)
Saving
(%) Wct+Wch
(kWh)
Saving
(kWh)
Saving
(%)
Spring 51,738 51,623 114.53 0.221 51,404 334.30 0.646
Mild-summer 71,289 70,668 621.49 0.872 70,560 729.36 1.023
Sunny-
summer 91,653 90,878 775.44 0.846 90,356 1,297.50 1.416
• Daily power consumptions
• Annual power consumptions
Operation
strategies
Wch
(kWh)
Wct
(kWh)
Wcd,pu
(kWh) Wtot
(kWh) Saving (kWh)
Saving (%)
Fixed approach 18,464,812 1,882,583 4,210,690 24,558,085 --- ---
Near optimal 18,715,458 1,501,701 4,210,690 24,427,849 130,236 0.530
HQS-based 18,715,134 1,448,765 4,210,690 24,374,589 183,496 0.747
Operating Condition Power Consumption
Cooling
Water
Temp Set-
point
Cooling
Tower
Number
Cooling
Tower
Freq
Chiller
Power
Cooling
Tower
Power
Total
Power Difference
Operation modes
°C - Hz kW kW kW kW %
Reference 22.7 3 26.51 856.2 59.1 915.35 -- --
First-level warning 21.3 3 30.74 836.2 93.0 929.2 14.0 1.5
Second-level warming 20.1 3 35.52 819.9 145.9 965.8 50.6 5.5
Using heat pumps 22.7 3CT+1HP 26.51 856.2 59.1 1215.2 300 32.8
Plume Control and Energy Benefits
At first-level warning, increase airflow rate
by 20% when plume potential is marginal
At second-level warning, increase airflow
by 40% when plume potential is high
Start heating using heat pumps when
visual plume is observed
Decision
maker
Platform for predicting
plume occurring possibility
Normal operation when there is
no predicted plume occurs
Additional energy consumption for
plume control could be reduced from
32.8% to 5.5% or 1.5% at low Load
Chiller Plant Sequencing Control
of Enhanced Robustness
Using Data Fusion Technique
Types of chiller sequencing control
� Return chilled water temperature based sequencing
control
� Bypass flow based sequencing control
� Direct power based sequencing control
� Total cooling load based sequencing control
Background (1)
Chiller sequencing control
� Aims to determine how many and which chillers are to be
put into operation according to building cooling load
� Plays a significant role for building energy efficiency
Total cooling load based chiller sequencing control
� Building cooling load measurement
�Maximum cooling capacity
� Optimal number of chillers to be put into operation
Nc = φ(Qcl, Qmax)
Background (2)
Problems
� Building cooling load cannot be measured accurately
� Chiller maximum cooling capacity vary with the
operating conditions
Fused Cooling Load Measurement
Cooling load measurement
� Direct measurement of building cooling load
Qdm = cpwρwMw(Tw,rtn-Tw,sup)
where cpw is the water specific thermal capacity; ρw is the
water density; Mw is water flow rate; Tw,rtn,Tw,sup are
chilled water return/supply temp.
� Indirect measurement of building cooling load
Qim = f(Pcom,Tcd,Tev)
where f is the chiller inverse model; Pcom is chiller power
consumption; Tcd,Tev are chiller condensing/evaporating
temperature
Robust building cooling load measurement technique
� Data fusion to merge “Direct measurement” and
“Indirect measurement” improving the accuracy and
reliability of building cooling load measurement
Chiller
Model 1Chiller
Model n
Central Chilling Plant
Chiller
Model 1
Chiller
Model nDirect
measurement
Data Fusion
Engine
Pcom,1 Tev,1,Tcd,1
+
Pcom,n,Tev,n,Tcd,n
Trtn Mw
Tsup
Qdm
Qim,1Qim,n
Qf
γf
…
Advanced soft measurement system
Robust Chiller Sequencing Control Building Cooling Load
Measurement Technique
Central chilling
plant
Indirect
Measurement
Data Fusion
EngineParameters
setting
Periodical
analysis
Alarming
subsystem
Chiller sequencing
control
Database
Building Automation
System
Direct
measurement
Robust Cooling Load
Measurement
From cooling source
HX
HX
Temperature controller
Differential pressure controller
Temperature
set-pointPressure
differential set-point
To coolingsource
Secondary side of HX Primary side of HX
Temperature controller
Temperature
set-point
MM
ΔP
TT
TT
To terminal
units
From terminal units
Modulating
valves
MM
HX
HX
TT TM
Temperature controller
Water flowcontroller
Temperature
set-point
Water flow
set-point
To terminal
units
From terminal units
Secondary side of HX Primary side of HX
TM
From cooling source
To coolingsource
� Original implemented strategy --- differential pressure controller by resorting to the modulating valve
� Proposed strategy --- cascade controller without using any modulating valve
Optimal Control of Variable Speed Pumps
� Speed control of pumps distributing water to
heat exchangers
� Site practically test showed that the proposed strategy can provide stable and reliable control. Compared to original implemented strategy, about 22.0% savings for pumps before heat exchangers in Zone 1 was achieved.
� Due to the low load of Zone 1 in ICC at current stage, a simulation test of annual energy savings by using PolyU strategy is performed.
Energy consumption (kWh)
Pumps Number
(standby) Original
strategy
(kWh)
Alternative
Strategy
(kWh)
Saving
(kWh)
Primary pumps in Zone 1 1(1) 528,008 456,132 71,876
Primary pumps for Zones 3&4 3(1) 921,235 795,830 125,405
Primary pumps in Zone 4 2(1) 401,008 346,420 54,588
Total saving of the primary pumps 251,869
Energy saving of primary pumps before
heat exchanges due to the use of
PolyU strategy is about 250000 kWh.
� Performance test and evaluation
Static pressure
Outdoor air
controller
Adaptive DCV
strategy
Model-based
outdoor air flow rate
Control strategy
P
Static pressure
controller
Static pressure
set point
Set point
The 1st floor
The 7th floor
………….
Optimal Outdoor air Ventilation Control
COP
HHMMC
COP
QWW
k
rtn
k
out
k
setoutk
setout
k
voutdoor
fant
)(,
,cos
−⋅+⋅=+=
Parameter identification of the fan model
Parameter estimators
Real process of the multi-zone
air conditioning system
Cost function
estimator
Iterative
algorithm
Model-based
predictor
Supervisor Constrains
Optimal set point Range of set point
Set point trailsLeast Square Algorithm
Outdoor Air Optimal Scheme
Energy-based outdoor air flow rate set-point
resetting scheme
� Site Implementation and Validation of Optimal Ventilation Strategy for Fresh Air Control
� CO2-based occupancy detection
� Site counting the number of occupancy in the typical floor
� Comparison between counted and predicted occupancies
0
10
20
30
40
50
60
70
80
90
100
8:30 9:30 10:30 11:30 12:30 13:30 14:30 15:30 16:30 17:30 18:30
Time (hour)
Num
ber of occupancy
Counted
Predicted
Demand-controlled Ventilation control
� Practically test and validation of the ventilation control strategy
Tests aimed at validating the actual operational performance of the
ventilation control strategy and also for verifying whether the control
settings provided by PolyU strategy can be properly sent to the ATC
system and further be used in practical control.
+45.8-+58.9-Total energy saving (%)
2050.13780.22203.55366.7Total energy consumption (kWh)
1725.62985.61915.24754.4Fresh air cooling energy
consumption (kWh)
324.5794.60288.3612.29Primary fan energy consumption
(kWh)
Summer case
(PolyU strategy applied to all
floors in Zone 2)
+59.2-+52.9-Primary fan energy saving (%)
324.5794.60288.3612.29Primary fan energy consumption
(kWh)Estimation case
(PolyU strategy applied to all
floors in Zone 2)
2.814.963.047.90Energy saved due to fresh air
cooling (kWh)
+4.11-+0.70-Primary fan energy saving (%)
761.92794.60607.99612.29Primary fan energy consumption
(kWh)Site test case
(PolyU strategy only applied to
typical floor)
(Nov., 2009)
PolyUFixed flowPolyUFixed flow
AHU2AHU1Control strategyStudy cases
About 662,000 kWh energy savings can be
achieved by using PolyU ventilation control
strategy for all floors per year in Zone 2!
Site Implementation of The
Control Strategies
Implementation Strategy of Optimal Control and Diagnosis
Tools in ICC
LAN
VAV BoxAHU PAU
Supply air control
optimizer
Fresh air control
optimizer
Fresh air
terminal
ATC
Decision Supervisor
Building
Management
System
DiagnosisOptimizer
Overall KVA, etc. Control
Parameters
Chiller Plant Control Optimizer
and Diagnosis
Control Setting
from PolyU
Control Setting
from ATC
Manual
Control
Control Setting
from PolyU
Control Setting
from ATC
Manual
Control
BA
CnetS
DK
IBmanager
Intelligent building management system
-- based on IBmanager� IBmanager is an open and integrated management platform. It
employs standard middleware and web-service technologies to
support the integration and interoperation among distributed BASs.
Summary of Energy Benefits• 1,000,000 kWh energy consumption is saved due to the
modification on the secondary water loops of Zone 3 & 4;
• 2,360,000 kWh , (about 5.1% of annual energy consumption of chillers and cooling towers) of the cooling system can be saving due to the change from single speed to variable speed using VFD.
• 607,000 kWh , (about 2.8% of annual energy consumption of chillers and cooling towers) of the cooling system will be wasted when the lowest frequency is limited at 37 Hz.
• 3, 500,000 kWh (about 7%) of the total energy consumption of HVAC system) can be saved using PoyUcontrol strategies based on the original design;
Summary of Energy Benefits• 1,000,000 kWh energy consumption is saved due to the
modification on the secondary water loops of Zone 3 & 4;
• 2,360,000 kWh , (about 5.1% of annual energy consumption of chillers and cooling towers) of the cooling system can be saving due to the change from single speed to variable speed using VFD.
• 607,000 kWh , (about 2.8% of annual energy consumption of chillers and cooling towers) of the cooling system will be wasted when the lowest frequency is limited at 37 Hz.
• 3, 500,000 kWh (about 7%) of the total energy consumption of HVAC system) can be saved using PoyUcontrol strategies based on the original design;
Saving by Control OptimizationSaving by Control OptimizationSaving by Control OptimizationSaving by Control Optimization – compared with the
case when the HVAC system operates correctly
according to the original design intend.
Saving by CommissioningSaving by CommissioningSaving by CommissioningSaving by Commissioning (Improving the system (Improving the system (Improving the system (Improving the system configuration and selectionconfiguration and selectionconfiguration and selectionconfiguration and selection – compared with the
original design.
Summary of Energy Benefits• 1,000,000 kWh energy consumption is saved due to the
modification on the secondary water loops of Zone 3 & 4;
• 2,360,000 kWh , (about 5.1% of annual energy consumption of chillers and cooling towers) of the cooling system can be saving due to the change from single speed to variable speed using VFD.
• 607,000 kWh , (about 2.8% of annual energy consumption of chillers and cooling towers) of the cooling system will be wasted when the lowest frequency is limited at 37 Hz.
• 3, 500,000 kWh (about 7%) of the total energy consumption of HVAC system) can be saved using PoyUcontrol strategies based on the original design;
Saving by Control OptimizationSaving by Control OptimizationSaving by Control OptimizationSaving by Control Optimization – compared with the
case when the HVAC system operates correctly
according to the original design intend.
Saving by CommissioningSaving by CommissioningSaving by CommissioningSaving by Commissioning (Improving the system (Improving the system (Improving the system (Improving the system configuration and selectionconfiguration and selectionconfiguration and selectionconfiguration and selection – compared with the
original design.
The annual total energy
saving is about 7.0M kWh !
Summary of Experience in ICC• Significant energy saving can be achieved by
allowing the system as good as the design intention by identifying and correcting the errors at different stages;
• Significant energy saving can be achieved by making the system better than the design intention by enhancing and optimizing the systems at different stages;
• The involvement of a professional energy consultant (commissioning agent) does not introduce troubles to the building construction project, but instead it facilitates different parties involved to support each other to do their jobs smoothly and correctly.