© 2011 Ingersoll Rand Waterside Energy Recovery Requirements, Design and Application Waterside Energy Recovery Requirements, Design and Application Mick Schwedler, PE manager Trane applications engineering
Jan 19, 2015
© 2011 Ingersoll Rand
WatersideEnergy RecoveryRequirements, Design and Application
WatersideEnergy RecoveryRequirements, Design and Application
Mick Schwedler, PEmanagerTrane applications engineering
reasons to useEnergy Recovery Required by code or standard
Availability of simultaneous heatingand cooling loads
Economically justified Reduces heating load Reduces ancillary power
Environmentally responsible Reduces emissions Eligible for “green” benefits (energy, water
usage)
ASHRAE 90.1-2010 (since 1999)Waterside Energy Recovery
Facility operates 24 hours per day Heat rejection exceeds 6 million Btu/hr
(~ 450 tons)
Design service water heating load exceeds 1 million Btu/hr
Required energy recovery is(smaller of): 60% of design heat rejection
Preheating water to 85°F
IF …
THEN
types ofHeat-Recovery Chillers Single condenser (“bundle”)
Dual condenserEqually sized
bundles
Auxiliary condenserUnequally sized
bundles
standardcondenser
heat-recovery
condenser=
standardcondenser
heat-recovery
condenser>
heat-recovery chillersSingle Condenser
centrifugal compressor
scroll compressor
helical-rotary (screw)compressor
heat-recovery chillersDual Condenser
heat-recoverycondenser
standardcondenser
evaporatorwater-cooled chiller withcentrifugal compressor
heat-recovery leaving capacity chillercondenser water control? efficiencyFull capacity hot yes decreasesPartial capacity warm no increases
heat-recovery chillersComparison of Options
Chiller condenser optionCharacteristic Dual Auxiliary “Heat pump”
Configuration Second, Second, No extrafull-size smaller condensercondenser condenser
Application Large Preheating Large base-heating loads heating loadsloads or continuous
operation
Leaving water Hot Warm Hot
Capacity control? Yes No Yes
Chiller efficiency Decreases Increases Acceptable
variable air volumeTempering Supply Air When required supply/primary airflow is less than minimum setting:
Reduce primary airflow to minimum
Let space temperature drift downward
Add heat to avoid overcooling105°F (40.6°C) water often is sufficient
Supply air is always dehumidifiedSupply air is always dehumidified
waterside heat recoveryTemperatures
Service-water 85°F to 95°Fpreheating (29.4°C to 35°C)
Space heating 105°F to 110F(40.6°C to 43.3C)
source: 2008 ASHRAE Systemsand Equipment Handbook
Effectively balancesheat-recovery temperaturesand system pressure drops
tempering VAV supply airHeating Coil Selectionselection parameter 1-row coil 2-row coilEntering water 113°F 105°FCoil flow rate 4.33 gpm 1.75 gpmFluid delta-T 6.02°F 14.91°FCoil fluid pressure drop 10.3 ft H2O 0.21 ft H2OAir pressure drop:
design cooling airflow 0.45 in. wg 0.79 in. wgminimum airflow (est) 0.04 in. wg 0.07 in. wg
Leaving-coil (primary) air 75°F 75°F
waterside heat recoveryEffect on Chillers Compressor work is proportional
to lift “Lift” is pressure difference between evaporator
and condenser
Warmer condenser water (for heat recovery)raises condenser pressure
Changes in lift affect different compressors differently Positive displacement
Centrifugal (full load vs. part load)
positive-displacement water chillerRefrigeration Cycle
enthalpy
pre
ssu
re
evaporator
compressorliquid/vaporseparator
expansiondevice
condenser
16
7
5
4 3
heat recovery
2
positive-displacement water chillerCapacity
temperature rise (leaving-condenser water)
100
0° 10° 20° 30° 40°
chill
er c
apac
ity,
%
80
60
40
20
0
compressortype:
scrollscrew
temperature rise (leaving-condenser water)
100
0° 10° 20° 30° 40°
pow
er in
crea
se,
% k
W/
ton
80
60
40
20
0
compressortype:
scrollscrew (S)
positive-displacement water chillerEfficiency
screw (M)screw (L)
centrifugal chiller performancePower Increase
condenser water temperature, °F
26
pow
er in
crea
se,
% k
W/
ton
10
imp
eller diam
eter, inch
es
20
30
40
085 87 89 91 93 95 97 99
28
30
32
power increase
impeller diameter
compressorchange
Heat recoveryChiller 85-105 F
centrifugal chiller comparisonEfficiency
Operating modeChiller type Cooling Heat recovery
Cooling only 0.57 kW/ton Not applicable(6.2 COP)
Heat recovery 0.60 kW/ton 0.69 kW/ton(5.9 COP) (5.1 COP)
Entering to leaving water temperatures:Evaporator 54°F to 44°F 54°F to 44°F
(12.2°C to 6.7°C) (12.2°C to 6.7°C)
Condenser 85°F to 95°F 85°F to 105°F(29.4°C to 35.0°C) (29.4°C to 40.6°C)
heat-recovery chiller controlCondensing Temperature
% load
% m
axim
um
pre
ssu
re d
iffe
ren
tial
B
CA
unloading with constantleaving hot-water temperature
unloading with constantentering hot-water temperature
Compressor type Acceptable basis of control
Positive displacement Entering-condenser water temperature
Leaving-condenser water temperature
• Provides less capacity• Uses more power
Centrifugal Entering-condenser water temperature
• Reduces likelihood of surge
heat-recovery chiller controlCondensing Temperature
Energy Recovery Topics Airside
Outdoor air Types Requirements Operation
Supply air tempering Requirements Operation
Waterside Requirements
Types
System configurations
Operation
system configurationPrimary–Secondary
Available heat= 150 × (52.6 – 40)= 1890 MBh
Auxiliary heat required= 2000 – 1890= 110 MBh
Available heat= 150 × (52.6 – 40)= 1890 MBh
Auxiliary heat required= 2000 – 1890= 110 MBh
heat-recoverychiller production
(supply)
distribution(demand)
40°F825 gpm56°F
40°F225 gpm
52.6°F
40°F
40°F
52.6°F
52.6°F
off
750 gpm
300 gpm
system configurationPreferential Loading
Available heat= 150 × (56 – 40)= 2400 MBh
Rejected heat= 2400 – 2000= 400 MBh
Available heat= 150 × (56 – 40)= 2400 MBh
Rejected heat= 2400 – 2000= 400 MBhproduction
(supply)
distribution(demand)
40°F825 gpm56°F
40°F225 gpm
51.2°F
40°F51.2°F
off
750 gpm
heat-recoverychiller
40°F56.0°F
300 gpm
525 gpm
system configurationsSidestream Loading
Available heat= 150 × (56 – 42.7)= 2000 MBh
No rejected heatNo auxiliary heat
Available heat= 150 × (56 – 42.7)= 2000 MBh
No rejected heatNo auxiliary heat
production(supply)
distribution(demand)
40°F825 gpm56°F
40°F75 gpm
50.2°F
40°F50.2°F
off
900 gpm
heat-recoverychiller
42.7°F56°F
300 gpm
51.2°F
system configurationsSidestream LoadingControl strategies:
Satisfy heating requirements
Maintain leaving-condenserwater temperature(positive-displacement compressors)
system configuration comparisonHeat Available/Required
System configurationPrimary–
Characteristic secondary Preferential Sidestream
Cooling load:cooling-only units 393 tons 350 tons 383 tonsheat-recovery unit 157 tons 200 tons 167 tons
Heat-recovery 40°F 40°F 42.7°Fsupply temperature
Available heat 1890 MBh 2400 MBh 2000 MBh
Auxiliary heat 110 MBh –400 MBh* 0 MBhrequired
*Surplus recovered heat must be rejected
system configurationsVariable Primary Flow
VFDmodulating control valvefor minimum chiller flow
Piping heat-recovery chillerin sidestream position maysimplify control
Piping heat-recovery chillerin sidestream position maysimplify control
controlvalve
bypass line
heat-recoverychiller
system configurationsDistributed SidestreamTypical application:
Remote heating requirement
Chilled water load
Small chiller (or water-to-water heat pump)
chilled watersupply or return
heatingload
heat-recovery chiller
airside system optionsLoad-shedding economizer
outdoor-airtemperature sensor
controller
chilled watersupply or return
heatingload
heat-recovery chiller
Control cooling load soheat rejection equals
heating load
airside system optionsLoading chiller with exhaust airstream
EAEA
RARAEAEA
spacespace
OAOA SASAMAMA CACA
CC
T
HH T HH
CC
Water to chillerWater to chiller
Water from chillerWater from chiller
single condenserHeat-Recovery Control
water-cooledchiller
condenser
evaporator
coolingtower
P P
P
coolingload
heatingload
V2heat
exchanger
T2
controller
T1
V1controller
Dual-Condenser Chillers
heat-recoverycondenser
standard condenserpiped to cooling tower
centrifugalheat-recovery chiller
dual condenserHeat-Recovery Control
water-cooledchillerevaporator
P
standardcondenser heat-
recoverycondenser
heatingload
P
coolingtower
P
coolingload
V2
T2
auxiliaryheat
PT1
Control based onentering-condenserwater temperature
Control based onentering-condenserwater temperature
controller
controller
Analysis ToolstoolSystem Analyzer™
TRACE™ Chiller PlantAnalyzer
EnergyPlus, HAP, TRACE
applicationHigh-level scoping (< 1 hr)
Simplified building entries
Full analysis of chilled water plant, economic rates
Full energy simulation
Hour-by-hour calculations of energy consumption, power demand, related costs
Waterside Energy Recovery Steps Simultaneous heating
and cooling loads
Chiller HR capacity = Design heat recovery load
Select lowest temperature that meets requirements
Select the proper chiller type
Analyze the system
Place the chiller(s) in the appropriate system location
Design the system with the proper connections and controls
Train the building operators
Operate the system properly
waterside heat recoveryReferencesFrom Trane:
Waterside Heat Recovery in HVAC SystemsSYS-APM005-EN
1991 Engineers Newsletter: “Two GoodOld Ideas Combine to Form One New Great Idea”http://www.trane.com/commercial/library/EN20-1.pdf
By others:2008 ASHRAE Handbook: HVAC Systems and Equipmentchapter 8
2003 ASHRAE Journal: “Energy Efficiency for Semiconductor Manufacturing Facilities”Ralph M. Cohen, PE (August issue)
waterside heat recoveryReferences
2008 ASHRAE Handbook: HVAC Systems and Equipmentchapter 8
2003 ASHRAE Journal: “Energy Efficiency for Semiconductor Manufacturing Facilities”Ralph M. Cohen, PE (August issue)