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Performance characteristics of the geotechnical cold rooms Baker, T. H. W.; Frederking, R. M. W.; Hoffman, D. R.
PERFORMANCE CHARACTERISTICS OF THE GEOTECHNICAL COLD ROOMS
T.H.W. Baker R.M.W. Frederking
D.R. Hoffman
Two low temperature Iaboratories have been operating in t h e
Division of Building Resea~ch, National Research Council of Canada,
since July 1954. e initial design of these cold rooms w a s first
described by G o l d ( 3 . One cold room was used until 1970 by t h e
Division" Building Services Section f o r experiments related to cold weather building research but i s now being used by the
Geotechnical Section for frozen ground studies (Permafrost cold
room). The other cold room is used by the Geotechnical S e c t i o n for ice research (Ice cold room). Construction and layout of the two rooms and a b r i e f description of the associated r e f r i g e r a t i o n
and c o n t r o l equipment are included in this paper.
In the 2 1 years since t h e i r construction these cold rooms
have performed extremely well. Some modifications and changes
have recently been made, however, and new control systems were
installed following which a perf~mance study was made of the a i r
temperatures maintained during steady state and transient
conditions. This study permitted f i n e adjustments to be made for
optimum control of temperature stability and response. The
resulls of t h i s study are also included in this paper.
This information is necessary to evaluate experiments
performed in the cold rooms. The temperature distribution and
stability in the cold room a f f e c t s t h e temperature h i s t o r y of
samples of ice and frozen soil which are moved from zone to zone
during storage, machining and t e s t i n g , and also a f f e c t the time required for specimens to reach thermal equilibrium before testing. PLANS AND CONSTRUCTION DETAIU
Details of the frame construction and wall section are
presented in Figures 1 and 2. Both cold rooms are identical.
The only permanent service connections brought into the cold
rooms were t h o s e required for lighting, refrigeration, and o t h e r
permanent machinery. Three service panels each consisting of
twelve 2-in. (50-cm) diameter capped ports arranged in three rows
connections were brought i n t a the rooms through these ports.
Recording equipment used in the experiments is located outside the
cold rooms.
The layouts of the c o l d rooms, at the time of this study, are
given in Figures 3 and 4. The equipment used for machining and t e s t i n g can be moved to any location within the room thus
providing maximum flexibility to accomodate a variety o f t e s t i n g
procedures.
From Ffgures 3 and 4 it can be seen t h a t there was a greater
mass of equfpment in the Ice cold room than in the Permafrost cold room at t h e time of t h i s performance study.
DESCRIPTION OF REFRTGERATION P M
The cooling load of the two rooms is shared between three
similar r e f r i g e r a t i o n circuits (Figure 5). The compressor and
condenser are located in a separate machinery room, with only the
evaporator unit and expansion valve in t h e cold room. Each room
has t w o evaporator units (Figure 6). A main evaporator is
connected to one compressor, t h e auxillary evaporator is connected
to t h e t h i r d (auxillary) compressor which can be connected to the
auxillary evapararor in either of t h e two rooms. This t h i ~ d
(auxillaxy) refrigeration c i r c u i t serves several purposes, namely:
back-up in the event o f failure of one of the main circuits; extra
cooling capacity for rapid "'draw downtt or high heat loads; and, as
an alternate system during t h e defrosting o f t h e heat exchanger
coils i n the main evaporator unit.
The system was designed to have a low inertia temperature
control. This was accomplished through high voXwne a i r cixcnlatian
and electrical reheating for fine temperature control. The
compressors sun continuously under a constant load, cooling the air
to about -40°C. A f t e r being cooled, the air is warmed by
electrical reheat coils t o bring i t s temperature up to t h e s e t
p o i n t temperature. A fan draws a i r from the room through t h e
evaporator unit for conditioning and it is exhausted through a
plenum above the false c e i l i n g so as to provide relatively d r a f t free a i r circulation, A schematic o f the electrical s i d e of the
r e f r i g e r a t i o n c i r c u i t i s shown in F i g u r e 7 .
Temperature control is achieved by varying the power supplied
to t h e electrical reheat coils. Cold room temperatu~e is measured by a 100-ohm resistance temperature sensor placed in the air
intake at the bottom of the evaporator. This is the temperature
control sensox t h a t modifies an electrical signal f e d inta a
s o l i d - s t a t e c u r r e n t a d j u s t i n g proportional controller. The
t h e set point temperature are compared within the controller in order t o produce a milliamp level control signal. This signal is sent to a silicon controlled rectifier package in the current valve
which regulates the power supplied t o t h e r e h e a t coils. One h a l f
sf the maximum power output is supplied to the reheat coils when
the room temperature is equal to the set point temperature. If the measured room temperature i s greater than the set temperature then the power output t o t h e coils is l e s s ; if less than t h e set
temperature then the power output is greater.
TEMPERATURE PERFORMANCE
It is necessary to "tune*' the controller to the unique
characteristics of the cold room in o r d e r to optimize temperature
control. For t h i s reason a temperature performance study was
undertaken i n both cold rooms. The control u n i t i s shown i n Figure 8. Thirty copper-constantan themocouples were placed at
various locations within t h e rooms and temperature measurements
were made using a Kaye data logger having a resolution of
approximately 50. I 'F (20.06OC)
.
Temperatures were converted todegrees Celsius and rounded o f f to the nearest tenth of a degree.
One thermocouple was placed in an ice bath to check the performance
of the data logger. Evaluation of the thermal behavioux of the
cold rooms included measurements of t h e temperature profiles moth
v e r t i c a l and horizontal) at different room t e q e r a t u r e settings,
temperature fluctuations under steady state and t r a n s i e n t
conditions, a ~ l d the change in room temperature during a defrost
cycle.
(a) Temperature Profiles
Typical profiles for t h e Permafrost and Ice cold roams are
shorn i n Figures 9 and TO, r e s p e c t i v e l y , f o r nominal control
settings ranging from -5 to -40°C. Thermocouples were spaced
every half metre. The horizontal temperature at midheight in
each room fluctuated only 2 0 . 2 ~ ~ from one position in t h e room t o another. The v e r t i c a l d i s t r i b u t i o n of temperatures i n the centre of t h e Ice cold room showed l i t t l e variation. In the Permafrost cold room a d i s t i n c t v e r t i c a l temperature gradient was found in t h e middle of t h e room with the difference in temperatures between the f loox and just above t h e false c e i l i n g being as much as 0 . 7 O C .
@) Constant Set Point
Temperature variations w i t h time were recorded Sn both rooms
for specific temperature s e t t i n g s . Figures I1 and 12 show the variations in temperature at t h e control sensor in the bottom o f
the evaporator and at the midpoint of the room when the Ice cold
shows t h e short-term fluctuation over a period of 70 minutes. It
was noted that opening the door for a few minutes raised the temperature at the midpoint of the room 0. S°C. Figure 12 shows the temperature fluctuation over a period of about 18 hours.
Fluctuations of about *0. I 0 C occur in both cold rooms a t any one
point. It should be noted that the temperature recorded a t t h e
control sensor was always a few tenths of a degree lower than t h a t
recorded a t the midpoint of the room and t h a t b o t h were below the
nominal set point. The temperature difference between the control
sensor and t h e s e t point were still within the specified limits of
the controller,
Step Change &-I Set Point
Changing the temperatures of the cold moms from one s e t
paint t o another was investigated. Figures 13 and 14 show t h e
temperatme change with time recorded at the control sensors and
midpoints of the two cold rooms when the setting was lowered from
-10 to -30'C over a period of 5 to 6 hours. Figure 15 shows the
temperature change in t h e Permafrost cold room when the nominal
set temperature was raised from -30 to -10'~ over a 4-hour period.
Figures 13 and 14 show t h a t the temperatures at the control
sensor and midpoint come to equilibrium in the Permafrost cold
room a f t e r approximately 3 hours and in the Ice cold room after
about 5 hours. Tfiis difference was probably due to the differences
in size and configuration of the two cold rooms and t h e bulk mass
of equipment in each of them. As shown in Figure 1 5 , when raising
the temperature in the Pemnafrost c o l d room, the temperature at
t h e controf sensor smoothly approached the set temperature a f t e r
3 hours. The midpoint of the room experienced an 'lovershooting"
of the set temperature by two degrees. F i n e tuning o f the control system can eliminate l ' o ~ e r s h o o t ~ ~ at any point in the room where
the control sensor is placed.
Defrost Cycle
Moisture in the air precipitates out, forming frost on t h e cooling coils o f the evaporator unit. For this reason, the
relative humidity in the cold rooms ranges from 35 t o 4 0 per cent.
The evaporator unit must be shut down about once a month for
defrosting d u r h g which t i m e the temperature is controlled by the
auxiliary cooling system. Heating elements are used to remove the
frost build-up on the cooling coils. The e f f e c t of def~asting t h e
main unit in the Ice cold room on the measured temperature at the
control sensor of the auxiliary u n i t and midpoint of the room is shown 5n Figure 16.
As the de-frost heaters melt the frost the room temperature
in a i r temperature occurs. A t this paint the heaters are t u n e d off and within an hour the temperatures stabilize. When the main unit and fan are turned on a b l a s t of h o t air enters the room which raises the temperature considerably f o r a short time.
SUMMARY
The DRR Geotechnical cold rooms have the following
characteristics:
1. TemperatuTe can be controlled f r o m 0 to -40°C. A i r temperature fluctuates, at any one point,
3 . Temperature variation between different locations in
the rooms is f OC.
4. Relative humidity is between 35 and 40 per cent.
5, Three to 5 hours are necessary for the rooms to reach
equilibrfum when the s e t room temperature is changed
20 Celsius degrees.
6 . E r r a t i c temperatures occur during the monthly defrost
cycle.
REFERENCE
1. Gold, L.W., New Snow and Ice Research Labo~atory i n Canada,
FIGURE 1
F R A M E C O N S T R U C T 1 O N
OF
C O L D ROOMOPPER VAPOUR SEAL (SOLDERED SEAMS)
-h R m m m " m
....
...
- = - A/4" PLYWOODWIRE HANGERS TILE FURRING
ACOUSTIC TILE
lJI4-l-
COPPER VAPOUR SEAL (SOLDERED SEAMS)3/4" T &
G
DIAGONAL 2" X 4" STUDDING AT 1 ' 1 3/4" 0 .C. 2" X 2" HORIZONTAL FURRING 3" 2" X 2 " VERTICAL FURRING 7 / 8 ' 7 T G FINISHED WALLS 8" FIBER GLASS " F l BER GLASS 7/8"T
& G FLOORING 3/4" T & G DIAGONAL 4" AT 1'
I 314" 0 .C. 4" AT 1 ' 1 314" O.C. COPPER VAPOUR SEAL(SC
3/4" T & G DIAGONAL 3LDERED SEAMS) '4" X 4" SLEEPERS AT 2 @ Q .C
.
S C A L E 2 0 " = FIGURE 2 W A L L S E C T I O N O F C O L D ROOMCOMPRESSOR 6 C Y L I N D E R
(3.5 T O N ) 2 S T A G E
D I R E C T E X P A N S I O N
F I G U R E 5
1 i. ' < " < F i g u r e 6
-.
. . .,re>?.
Photo of Evaporator . , d . . ,+.,, , . . - <, "- C . . r ,! ; - ' .,:4 I I -=!=& ;;.. . ' / ; , f " > < > r 8 208 V, 3 PHASE TEMP TEMPERATURE C T L CURRENT RECORDER VALVE TEMPERATURE REHEAT, 15KW SENSORS I200 RPM C O L D ROOM 208 V, 3 PHASE DEFROST, 3KW F i g u r e 8Photo of Control Panel
Figure 7 E l e c t r i c a l Schematic I ? ! -a* . &?*, '"Rh"'-" > .-
M I D H E I G H T H O R I Z O N T A L
D I S T R I B U T I O N D I S T R I B U T I O N V E R T I C A L N O M I N A L S E T T I N G
B A C K FRONT R I G H T L E F T T O P BOTTOM
F l G U R E 9
M I O H E I G H T H O R I Z O N T A L DISTRIBUTION
VERTICAL N O M I N A L
D I S T R I B U T I O N
-
SETTING - s a cBAC K FRONT R I G H T LEFT
0 - 3 4 b TOP BOTTOM F I G U R E 10 P R O F I L E S O F I C E C O L D ROOM
- 1 0 . 0 h 4 M I D P O I N T O F R O O M OZ ...
t
,,,,,,,,/,,,,,,, \ ,,,,,,,,,--- -- 9 . 0 - 2 - 4 '.J 0 - 6 10 T I M E , h I I N O M I N A L-
-
S E T T 1 N G - -lO°C-
- F I G U R E 1 2 L O N G T E R M F L U C T U A T l O l d I N I C E C O L D ROOM-
-
P O I N T OF R O O M-
-
-
-
-
d --
-
-
-
-
3 4 FIGURE 1 5 T R A N S I E N T E V E N T , -30°C TO - l a D C I N P E R M A F R O S T C O L D R O O MT E M P E R A T U R E , *C