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ENGINEERING ADVANTAGE
ENERGY INSIGHTS
OPTIMISING HYDRONIC SYSTEMS
FOR ENERGY SAVINGS
Tom Pak
May 9th 2012
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ENGINEERING ADVANTAGE
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World's energy consumption
2
40% of the world's energy
consumption is used in buildings*
50% of this is in HVAC systems alone*
(*) Sources: European Commission EPBD (point 6, pp1) &
US Department of Energys Buildings Energy Data Book
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Energy savings on HVAC in buildings
3
HVAC installation Use of new technologies System approach of
hydronic design
Shorter pay-back times
HVAC installation Use of new technologies System approach of
hydronic design
Shorter pay-back times
Building structure(insulation, double glazing, )
Best way to save energy Larger energy savings
Long pay-back times
Building structure(insulation, double glazing, )
Best way to save energy Larger energy savings
Long pay-back times
Human factor Avoid interferences with
the HVAC system
Educate tenants andmaintenance team
Never-ending task
Human factor Avoid interferences with
the HVAC system
Educate tenants andmaintenance team
Never-ending task
Building modifications require
adaptation or modernization of
the HVAC installation to take into
account new heat gains/losses
When modifying a HVAC
installation one must take into
account the capabilities of
people using the installation
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Energy savings via hydronic optimization
4
Optimising a building's HVAC
system can reduce its energy
consumption by 30% :
By avoiding the deterioration
of production unit
efficiencies,
By optimizing the energy
efficiency of the hydronic
distribution,
By guaranteeing a stable and
accurate room temperature.
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IMPROVING
PRODUCTION UNIT
EFFICIENCIES
12
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Coefficient of Performance (COP) isused to indicate chiller efficiency:
Heat transfer (and thus COP) is good when Log Mean Temperature Differencebetween water and refrigerant is kept high
Evaporator refrigerant temperature remains constant
Supply water temperature Tsis usually kept constant
Thus return water temperature Trmust be kept "high"
to keep LMTD high
Keeping a high Tr(thus a high T = T
s-T
r) provides higher COP at partial load
Chillers
24
Evaporator
Condenser
Chilled water
Tr Ts645.2
KK
=compressor
evaporator
P
PCOP
Refrigerant saturated
suction temp.
Tr
Ts
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Effect of a decrease of the return water temp. on COP
25
Example :
Chiller: 200 tons (703 kW)
Water condenser temperatures: 29,5/35C
Supply temperature of chilled water Ts
: 7C
A reduction of return temperature of chilled water can lead to a
15% drop of the COP
Return temp. chilled water Tr [C]
COP
5
4,6
4,4
4,24
4,2
4,4
4,6
4,8
5
5,2
10,5 11 11,5 12 12,5 13
15%
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6,0
8,0
10,0
12,0
14,0
16,0
18,0
20,0
22,0
24,0
26,0
0% 20% 40% 60% 80% 100%
Variable flow proportional control
26
Re
turntemp.Tr
2-way circuit (variable flow)
Flow through terminal unit
Temperature regime:
Ts/Tr/Ti = 7/12/24C
qp
STAD
H
C
Variable flow circuit
The T through a terminal unit increases
when the flow reduces.
Thus the return water temperature increases
when the flow reduces.
All benefits for chiller COP.
Cooling
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Constant flow system proportional control
27
Returntemp.T
r
qs
qbSTAD-B C
H
STAD-P
qp
Flow through terminal unit
3-way diverting circuit (constant flow)
6,0
8,0
10,0
12,0
14,016,0
18,0
20,0
22,0
24,0
26,0
0% 20% 40% 60% 80% 100%
Variable flow circuit
Constant flow circuit
The T through a terminal unit increases
when the flow reduces.
But the flow through the terminal unit is
reduced by bypassing an increasing fractionof the primary flow (at temperature Ts).
Thus the return water temperature decreases
when the flow reduces !!!Constant
flow
Variable
flow
Temperature regime:
Ts/Tr/Ti = 7/12/24C
Cooling
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shut
Variable flow system with 2-way on-off control
28
When some CV are closed:
there is less total flow and Dp in piping
and thus more available Dp everywhere in the system
open valves receive a flow that is higher than design flow
At partial load in the system,
if a valve is open: q >= qdesignopen
qd
openopen
open openopen
qd
qd
qd
qd
qd
shut
> 0 >
> >0
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On-off control Flow increase at partial load
Manually balanced variable flow on-off control system
100 identical units; Pump head 150 kPa; Terminal unit 20
kPa; On-off CV 5 kPa
Temperature regime:
Ts/Tr/Ti = 7/12/24C
0%
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
0% 20% 40% 60% 80% 100%
To
talsystemflow
System load
At 50% load, the total flow in system reaches 73% of the total design flow.
This is a 46% increase w.r.t. the required flow (50%) at 50% load.
Seasonal flow increase lead to an estimated increased pumping energy
consumption equal to +3% of total plant energy consumption
29
3%
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0%
20%
40%
60%
80%
100%
120%
0% 20% 40% 60% 80% 100% 120% 140% 160%
On-off control Emission at partial load
At flow that is near design flow,
emitted power does not increase
much with the flow
Control signal switches on/off when
room temperature deviates much
beyond the thermostat differential
Flow
Emission
30
Roomt
Designset-point
24C
Time
At partial load in the system,if a valve is open:
k
TqP
=
(Troom - Tset-point) >=< q qdesign
P PdesignT Tdesign
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d.
0
2
4
6
8
10
12
14
0% 20% 40% 60% 80% 100%
Return water temp. degradation
Re
turntemp.T
r
System load
Temperature regime:
Ts/Tr/Ti = 7/12/24C
Below 50% of the load, which represents typically 70% of the cooling
season, the return water temperature is degraded by 1.5 to 2C.
This will result approximately in a 3 to 4% increase in seasonal chiller
energy consumption
Manually balanced variable flow on-off control system
100 identical units; Pump head 150 kPa; Terminal unit 20
kPa; On-off CV 5 kPa
31
3%
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6,0
8,0
10,0
12,0
14,0
16,0
18,0
20,0
22,0
24,0
26,0
0% 20% 40% 60% 80% 100%
6,0
8,0
10,0
12,0
14,0
16,0
18,0
20,0
22,0
24,0
26,0
0% 20% 40% 60% 80% 100%
Return water temp. proportional vs on-off control
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Returntemp.T
r
2-way proportional
3-way proportional
Temperature regime:
Ts/Tr/Ti = 7/12/24C
Cooling
Flow through terminal unit
Returntemp.T
r
System load
2-way on-off, MBV
3-way on-off, MBV
Proportional control On-off control
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Case Study - Local University campus buildings
33
Renovation of 2 University buildings with a total of 9840 m2
Installed cooling capacity: Building 1 : 1452 tons refrig.
Building 2 : 1730 tons refrig.
Work performed during summer 2010
Results compared for Oct.-Nov. 2009 vs 2010
DP controllers paired with manual balancing valves installed
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Local University campus building 1 chiller saving
34
Variable secondary flow
with differential pressure
bypass
Dp controllers at on-off
control FCU groups and
PAU/AHUs
and re-balanced
Annualized 22%
chiller energy
savingCooling load [kW]
Powerinput[kW]
2009
2010
Chiller Power Input vs. Cooling Load
34
22%
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Local University campus building 2 chiller saving
Variable flow primary-secondary system
Addition of Dp controllersat FCU groups zones and
pressure independent
control valves for
PAU/AHU and re-balanced
Annualized 16.5%
chiller energy
savingCooling load [kW]
Powerinpu
t[kW]
2009
2010
Chiller Power Input vs. Cooling Load
35
16%
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Case study - business hotel at Sheung Wan
> First LEED and BEAM Plus Platinum
certifications of new-built hotel
> 38 floors, 274 rooms
> Chiller capacity 667 kW x 2 nos
> Variable primary flow design
> Hydronic balancing design
> Chiller plant balancing> Dp control at each floor and
modulating terminals
> Balancing and control valve at FCUs
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Hydronic balancing in variable primary flow
Balanced chiller plant
1
Proper fail-safe bypass valve
sizing and characteristic
2
Balancing & control
valve for proportional
balancing
4
DP stabilization against large
Dp fluctuations in part load
3
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Computerized hydronic system design
TA Select 4
hydronic system calculation
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Computerized hydronic system design
> Pipe sizing per BEC recommendations
> Balancing valve sizing and pre-settings for easy and efficient
commissioning
> Minimum control valve authority checks (suggest > 0.25) to ensure
indoor comfort with stable temperature control
> Correct Index circuit identification to help determining optimal VFD
sensor location and set-point
> Pump head optimization:
> Initial : 350 kPa
> Select 4 : 236 kPa (-33%)
> Final set : 250 kPa (-29%)
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Computerized hydronic system design
> Bypass valve sizing calculation
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Tips for reliable and energy efficient VPF system
> Make use of computerized software for hydraulic design calculations
> Chiller plant must be balanced to avoid uneven distribution of flow
> Proper bypass valve sizing and select with good rangeabilty, linear
characteristic (or equal percentage characterisitic at 0.25 authority) valve> Use of high precision flow meter and local controller to monitor total return
flow as fail-safe measure against chiller minimum flow
> Use of DP controllers
> to stablize Dp fluctuations to avoid overflow and low dT problems
> to maintain good control valve authority necessary for stable temperature control
> as flow/DP/DT/energy measuring station for energy audit purpose
> Make system sustainable and adaptive to future changes
> Locate VSP sensor at index circuit and adjust set-point to the DP of the most
demanding stablized circuit potentially up to 40% pump energy saving
> Make use of computerized balancing method and instrument to produce
balancing report without manual record of measurements and verfications
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Conclusion
92
Important energy savings can be achieved by taking care of: Maintaining cold/warm return water temperature
to condensing boilers/chillers (~15%),
Having an adequate pressurisation avoiding scaling/foulingin boilers/evaporators (~5-10%).
Minimising pumping costs requires having (up to 40% on 7-17% in cooling):
A good pressure maintenance to avoid corrosion leading to aging and fouling,
An optimized hydronic distribution design (Dp control),
A systematic methodology of balancing and commissioning.
Stable and accurate room t control gives (~5-20%) energy savings by:
Avoiding oversizing in on-off systems,
Using state-of-the-art thermostatic radiator valves,
Sizing of modulating control valves for good minimum authority.
The approach "He who can do more can do less" is to be avoided
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