U.S. patent number 3,898,860 [Application Number 05/514,347] was granted by the patent office on 1975-08-12 for automatic defrosting control system.
This patent grant is currently assigned to Texas Instruments Incorporated. Invention is credited to James B. Allen, Samuel T. Bryant, Glen C. Shepherd.
United States Patent |
3,898,860 |
Shepherd , et al. |
August 12, 1975 |
Automatic defrosting control system
Abstract
An automatic defrosting control system for a refrigeration
system having an evaporator or the like for absorbing heat from a
zone to be cooled and a cold control to maintain the zone
substantially at a preselected temperature, the evaporator being
subject to the accretion of frost thereon which thereby increases
the periods of energization of the evaporator in order to maintain
the zone at the preselected temperature. The control system
comprises means for causing defrosting of the evaporator, a
thermostat and a thermal time-delay relay.
Inventors: |
Shepherd; Glen C. (Garland,
TX), Allen; James B. (Richardson, TX), Bryant; Samuel
T. (Louisville, KY) |
Assignee: |
Texas Instruments Incorporated
(Dallas, TX)
|
Family
ID: |
24046781 |
Appl.
No.: |
05/514,347 |
Filed: |
October 15, 1974 |
Current U.S.
Class: |
62/155; 62/234;
62/140 |
Current CPC
Class: |
F25D
21/002 (20130101); F25D 17/065 (20130101); F25D
2317/0653 (20130101); F25B 2600/23 (20130101); F25D
2400/04 (20130101) |
Current International
Class: |
F25D
21/00 (20060101); F25D 17/06 (20060101); F25d
021/06 () |
Field of
Search: |
;62/80,155,234,140 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Wye; William J.
Attorney, Agent or Firm: McAndrews; James P. Haug; John A.
Baumann; Russell E.
Claims
What is claimed is:
1. An automatic defrosting control system for a refrigeration
system having cooling means for absorbing heat from a zone to be
cooled and thermostatic means for periodically energizing the
cooling means to maintain the zone substantially at a preselected
temperature, said cooling means being subject to the accretion of
frost thereon which thereby increases the periods of energization
of the cooling means in order to maintain the zone at the
preselected temperature, said control system comprising:
means for causing defrosting of said cooling means;
a thermostat adapted to be positioned in heat-exchange relation
with both said cooling means and said defrosting means and adapted
for connection in a control circuit, said thermostat having a first
switching position for terminating energization of said defrosting
means and a second switching position for enabling operation
thereof, said thermostat switching from its first to its second
position in response to its temperature falling to a lower
predetermined level and switching to its first position in response
to its temperature rising to a higher predetermined level;
a thermal time-delay adapted to be positioned in heat-exchange
relation with said cooling means and adapted for connection in said
control circuit, said relay having a first switching position for
permitting operation of said cooling means and a second switching
position for energizing said defrosting means and preventing
operation of said cooling means, said relay switching from its
first position to its second position upon reaching a given
temperature and switching from its second to its first position
upon reaching a different preselected temperature;
said thermostatic means being responsive to the temperature in said
zone to periodically energize said cooling means to cycle between
an "on" mode and an "off" mode to maintain the zone substantially
at said preselected temperature; and
means responsive to the duration of one of said modes to supply
heat to said relay whereby upon a sufficient accretion of frost
forming on the cooling means the increased duration of the "on"
mode will cause the temperature of the relay to reach its given
temperature and switch to its second position and will cool said
thermostat to cause its temperature to fall below its lower
predetermined level and switch to its second position thereby
energizing said defrosting means.
2. A system as set forth in claim 1 in which said heat-supplying
means is an electric resistance heater adapted to be energized
during the "off" mode of the cooling means whereby as the accretion
of frost increases the duration of the "on" mode lengthens and the
duration of the "off" mode shortens thereby to decrease the heat
supplied to the relay and permit it to cool to a lower given
temperature and switch to its second position to energize said
defrosting means.
3. A system as set forth in claim 2 wherein the thermostatic means
and the relay when in its first position are serially connected
with the cooling means and the heater is shunt-connected across the
relay and thermostatic means whereby the heater is deenergized only
when the relay is in its first position and the thermostatic means
is closed.
4. A system as set forth in claim 3 wherein said heater is a
self-regulating, self-heating positive temperature coefficient
resistor having a relatively low initial resistance which increases
abruptly as its temperature rises above a given level.
5. A system as set forth in claim 4 which further includes another
heater in heat-exchange relation to said relay and adapted for
connection in the control circuit when the thermostat is in its
first position to supply heat to said relay.
Description
BACKGROUND OF THE INVENTION
This invention relates to a defrost system for various types of
refrigeration apparatus, the defrost system being operable in
response to the build-up of frost on the cooling unit (e.g., the
evaporator) of the refrigeration apparatus.
The accumulation or build-up of frost on the evaporator of a
refrigerator or other refrigeration unit has long been a problem.
Various automatic defrosting systems have been used and are well
known in the art. Typically, an automatic defrost system is
controlled by a timer which initiates operation of the defrost
system at certain times of the day or after the compressor has run
a predetermined length of time. The rate at which frost forms on
the evaporator is a function of the amount of water vapor in the
air passing over the evaporator, the greater the water content the
faster the frost accumulates. In a refrigerator, the amount of
water vapor within the air to be cooled depends a great deal on the
ambient conditions (i.e., room temperature and relative humidity)
outside the refrigerator because ambient air is introduced into the
refrigerator each time the door is opened and closed, and water
vapor sources (e.g., wet produce and open containers of liquids)
within the refrigerator. With time-controlled defrost systems and
with a slow build-up of frost, operation of the defrost system is
sometimes initiated before any significant amount of frost has
built up on the evaporator, thus resulting in a wastage of power to
defrost the refrigerator when it is not required and exposing the
items in the refrigerator to unnecessary defrost cycles. On the
other hand, under heavy frost conditions, excessive frost may build
up on the evaporator between the timed defrost cycles, thus
reducing the efficiency of the refrigerator, increasng the power
consumed thereby and warming foodstuff that should be kept cool,
resulting in shorter shelf-life for refrigerated foods and possible
contamination unknown to the user.
Another defrosting system is one in which the number of door
openings are counted and a defrosting cycle is initiated after a
selected number of openings occur. This arrangement is
disadvantageous in that an unused or little used refrigerator would
not be defrosted even though a substantial frost deposit has built
up. Also, mechanical counters are relatively unreliable in
continued use. Depressed temperature systems have also been
utilized where defrosting cycles are initiated when the evaporator
reaches a temperature much lower than its normal operating
temperature. This depressed evaporator temperature occurs after ice
forms on the evaporator, reducing its efficiency. Depressed
temperatures systems have not been too successful because the low
temperature varies from evaporator to evaporator due to production
tolerances. Good sensing of the depressed temperature has been
difficult due to inconsistency of heat transfer materials used
between the evaporator and the sensing control. Depressed
temperature systems have, as a rule, been more expensive than the
systems in current usage.
Other systems utilized have been restricted air-flow methods with
electronic sensors, but these are relatively expensive and
difficult to build in production. Fluidic systems initiating
defrost based on pressure changes in the refrigerating equipment
are also expensive.
SUMMARY OF THE INVENTION
Among the several objects of this invention may be noted the
provision of an automatic defrost system for refrigeration
apparatus (e.g., a refrigerator, a freezer, a refrigerated vending
machine, or an air conditioner) in which build-up of frost on the
evaporator of the refrigeration apparatus initiates a defrosting
cycle rather than having defrosting initiated by a clock or counter
mechanism; the provision of a demand defrost system which conserves
power and increases the operating efficiency of the refrigeration
apparatus by eliminating unnecessary defrost cycles and by keeping
the refrigeration apparatus free of excessive frost; the provision
of such a defrost system which maintains better temperature control
in the refrigeration system and which does not expose refrigerated
or frozen items to unnecessary defrost cycles; the provision of
defrost systems of the class described which permit a fast cool
down of warm foods, fast freezing of foods and increased ice
production; the provision of such a defrost system which is
relatively simple and of economical construction and which will
reliably operate regardless of ambient climatic conditions. Other
objects and features will be in part apparent and in part pointed
out hereinafter.
Briefly, an automatic defrosting control system of this invention
comprises means for causing defrosting of the refrigeration system
cooling means, a thermostat and a thermal time-delay relay. The
thermostat is positioned adjacent and in heat-exchange relation
with both the defrosting and cooling means and is connected in a
control circuit. The thermostat has a first switching position for
terminating energization of the defrosting means and a second
switching position for enabling operation thereof. It switches from
its first and its second position in response to its temperature
falling to a lower predetermined level and switches to its first
position in response to its temperature rising to a higher
predetermined level. The thermal time-delay relay if positioned in
heat-exchange relation with the cooling means and is also connected
in the control circuit. The relay has a first switching position
for permitting operation of the cooling means and a second
switching position for energizing the defrosting means and
preventing operation of the cooling means. The relay switches from
its first position to its second position upon reaching a given
temperature and switches from its second to its first position upon
reaching a different preselected temperature. The thermostatic
means responsive to the zone temperature periodically energizes the
cooling means to cycle between an "on" mode and an "off" mode to
maintain the zone substantially at the preselected temperature.
Also provided are means responsive to the duration of one of said
modes to supply heat to the relay whereby upon a sufficient
accretion of frost forming on the cooling means the increased
duration of the "on" mode will cause the temperature of the relay
to reach its given temperature and switch to its second position
and will cool the thermostat to cause its temperature to fall below
its lower predetermined level and switch to its second position
thereby energizing the defrosting means.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a view in section of refrigeration apparatus employing a
defrost system of this invention and illustrating the normal flow
of air therethrough when the refrigeration apparatus is in
operation;
FIG. 2 is a circuit diagram of a defrost system of this
invention;
FIG. 3 is a view, partially in section, of a thermal time-delay
relay utilized in a defrost system of this invention; and
FIG. 4 is a graphical representation of the temperatures of various
components of the refrigeration system, the thermostat and the
relay during operation beginning with a frost-free condition after
a defrost period, through normal operation and frost accumulation
to a point where the frost deposit is substantial enough to
initiate defrosting.
Corresponding reference characters indicate corresponding parts
throughout the several views of the drawings.
DESCRIPTION OF A PREFERRED EMBODIMENT
Referring now to the drawings, a defrost system of this invention,
as indicated generally at 1, is shown installed in a conventional
two-door refrigerator-freezer 3. The refrigerator-freezer includes
a cabinet 5 having a top 7, side walls 9, a back wall 11, a bottom
wall (not shown) and a partition 13 dividing the interior of the
cabinet and defining a freezer compartment 15 and a food
compartment 16, these compartments constituting refrigerated zones.
A freezer door 17 and refrigerator door 19 close the front of the
cabinet. The refrigerator includes a conventional refrigeration
system including a compressor driven by an electric compressor
motor C (see FIGS. 3 and 5-7), a condenser (now shown) and a
cooling unit or evaporator generally indicated at 23. The
evaporator includes a plurality of refrigerant lines 25
constituting a coil, this coil being subject to frost build-up. A
flow path generally indicated at 27 provides for the intake of air
from both the freezer and food compartments, for the passage of
this air over the evaporator for absorbing heat from the air and
thus chilling the air, and for the discharge of the chilled air
into the refrigerated compartments or zones. A blower or fan 29 is
provided for forcing air through the flow path. While the defrost
system of this invention is depicted as installed in a
two-compartment refrigerator-freezer, it will be understood that it
may be installed in other refrigeration apparatus, such as a
single-compartment refrigerator, a freezer, a refrigerated vending
machine, or an air conditioner.
More particularly, flow path 27 is, in part, defined by partition
13 and by a horizontal panel 31 in freezer compartment 15 spaced
above the partition and thus forming a main passage 33 between the
horizontal panel and the partition. An opening 35 is provided in
partition 13 for the intake of air into the passage from food
compartment 16 and an opening 37 is provided in panel 31 for the
intake of air from the freezer compartment. Evaporator 23 is
located within passage 33 for chilling air from the food and
freezer compartments as it passes thereover. An inner vertical
panel 39 is spaced from back wall 11, thereby to provide a return
or outlet passage 41 for the discharge of chilled air into the food
compartment via an outlet 43. A vertical wall 45 extends up from
panel 31 and a fan shroud 47 is disposed between vertical wall 45
and panel 39, thereby to define a fan intake chamber 49 and a
discharge chamber 51, with the upper end of the fan intake chamber
being closed by a cap 53. An opening 55 in panel 31 provides
communication between main passage 33 and the fan inlet chamber. A
baffle 57 directs and divides the chilled air discharged from the
fan into outlet passage 41 for discharge into the food compartment
and into freezer compartment 15 via openings 58 and 59.
The defrost system 1 of this invention comprises a defrost
termination thermostat T1 and thermal time-delay relay TR which
serves as a defrost initiation thermostat, both of which are
connected in a circuit for controlling energization of a heater DH
for melting and removal of frost from evaporator 23 upon a
predetermined build-up of frost thereon. Thermostat T1 is a
conventional temperature-responsive wide-differential switch, such
as any of the widely used bimetallic disk-actuated types in which
the contacts are abruptly moved from one switching position to the
other when heated and cooled. Relay TR is also a wide-differential
type switching unit, again preferably a bimetallic disk-actuated
type.
T1 is mounted on or adjacent evaporator 23 preferably on the most
frost-prone portion thereof. It is also in close heat-exchange
relationship with defroster heater DH. Thermal relay TR is
preferably mounted out of the air flow across the evaporator to
minimize convection cooling and may be conveniently mounted within
an enclosed well in the side wall of the refrigerator.
Referring now to FIG. 2, thermostat T1 and relay TR are
schematically shown connected in a control circuit for selectively
energizing defrost heater DH and periodically actuating compressor
motor C in response to the temperature sensed by a thermostat T3, a
conventional adjustable cold control typically positioned in
refrigerator food compartment 16. Included in the control circuit
is a heater comprising a resistor H together with a second heater
R, also constituted by a resistor. Resistor H is preferably a
self-regulating, self-heating positive temperature coefficient
resistor which has a relatively low resistance when deenergized at
ambient temperature but which will increase in resistance abruptly
as its temperature rises above a given level. Heaters H and R are
positioned in close heat-exchange relation with TR (as indicated by
the dashed lines therebetween indicating a thermal link) and are
preferably enclosed within the housing thereof.
FIG. 3 illustrates the physical arrangement of thermal relay TR
with the single-pole double-throw switching components and the
thermal-actuating disk being enclosed within a housing 61. PTC
heater H is secured to one surface of a heat sink 63 of metal such
as copper, which acts as a thermal capacitor, and heater resistor R
is positioned in sink 63. Sink 63 and housing 61 are in facial
contact for efficient heat transfer therebetween. An insulating
case 65 of phenolic resin or the like encloses the componentS of TR
and the entire package is surrounded by a good thermal insulation
material 67 such as foamed polyurethane.
T1 will move from a first (solid-line) switching position, in which
operation of the defrost heater DH is terminated, to its second
(broken-line) position when its temperature falls to a level of
about 0.degree.-10.degree.F., for example, and will not switch back
to its first position until its temperature rises to say
65.degree.F. Similarly TR will move from its first (solid-line)
switching position, in which the compressor may be energized, to
its second (broken-line) position in which the heater DH may be
energized only when its temperature falls to a low level in the
order of 10.degree.-20.degree.F., remaining there until its
temperature rises to a high level, e.g., 70.degree.-100.degree.F.,
whereupon it abruptly reverts to its first position.
As illustrated in FIG. 2, and with thermostat T1 and relay T2 both
in their first or solid-line positions, the defrost heater DH is
disabled and compressor C will be periodically energized each time
cold control thermostat T3 moves to its solid-line position in
response to the food compartment's temperature rising above a
selected control temperature level. Resistor heater H will be
energized to heat TR's thermal actuator during compressor "off"
modes when T3 is open and will be deenergized during compressor
"on" modes by the shunting action of TR and T3, when closed. R,
which is arelatively high-resistance low-wattage (e.g., 2 watts)
heater will also supply heat to TR as R will be directly connected
across an a.c. power source indicated at L1, L2 when T1 is in its
solid-line position. This is the normal operational mode of the
circuit between termination of one defrost mode and the initiation
of the next.
FIG. 4 illustrates the temperatures of the various system
components, each noted parenthetically in relation to its
respective temperature curve, beginning with the termination of a
defrost mode. At that moment T3 will be closed, TR will be in its
second or broken-line position, and T1 will have just switched to
its solid-line position (thereby disabling heater DH). However, as
R was deenergized during defrosting and it will require a finite
time for TR to be heated by R and H to its high actuation
temperature a few minutes are allowed for draining melted frost
("soaking") from the evaporator before TR is heated to a high
enough temperature to move to its first (solid-line) position and
permit reenergization etc. The evaporator tubing 25, T1, food
compartment 16 and freezer compartment 15 will all be at their
maximum temperatures to which they were heated by DH. TR's
temperature will continue to rise briefly until it reaches its high
level whereupon it switches to its solid-line position and permits
reenergization of compressor C. All components then cool, including
TR, because heater H will be deenergized during the long initial
pull-down compressor "on" mode. However, heater R will prevent TR
from cooling to its low temperature during this pull-down. Even if
T1 is cooled sufficiently during such pull-down so that it moves to
its second (dashed-line) position thereby deenergizing R, TR will
not cool sufficiently during initial pull-down or immediately
thereafter to reinitiate defrosting. The normal operational mode
described above will continue with each indicated "on" mode of the
compressor causing the illustrated temperature decreases in coils
25 and each "off" mode energizing heater H to increase or ratchet
it temperature upwardly.
As normal operational mode continues and frost accumulates on the
evaporator coils, a cooling of T1 occurs until it will reach its
lower temperature, e.g. 20.degree.F., and switch to its second
(broken-line) position. However, while this enables operation of
heater DH and deenergizes heater R, energization of DH will not
occur as TR remains in its first (solid-line) position with its
temperature still above its lower actuation temperature. However,
as frost accumulates the cooling efficiency drops and in order to
maintain the preselected zone temperatures the durations of the
"on" compressor mode continue to increase while the "off" mode
periods decrease. Thus, heater H will be energized shorter
increments of time so that gradually, as indicated in FIG. 4, the
temperature of TR will fall until its temperature drops to its
lower actuation level of 10.degree.-20.degree.F. as indicated at X.
TR will then switch to its second (broken-line) position to
energize heater DH thereby initiating a defrost cycle. It should be
understood that the curves of FIG. 4 are merely representative or
illustrative and that many "on" and "off" cycles of the compressor
would take place between a termination of one defrost mode and the
initiation of the next one. During defrosting, heater H will heat
TR but without the additional heat supplied by R, which serves as a
lock-out heater during initial pull-down, TR will not reactuate to
its solid-line position.
During the defrost mode, T3 continues to remain in its closed
position and TR in its broken-line position. After the accretion of
frost is melted by DH, the temperature of the evaporator and T1
will rise until the temperature of the latter increases to
65.degree.F. This termination thermostat, which also provides a
safety function inpreventing overheating of the unit in case of a
component or circuitry fault or failure, will then switch to its
first or solid-line position thereby completing one full cycle of
operation of the automatic defrosting system of this embodiment of
the invention.
It will be noted that the particular switching temperatures
referred to above are merely illustrative and they may be varied
widely within broad limits. It will be understood that the wattage,
type and placement of optional resistor heaters R and H may be
changed to vary the temperature gradients. Typically the run or
"on" modes of the compressor will increase from say 18-20 minutes,
with a relatively frost-free evaporator, to 40-45 minutes when the
evaporator becomes frosted to the extent that it requires
defrosting. TR will have a cooling time constant that generally
matches that of the compressor run time, so that under normal
operation its temperature will cycle as indicated in FIG. 4, but
with the increased length of the run cycle caused by frosting and
with both heaters H and R deenergized TR will cool in about 45
minutes so as to enter the defrost initiation "window" and initiate
defrosting. This system is, in effect, a thermal analog timer that
montors run time which has a close relationship to the cooling
efficiency of the refrigerator. And this efficiency in turn is
closely related to the accumulation of frost on the evaporator
which causes long run periods. Thus, the demand defrost thermal
analog system of this invention integrates freezer temperature and
the ratio of compressor "on-off" time to initiate defrosting when
the refrigeration system begins to lose its heat-exchange
efficiency, and it does so economically by the use of a
thermostatic switch and a thermal time-delay relay.
In view of the above, it will be seen that the several objects of
the invention are achieved and other advantageous results
attained.
As various changes could be made in the above constructions without
departing from the scope of the invention, it is intended that all
matter contained in the above description or shown in the
accompanying drawings shall be interpreted as illustrative and not
in a limiting sense.
* * * * *