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8/18/2019 R&T 2001 - Cold Storage Warehouse Dock Study - Jekel
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Cold Storage Warehouse DockParametric Study
Todd B. Jekel, Ph.D.Industrial Refrigeration Consortium
Topics
Objective
Modeling loads Infiltration
Desiccant operation
Effects of dock temperature setpoint
and addition of desiccant dehumidifierEffects of infiltration and defrost
Conclusions
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Objective
Develop a modeling tool for freezer anddock loads associated with dockoperation
Investigate effect of infiltration, defrostand dock setpoint on total refrigerationsystem energy use
Investigate effect of adding a desiccantdehumidifier to the dock
Refrigerated dock function
The most obvious function is to facilitate thestaging and transfer of stored goods
What about from the refrigerationperspective? “Protects” the freezer from infiltration by allowing
for removal of humidity at a higher temperaturelevel
“Protects” the employees from dangerous snowand ice at the freezer/dock door Assisted by a well designed and operated freezer door
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Simulation of the Loads
Weather NOAA surface observations
of temperature and wetbulb
Dock People
Equipment (fans, forks, lights)
Infiltration (ambient load and freezer credit)
Transmission
Defrost
Freezer (incremental) Load from dock plus door heat (to avoid snow/frost)
Defrost associated with latent load from dock
0 5 10 15 20 25
70
75
80
85
90
95
100
Hour Number
T e m p e r a t u r e ,
[ o F ]
Dry-bulbDry-bulb
Wet-bulbWet-bulb
ASHRAE 0.4% Design
ASHRAE 0.4% Design Mean Coincident Wetbulb Temperature
Drybulb Temperature
Infiltration
Ambient air that enters the conditionedspace
Uncontrolled
Unconditioned
Importance in refrigerated spaces
Largest source of humidity (i.e. frost)
Not as much of a problem now in WI
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Infiltration through anunprotected door
The amount of air flow through a doorway asa function of only temperature difference isimpressive
Truck bay door 10’ wide x 9’ high
Dock 35F/86%, Ambient 91F/73F1 wetbulb
Results in:2
equivalent of 80 ft/min velocity through the door
36 tons sensible, 32 tons latent
In other words, 1.1 ton-hrs per minute of open door
1 ASHRAE 0.4% Design conditions for Minneapolis
2 No influence of pressure difference from wind, etc.
Freezer infiltration
10’ wide x 14’ high
Usually have a protective device
Strip curtain, air curtain, or both
Doorway effectiveness, η
Fraction of unprotected doorway air exchange thatis protected from exchange
In other words, multiply the unprotected doorwayexchange by (1 – η) to determine the estimatedprotected doorway air exchange
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Freezer doorway effectiveness
82-94%Strip curtain
78-93%Fast sliding doors
65-78%Dual horizontal
air curtain
49-80% Vertical air curtain
Values taken from:
Downing, C.C., W.A. Meffert, 1993, “Effectiveness of cold-storage door infiltration protectivedevices,” ASHRAE Transactions, vol. 99, part 2, pp. 356-366.
Freezer loads
Plots of sensible and latent load on freezer asa function of door effectiveness and dockconditions
5 10 15 20 25 30 35 40 45 500
2
4
6
8
10
Dock Dewpoint [oF]
L a t e n t L o
a d
[ t o n s ]
m
w [
l b / h r ]
Warehouse: -20oF, 90% RH
10 0
60
40
20
0
80
η = 95%
η = 90%
η = 85%
η = 80%
20oF Dry Bulb
50oF DB
40oF DB
30oF DB
20 25 30 35 40 45 500
5
10
15
20
Dock Temperature [oF]
S e n s i b l e L
o a d
[ t o n s ]
Warehouse: -20oF, 90% RH
η = 95%
η = 85%
η = 80%
η = 90%
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How do desiccants dehumidify?
Adsorption of water vapor from humid air onthe surface of the desiccant (solid type)
A “heat-activated water pump”
Use heat source to regenerate (drive-off moisture)the desiccant
Adsorbs water vapor from humid air on thesurface of the desiccant (gives off heat similar tocondensation)
Humid air is dehumidified and heated
Schematic and PsychrometricRepresentation of Desiccant
2,300 scfm
256 F / 0.022 lb/lb120 F / 0.038 lb/lb
9,000 scfm
42 F / 0.005 lb/lb74 F / 0.0008 lb/lb
R
PS
50 100 150 200 2500.00
0.01
0.02
0.03
0.04
T [°F]
H
u m
i d i t y R a t i o
Pressure = 14.7 [psia]
0.5
0.2
0.05
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Desiccant System Schematic
35 F
> 40 FDesiccant
wheel
operational
Exhaust to
ambient
Conditioned
Supply Air
Intake air
from Dock
Intake
from
ambient
F r e e z e r
Dock Details
Located in Minneapolis, MN
Dock setpoint of 35F
Attached to a –20F warehouse
8,000 ft2 of dock perfreezer door (η = 85%)
900 ft2 of dock per truckbay door (open 2 minutesper hour)
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Design Day Energy Use
Mechanical-refrigeration only Freezer load: 4.7 ton-hr/ft2 of door/SHR = 0.85
Peak dock load 200 ft2 /ton
0.33 kWh/ft2 per design day
$0.016/ft2 per design day1
With desiccant (flow rate 0.56 cfm/ft2 ofdock) Freezer load: 4 ton-hr/ft2 of door/SHR = 0.98
Peak dock load 175 ft2 /ton
0.35 kWh/ft2 and 0.007 therms/ft2 per design day
$0.019/ft2 per design day11 Assume $0.05/kWh and $0.25/therm
Mechanical-only LoadBreakdown
Credit
29%
Lights
7%
Forks
5%
Defrost
8%
Net load
72%
Ambient infiltration
38%
Occupants
0% Transmission
10%
Evaporator fans3%
Dock setpoint 35F
Gross Load 140 ft2/ton
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Desiccant Load Breakdown
Credit
26%
Lights
7%
Forks
5%
Evaporator fans
4%
Defrost6%
Net load
74%
Transmission
10%Occupants
0%
Ambient infiltration
37%
Desiccant
5%
Dock setpoint 35F
Gross Load 130 ft2/ton
Effect of Dock Setpoint
0
0.005
0.01
0.015
0.02
0.025
0.03
0.035
25 30 35 40 45 50
Dock Dry-bulb Setpoint (F)
C o
s t p e r D e s i g n
D a y ( $ / s q f t )
Mechanical only/Hot Gas
Mechanical only/Electric
Desiccant, 0.56 c fm/sqft
Desiccant, 0.38 c fm/sqft
No Defrost
Required
Note: “Hot Gas” and “Electric” refer to the method of applying dock/freezer door heatto avoid frost, etc.
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Effects of Defrost Load
Double the energy associated with defrost
Mechanical Refrigeration-only 16% increase in dock load
Negligible effect on freezer load
9% increase in design day energy use and cost
With 0.56 cfm/ft2 desiccant 10% increase in dock load
Negligible effect on freezer load
6% reduction in design day energy use and cost
Conclusions
Infiltration Ambient
Large effect on dock load
Dock/freezer Large effect on both dock and freezer load
Mechanical refrigeration-only 33-35F dock setpoint is near optimum
Desiccant opportunities Benefits from higher setpoint in the dock
Proper sizing important
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Future work
General Optimum dock temperature determination as a function of
ambient conditions.
Freezer door Dock/freezer air exchange conditions that result in “no frost”
condition in the freezer.
Methods for control of door heat addition to prevent freezerfrost.
Desiccant Investigate sizing of desiccant system.
Investigate siting of desiccant system inlets and outlets.
Investigate alternative control of desiccant system.