U.S. patent number 3,852,974 [Application Number 05/387,982] was granted by the patent office on 1974-12-10 for refrigeration system with subcooler.
Invention is credited to Ted R. Brown.
United States Patent |
3,852,974 |
Brown |
December 10, 1974 |
REFRIGERATION SYSTEM WITH SUBCOOLER
Abstract
A secondary or booster refrigeration system associated with a
primary refrigeration system so that high temperature liquid
refrigerant of the primary system is itself subcooled by
refrigeration after it has been condensed. The secondary or booster
refrigeration system is situated so that the evaporation coil is in
heat exchange relation with that portion of the primary
refrigeration circuit carrying the condensed liquid refrigerant.
Optionally, the secondary or booster refrigeration system may
itself be liquid subcooled by heat exchange with the suction line
of the primary refrigeration system. Operational control of the
secondary refrigeration system is achieved by means responsive to
the temperature and/or humidity in the space cooled by the primary
refrigeration system and/or the ambient temperature in the vicinity
of the condenser of the primary refrigeration system.
Inventors: |
Brown; Ted R. (Salt Lake City,
UT) |
Family
ID: |
26899578 |
Appl.
No.: |
05/387,982 |
Filed: |
August 13, 1973 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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204554 |
Dec 3, 1971 |
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Current U.S.
Class: |
62/79; 62/175;
62/335; 62/510 |
Current CPC
Class: |
F25B
7/00 (20130101); F25B 1/00 (20130101); F25B
40/00 (20130101) |
Current International
Class: |
F25B
7/00 (20060101); F25B 1/00 (20060101); F25B
40/00 (20060101); F25b 007/00 () |
Field of
Search: |
;62/335,79,175,196,332,333,510 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Attorney, Agent or Firm: Workman; H. Ross
Parent Case Text
This is a continuation-in-part of my copending application Ser. No.
204,554, filed Dec. 3, 1971, now abandoned.
Claims
What is claimed and desired to be secured by United States Letters
Patent is:
1. A method of modifying an existing refrigeration system to
increase the refrigeration capacity thereof, the existing system
comprising a compressor, condensor and evaporator, the evaporator
comprising an expansion device and acting to cool a conditioned
space, comprising the steps of:
providing a secondary refrigeration system;
placing the evaporation coil of the secondary refrigeration circuit
in heat exchange relationship with condensed liquid refrigerant of
the existing refrigeration system upstream of the existing system
evaporator expansion device;
monitoring temperature in at least one of (1) the existing system
conditioned space and (2) the existing condenser environment;
and
initiating the secondary refrigeration system when the monitored
temperature reaches a predetermined upper limit to boost the
capacity of the existing system to reduce the temperature in the
conditioned space.
2. A method of modifying an existing refrigeration system as
defined in claim 1 wherein said monitoring step comprises sensing a
preselected upper temperature limit and thereafter generating an
initiating signal to automatically energize the secondary
refrigeration system.
3. A method of modifying an existing refrigeration system as
defined in claim 1 wherein said monitoring step comprises sensing a
preselected lower temperature limit and thereafter generating a
signal to automatically de-energize the secondary refrigeration
system.
4. A method as defined in claim 1 wherein said monitoring step
further comprises monitoring the humidity in the conditioned space
and where said initiating step comprises initiating the secondary
refrigeration system when the monitored humidity reaches a
predetermined upper limit.
5. A method of boosting the capacity of an existing refrigeration
system to cool a conditioned space without substantially altering
the components of the system, the steps of:
sensing at least one of the conditions of (1) temperature and (2)
humidity in the existing conditioned space; providing a secondary
compressor, secondary condenser, and a secondary closed loop
refrigerant path, each of which is completely independent of the
existing refrigeration system; situating a secondary evaporator
forming part of the secondary closed loop refrigerant path in heat
exchange relation with the portion of the existing system upstream
from the primary evaporator expansion device which carries only
liquified refrigerant at a temperature which is not more than the
condensing temperature of the existing system; and continuously
subcooling the existing liquified refrigerant with the secondary
evaporator substantially below its condensing temperature until the
condition sensed in the existing conditioned space reaches a
predetermined limit.
6. A refrigeration system for cooling a conditioned space
comprising a primary refrigeration system comprising a primary
compressor, primary condenser, and primary evaporation coil and
associated expansion device located in the conditioned space and
having a discrete body of refrigerant; and a secondary
refrigeration system comprising a secondary compressor, secondary
condenser, and secondary evaporation coil and having a second
discrete body of refrigerant, said evaporation coil of the
secondary refrigeration system being in heat exchange relation with
the portion of the primary refrigeration system between the
condenser and the expansion device of the evaporation coil; means
for monitoring temperature in at least one of (1) the primary
system conditioned space and (2) the primary condenser environment;
and means for initiating the secondary refrigeration system when
the monitored temperature reaches a predetermined upper limit.
7. A refrigeration system for cooling a conditioned space as
defined in claim 6 comprising means for sensing a preselected upper
temperature limit and thereafter generating an initiating signal to
automatically energize the secondary refrigeration system.
8. A refrigeration system for cooling a conditioned space as
defined in claim 6 comprising means for sensing a preselected lower
temperature limit and thereafter generating a signal to
automatically de-energize the secondary refrigeration system.
9. A refrigeration system for cooling a conditioned space
comprising a primary refrigeration system comprising a primary
compressor, primary condenser, and primary evaporation coil located
in the conditioned space and having a discrete body of refrigerant;
and a secondary refrigeration system comprising a secondary
compressor, secondary condenser, and secondary evaporation coil and
having a discrete body of refrigerant, said secondary evaporation
coil being in heat exchange relation with the portion of the
primary refrigeration system between the condenser and the
evaporation coil; means for monitoring humidity in the conditioned
space; and means for initiating the secondary refrigeration system
when the monitored humidity reaches a predetermined upper
limit.
10. A refrigeration system for cooling a conditioned space
comprising a primary refrigeration system as defined in claim 9
comprising means for monitoring humidity in the conditioned space
and means for de-energizing the secondary refrigeration system when
the monitored humidity reaches a predetermined lower limit.
11. A refrigeration system for cooling a conditioned space
comprising a primary refrigeration system comprising a primary
compressor, primary condenser, and primary evaporation coil located
in the conditioned space and having a discrete body of refrigerant;
and a secondary refrigeration system comprising a secondary
compressor, secondary condenser, and secondary evaporation coil and
having a second discrete body of refrigerant; said evaporation coil
of the secondary refrigeration system being in heat exchange
relation with the portion of the primary refrigeration system
between the condenser and the evaporation coil; means for
monitoring at least one of the conditions affecting the capacity of
the primary system, the conditions comprising humidity in the
primary conditioned space, temperature in the primary conditioned
space and temperature of the environment of the primary condenser;
means for initiating the secondary refrigeration system when the
monitored conditions reach the predetermined upper limit; and means
for terminating the operation of the secondary system when the
monitored conditions reach a predetermined lower limit.
Description
BACKGROUND
1. Field of the Invention
The present invention relates to refrigeration systems and more
particularly to improved refrigeration booster apparatus and method
for increasing the capacity of a refrigeration system.
2. The Prior Art
In refrigeration systems, gaseous refrigerant is compressed by a
compressor so as to maintain the refrigerant under substantial
pressure. This compression step results in raising the temperature
of the refrigerant. Thereafter, the compressed gaseous refrigerant
is condensed, usually by a heat exchange-type condenser, into
liquid form. The liquid refrigerant is then evaporated in an
evaporation coil. The evaporation is a cooling or refrigerating
step which results in decreasing the temperature around the
evaporation coil to a low point.
The temperature at which the gaseous refrigerant is condensed to
liquid is called the condensing temperature. The term "subcooling"
as used in this specification means any reduction of the
temperature of liquid refrigerant below its condensing temperature.
Historically, varieties of ways have been used to produce greater
refrigerating capacity in the evaporation coil. A common approach
is that of increasing the volume of refrigerant to be handled by
the refrigeration system. For example, the compressor for the
refrigeration system should have a capacity of about one-half to
ten horsepower per ton (12,000 BTUs per hour heat) depending upon
how low a temperature is desired in the evaporating coil. If the
evaporating coil is operating at, for example, -20.degree.F and it
is desired to reduce the temperature in the evaporating coil to
-40.degree.F, normally the compressor is replaced by a larger
compressor or a compound compressor system which is connected in
series so that the compression capacity is substantially increased.
It should be observed that the capacity of the compressors must be
increased by as much as 50 percent to reduce the temperature in the
evaporating coil the addition 20.degree. from -20.degree.F to
-40.degree.F because of the difficulty of removing heat from an
already low temperature site.
Increasing the compression capacity and refrigerant volume of the
refrigeration system has some distinct disadvantages. For example,
the costs involved with purchasing compressors having 50 percent
greater capacity or in acquiring another compressor system and the
attendant increased refrigeration lines, power supplies and the
like to handle the greater refrigerant volume makes this method
extremely expensive. Moreover, if it is desired to increase the
capacity of an existing refrigeration system using prior art
techniques, all of the refrigeration lines in the system must be
replaced with larger lines so that the additional volume of
refrigerant can be accommodated or the efficiency of the system is
adversely affected.
The expense and inconvenience of this requirement can be best
illustrated by referring to the example of grocery store freezer
units which normally have the refrigeration lines buried in the
floor and traversing substantial distances to frozen food cases
located at various locations around the grocery store. When it is
desired to increase the refrigerating capacity of the system
servicing the freezer units, the floors must be broken up to expose
the refrigeration lines to accommodate replacement of the
refrigeration lines.
As an alternative to increasing the compression capacity and
refrigerant flow rate, several prior art techniques have improved
the efficiency of a refrigeration system by reducing the superheat
existing in the compressed gaseous refrigerant between the
compressor and the condenser. For example, see U.S. Pat. No.
2,960,837. This approach improves only the capacity of the
condenser.
Where cascade or large capacity refrigeration systems are used to
obtain low evaporation coil temperatures, it is also common to
endeavor to improve the efficiency of the refrigeration system by
reducing the condensing temperature of compressed gaseous
refrigerant to liquid refrigerant. Examples of this technique can
be found in U.S. Pat. Nos. 2,680,956 and 2,453,823. From the
mentioned patents and numerous other prior art sources, it is known
to be conventional to couple a refrigeration system with the
condenser of a second refrigeration system to improve the
condensation process.
Nevertheless, it is well-known that regardless of how low the
temperature is reduced in the condenser, the temperature of the
condensed liquid emerging from the condenser will always be
approximately the condensation temperature of the particular
refrigerant used. Accordingly, even though refrigeration systems
are used to reduce the temperature in the condenser, the condensed
liquid refrigerant will nevertheless emerge from the condenser at
approximately the condensing temperature of the refrigerant.
In previously known attempts to increase the capacity of
refrigeration systems, suction gas has been brought into heat
exchange with the condensed refrigerant for subcooling purposes.
While suction gas-liquid heat exchangers are frequently used, it is
well-known that they are limited in their subcooling ability to
about one-third of the temperature difference between the entering
liquid and the entering gas. Moreover, a pressure drop inevitably
results in the suction line because of the heat exchanger thereby
reducing the efficiency of the compressor.
A persistent problem in using conventional refrigeration circuits
for food storage and other temperature-sensitive units has been the
dehydration of food. It has been found that dehydration is greatest
when the difference between the temperature of the evaporation coil
and the air in the unit is large. One explanation for dehydration
in this circumstance is that moisture in the unit accumulates on
the coil as frost thereby continuously drawing moisture from the
food storage unit.
In climates where there are large temperature differences in summer
and winter, conventional refrigeration systems must have sufficient
capacity to operate at a desired low temperature even in the heat
of summer. Accordingly, when cold winter temperatures occur, the
conventional systems have excess capacity which, in addition to the
increased expense of operation and maintenance, undesirably creates
temperatures in the evaporation coil so low that dehydration
inevitably results.
In many instances, a refrigeration system is used principally to
maintain a desired low temperature with very little fluctuation in
the work load requirement placed upon it. With this knowledge, it
is possible to very closely design the refrigeration system thus
greatly reducing the equipment costs for such a system. However,
certain excessive load requirements may be placed upon the
refrigeration system and thus exceed the refrigeration system's
capacity for handling such a load requirement. An example of such
an unusual circumstance that may confront an existing refrigeration
system would be by placement of a large quantity of material
requiring cooling or very high ambient temperatures in the vicinity
of the condenser coils thus lowering the capacity of the
refrigeration system. It is, therefore, suggested that another
distinct advantage of this invention is that of modifying an
existing refrigeration system with a smaller, less expensive
refrigeration system which would be selectively controlled to act
as a booster for the existing refrigeration system. In this way, it
is possible to operate the existing or primary refrigeration system
as a temperature maintenance system but being able also to increase
the refrigeration capacity of the existing system.
High humidity conditions within the cooling chamber would cause
increased condensation or frost accumulation on the evaporator
coils and would place an increased work requirement on the existing
refrigeration system. A condition of high ambient temperature
coupled with a high relative humidity would create a demand upon
the capacity of the system.
However, continued operation of the secondary refrigeration system
under all circumstances would not only be unnecessary but wasteful.
For example, very low humidity conditions within the cooling
chamber result in excessive moisture being removed from the
products within the cooling chamber by condensation on very cold
evaporation coil surfaces thus causing undesirable dehydration
sometimes called freezer burn. Such a circumstance would arise, for
example, if there were a condition of low ambient temperatures
within the vicinity of a condenser coil thereby greatly increasing
the thermal capacity, hence the thermal efficiency of the entire
unit.
BRIEF SUMMARY AND OBJECTS OF THE INVENTION
It has been found according to the present invention that a high
temperature liquid line in a main refrigeration system can be
subcooled with a small auxiliary or booster refrigeration system to
increase the refrigeration effect of the existing volume of
refrigerant so that the capacity of the refrigeration system is
increased without increasing the volume of refrigerant handled by
the system. Because the booster system operates on the high
temperature liquid line, where temperature is most easily and
efficiently reduced, the heat in the high temperature liquid line
can be removed with a much smaller compressor capacity than would
be required if the main refrigeration system itself were enlarged
to produce the same increase in refrigerating effect. Accordingly,
when the subcoded liquid passes through the expansion valve into
the evaporating coil, surprising increases in refrigeration
capacity can be obtained without large, expensive compressors and
without replacing coolant lines. Moreover, the auxiliary system can
be selectively shut down without interference with the main system
so as to minimize dehydration of food, where desired.
Operational control of the secondary or booster refrigeration
system is achieved by monitoring preselected conditions affecting
the capacity of the primary refrigeration system and selectively
activating or deactivating the secondary refrigeration system in
response to these conditions.
It is, therefore, a primary object of the present invention to
provide an improved refrigeration system.
It is another primary object of the present invention to provide
novel method and apparatus for subcooling the high temperature
liquid line of a refrigeration system to achieve increased capacity
in the system.
One still further valuable object of the present invention is to
provide method and apparatus for improving the capacity of an
existing refrigeration system without at the same time requiring
replacement or supplementation of the compression capacity or
refrigerant volume circulated.
An even further object of this invention is to provide a primary
refrigeration system and a secondary refrigeration system acting in
liquid sub-cooling relation therewith wherein operation of the
secondary refrigeration system is determined by temperatures within
the conditioned space of the primary refrigeration system.
Another object of this invention is to provide a primary
refrigeration system and a secondary refrigeration system acting in
liquid sub-cooling relation therewith wherein operation of the
secondary refrigeration system is determined by ambient
temperatures in the vicinity of the condenser coils of the primary
refrigeration system.
Still another object of this invention is to provide a primary
refrigeration system and a secondary refrigeration system acting in
liquid sub-cooling relation therewith wherein operation of the
secondary refrigeration system is determined by humidity within the
conditioned space of the primary refrigeration system.
These and other objects and features of the present invention will
become more fully apparent from the following description and
appended claims taken in conjunction with the accompanying
drawing.
BRIEF DESCRIPTION OF THE DRAWING
The FIGURE is a schematic circuit diagram illustrating primary and
secondary refrigeration circuits in heat exchange one with another
according to the presently preferred embodiment of the
invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Reference is now made to the FIGURE illustrating presently
preferred embodiments of the invention. It is pointed out that all
temperatures used in this specification are for illustrative
purposes and are only representative of any of a wide range of
applicable temperatures, depending upon the size and refrigerant
capacity of the system and the type of refrigerant used.
A primary refrigeration circuit generally designated 10 includes a
refrigerant compressor 12 which may be of any suitable conventional
compressor having a desired capacity. Refrigerant vapor compressed
by the compressor 12 is transferred through conduit 14 at a
temperature of, for example, 200.degree.F to a condenser 16. Any
suitable type of condenser can be used which has the ability to
reduce the temperature of the refrigerant vapor to its condensing
temperature of, for example, 130.degree.F and to remove its heat of
vaporization sufficient to transform the high pressure refrigerant
vapor in conduit 14 to a liquid as the refrigerant emerges in line
18. Most commonly, condensers are of the heat-exchange variety
which use fluids, such as water or air, to remove heat energy from
the refrigerant in line 14 sufficiently to accommodate
condensation. However, if desired, the condenser 16 may also be
refrigeration cooled as, for example, illustrated and described in
U.S. Pat. No. 2,680,956.
The liquid refrigerant emerges from the condenser 16 in line 18 at,
for example, about 125.degree.F. Thereafter, the liquid refrigerant
is exposed to the evaporation coil 20 of the secondary
refrigeration system generally designated 22 for the purpose and in
a manner hereinafter more fully described.
Commonly, liquid refrigerant is conducted to a conventional heat
exchanger 26 disposed in heat exchange relation with suction line
28. The liquid refrigerant, emerging from the heat exchanger 26 is
subcooled by the heat exchange and then conducted to an expansion
valve 30. The liquid refrigerant is allowed to expand to vapor
through the expansion valve 30 into the evaporation coil 32.
Alternatively, other suitable liquid flow control devices could be
used in lieu of expansion valves. The vaporization of the liquid by
the expansion step and consequent absorption of its heat of
vaporization is the principal cooling step in the refrigeration
cycle and results in a substantial reduction of temperature in the
area surrounding the expansion coil 32. Significantly, the higher
the temperature of the liquid refrigerant at the expansion valve 30
the more pounds of refrigerant that must be vaporized to maintain
the evaporation coil 32 at, for example, -40.degree.F.
Accordingly, the location of the heat exchanger 26 on the suction
line 28 takes advantage of the low temperature of the vaporized
refrigerant existing in the suction line 28 to subcool the liquid
refrigerant with the vaporized refrigerant as it emerges from the
evaporating coil 32. Nevertheless, the use of the heat exchanger 26
is not essential in a refrigeration system nor is it essential in
the illustrated embodiment of this invention. Alternatively, the
line 18 could be connected directly to the expansion valve 30.
The expansion valve 30 is thermostatically operated by a thermal
control element 34 in a conventional manner. The thermal control
element 34 is sensitive to the temperature in the suction line and
the pressure of the system in the evaporator coil 32. Thermal
control element 34 controls the opening in the expansion valve 30
so as to determine the admission of refrigerant to the evaporation
coil 32 and simultaneously preclude passage of liquid refrigerant
to compressor 12 where it could cause considerable damage.
The vaporized refrigerant in the suction line 28 absorbs heat from
liquid refrigerant in line 18 by the heat exchange relation in heat
exchanger 26 and is thereafter returned to the intake or suction
port of the compressor 12. The description of the foregoing primary
refrigeration circuit relates to conventional refrigeration
systems, except that portion affected by the secondary
refrigeration circuit 22, which will now be more fully
described.
A compressor 40 compresses refrigerant which is thereafter
conducted in conduit 42 to a conventional condenser 44. The
condenser 44 may be similar to condenser 16, if desired.
Refrigerant emerging from the condenser 44 is in liquid form and
may be further cooled by contact with suction line 28. The liquid
subcooling is easily accomplished by conducting the condensed
liquid refrigerant from line 42 to a heat exchanger 60, situated at
suction line 28. The liquid is subcooled by the suction gas which
is at about -10.degree.F. The subcooled liquid is then passed to
the expansion valve 48. This technique advantageously subcools the
liquid from, for example, about 125.degree.F to 80.degree.F. Heat
exchanger 60 is optional and the liquid refrigerant from the
secondary condenser 44 could be passed directly into expansion
valve 48. Preferably, evaporation coil 20 is situated in heat
exchange relation with the line 18 of the refrigeration circuit 10.
Alternatively, the evaporation coil 20 could be disposed in heat
exchange relation with line 29. The admission of the liquid
refrigerant through the expansion valve 48 to the evaporation coil
20 is determined by the thermal control element 50. Thermal control
element 50 is situated adjacent the suction line 52 of compressor
40. It is clear that the refrigeration circuit 22 is closed with
respect to circuit 10 and different types of refrigerant can be
used for each circuit if desired.
The heat available in line 42 of the booster system 22 can be used,
if desired. For example, where used with frozen food fixtures,
moisture condensation, frost or uncomfortably cold surfaces for
contact can be prevented by using the heat in line 42. Thus, the
use of separate heaters and the like can be avoided. The use of
heat in this manner may, in some cases, eliminate the need for or
reduce the size of condenser 44.
Using a refrigerated subcooling booster 22 has been found to have
surprising and advantageous effects upon the refrigeration circuit
10. It has been found, for example, that heat can be removed from
line 18 or 29 with a far smaller compressor and lower horsepower
requirements than would be necessary to remove the same amount of
heat at the evaporation coil 32 by increasing the size of circuit
10. This is true because refrigeration systems are more efficient
at removing heat at the high temperature of about 125.degree.F than
at very low temperatures, for example, -40.degree.F. Accordingly,
when the liquid refrigerant in line 18 is subcooled by
refrigeration of circuit 22 to, for example, 30.degree.F, the
refrigerating effect of each pound of liquid refrigerant fed to the
evaporating coil 32 is substantially increased.
The advantage of using the secondary or booster refrigeration
system 22 will be more fully understood by continued reference to
the drawing. First, existing refrigeration systems can be improved
to have substantially greater capacity without acquiring larger
compressors or without implementing a cascade-type compressor
system. In addition, the refrigeration lines will not need to be
replaced to accommodate larger refrigerant flow rates. Moreover,
because it is much more efficient to remove heat in a high
temperature line than in a low temperature line, the horsepower
requirement to remove heat through system 22 is much lower than
that required to remove the same amount of heat by increasing the
size of system 10 alone. Thus, costs of improving the refrigeration
system are substantially reduced.
One advantage of the above-described invention is in making it
possible for one to adjust the refrigeration system to balance the
coil-ambient temperature and to compensate for difference in
seasonal temperatures in which the system operates. Thus, in
geographic areas where a wide range of temperatures is encountered
during the year, the sub-cooling booster may be selectively
switched on during the periods when the ambient temperature
surrounding the main condenser 16 is relatively high such as during
the summer months. During winter months the booster system 22 may
be switched off, thereby conserving operational costs during the
period when the main system is more efficient.
Where a system is designed for dehumidified storage as required by
some products, the booster 22 can most efficiently facilitate that
design and provide a means of controlling the relative humidity by
cycling the booster system off to maintain a control point of
relative humidity. The humidity is reduced when the booster system
is on.
The conditions which affect the capacity of the primary system are
monitored with conventional monitoring devices including, for
example, thermostats, humidistats, thermometers, hygrometers and
the like (not shown). These sensing devices are preferably
connected to a suitable control terminal 62. The operational state
of the secondary refrigeration system 22 is desirably controlled
through control terminal 62.
In operation, the secondary system 22 is off when the temperature
in the conditioned space is adequately maintained by the primary
system. However, when the temperature in the conditioned space is
raised significantly, the temperature change will be sensed and
indicated at the control terminal. The secondary system is then
actuated to boost the capacity of the primary system. Similarly,
when the capacity of the primary system is reduced due to high
ambient temperatures at the primary condenser, that condition
appears at the control terminal and the secondary system is
energized. Moreover, the operating costs for removal of a given
quantity of heat is less with both the primary and secondary
systems operating than normally incurred by a single system having
the same capacity. Thus, this embodiment of the invention is
desirable whenever control of humidity within the space is
desirable.
In the event the humidity in the conditioned space is reduced to a
detrimental level, operation of the secondary system will be
terminated to avoid dehydration. Under some circumstances, the
existence of low humidity and need for increased capacity in the
primary system may require a priority determination as to whether
the humidity or temperature sensors control the operation of the
secondary system 22. The determination of priority will likely turn
on the nature of goods in the conditioned space. Under most
circumstances, temperature should control and the effect of the
humidity monitor is made subservient to the temperature monitors
according to techniques well-known in the art. However, where
humidity considerations are of primary concern, temperature
conditions can be made subservient.
The invention may be embodied in other specific forms without
departing from its spirit or essential characteristics. The
described embodiment is to be considered in all respects only as
illustrative and not restrictive and the scope of the invention is,
therefore, indicated by the appended claims rather than by the
foregoing description. All changes which come within the meaning
and range of equivalency of the claims are to be embraced within
their scope.
* * * * *