Abstrict A dehumidifier unit for pre-conditioning air delivered to a multiplicity
of separate refrigeration air conditioner units and especially ductless
systems where the compressor-condenser unit is separate from the
fan-coil unit, and assisted by heat pipe transfer of heat from air
dehumidified through a desiccant wheel and by heat of compression
from the condenser of one compressor-condenser unit, and with a
heater to maintain the temperature of regeneration air through the
wheel, one dehumidifier unit pre-conditioning air for a multiplicity
of refrigeration air conditioners or fan-coil units.
Claims I claim:
1. A convertible desiccant assisted air pre-conditioner for implemented
use to dehumidify an air column delivered into an air conditioned
space, and including;
a first ducting means dedicated to dehumidification of incoming
air at an intake end and delivering supply air at a discharge end
for conditioning said air conditioned space,
a second ducting means dedicated to desiccant regeneration by means
of return air from said air conditioned space,
there being at least one air flow control means at an intake end
of the second ducting means,
a third ducting means for receiving return air at an intake end
and delivering exhaust air at a discharge end,
there being one air flow control means space at the intake end
of the third ducting means and at least one air flow control means
space at the discharge end of the third ducting means,
a coupler means duct open between the at least one air flow control
means at an intake end of the second ducting means and said one
flow control means space at the intake end of the third ducting
means,
desiccant dehumidifying means exposed to an air column flowing
through the first ducting means for dehumidification and exposed
to an air column flowing through the second ducting means for regeneration
of weakened desiccant,
heater means for tempering the air column to a regenerating temperature
through the second ducting means,
and heat transfer means exposed to air columns flowing through
each of said first and third ducting means.
2. The desiccant assisted air pre-conditioner as set forth in claim
1 wherein useful implementation is by means of a flow splitter
member fixed in said one flow control means space at the intake
end of the third ducting means and splitting intake air between
the third ducting means and said coupler ducting means, and a corner
member fixed in said at least one flow control means space at the
intake end of the second ducting means and turning a split off portion
of the air flow through the second ducting means and through the
heating means and the desiccant dehumidifying means exposed therein
and passing a portion thereof through the third ducting means and
through the heat transfer means exposed therein, whereby dehumidified
air flows from the discharge end of the first ducting means at reduced
temperature assisted by the transfer of heat of absorption to air
flow exhausted from the discharge end of the third ducting means,
and weakened desiccant regenerated by means of the heated air column
flowing through the dehumidifier means exposed in the second ducting
means.
3. The desiccant assisted air pre-conditioner as set forth in claim
1 wherein the desiccant dehumidifying means is of wheel configuration
having a dehumidifying segment exposed into the air column in the
first ducting means and having a regenerating segment exposed into
the air column in the second ducting means, and with motor means
for revolving the wheel.
4. The desiccant assisted air pre-conditioner as set forth in claim
1 wherein the heat transfer means is comprised of at least one
heat pipe having a hot end exposed in the first ducting means downstream
of the dehumidifying means for absorbing heat, and having a cold
end exposed in the third ducting means for dissipating said heat.
5. The desiccant assisted air pre-conditioner as set forth in claim
4 there being an air flow control means space intermediate the
intake and discharge ends of the third ducting means and upstream
of the heat transfer means exposed therein, and wherein an evaporative
cooler means is fixed in said last mentioned control means space
for assisting the cold end of the heat pipe to dissipate heat.
6. The desiccant assisted air pre-conditioner as set forth in claim
2 wherein the desiccant dehumidifying means is of wheel configuration
having a dehumifying segment exposed into the air column in the
first ducting means and having a regenerating segment exposed into
the air column in the second ducting means, and with motor means
for revolving the same.
7. The desiccant assisted air pre-conditioner as set forth in claim
2 wherein the heat transfer means is comprised of at least one
heat pipe having a hot end exposed in the first ducting means downstream
of the dehumidifier means for absorbing heat, and having a cold
end exposed in the third ducting means for dissipating heat.
8. The desiccant assisted air pre-conditioner as set forth in claim
7 there being an air flow control means space intermediate the
intake and discharge ends of the third ducting means and upstream
of the heat transfer means exposed therein, and wherein an evaporative
cooler means is fixed in said last mentioned control means space
for assisting the cold end of the heat pipe to dissipate heat.
9. The desiccant assisted air pre-conditioner as set forth in claim
1 wherein a first fan means at the intake end of the first ducting
means transports conditioned air therethrough, and a second fan
means at the intake end of the third ducting means transports regeneration
air therethrough.
10. The desiccant assisted air pre-conditioner as set forth in
claim 2 wherein a first fan means at the intake end of the first
ducting means transports conditioned air therethrough, and a second
fan means at the intake end of the third ducting means transports
regeneration air therethrough.
11. The desiccant assisted air pre-conditioner as set forth in
claim 2 and in combination with at least one refrigeration air conditioner
system comprised of a refrigerant compressor, a refrigerant condenser
for removal of heat of compression, a thermal expansion valve and
refrigeration coil with refrigerant return to the compressor, wherein
the second ducting means of the pre-conditioner has a supplemental
heat section in which the said heating means is exposed together
with a condenser section comprised of a substantial portion of the
said refrigerant condenser, whereby refrigerant heat of compression
is applied to the regeneration air and supplemented by the heating
means for maintaining a regeneration temperature, and reducing energy
to cool applied by the refrigeration air conditioner.
12. The desiccant assisted air pre-conditioner as set forth in
claim 3 and in combination with at least one refrigeration air conditioner
system comprised of a refrigerant compressor, a refrigerant condenser
for removal of heat of compression, a thermal expansion valve and
refrigeration coil with refrigerant return to the compressor, wherein
the second ducting means of the pre-conditioner has a supplemental
heat section in which the said heating means is exposed together
with a condenser section comprised of a substantial portion of the
said refrigerant condenser, whereby refrigerant heat of compression
is applied to the regeneration air and supplemented by the heating
means for maintaining a regeneration temperature, and reducing energy
to cool applied by the refrigeration air conditioner.
13. The desiccant assisted air pre-conditioner as set forth in
claim 4 and in combination with at least one refrigeration air conditioner
system comprised of a refrigerant compressor, a refrigerant condenser
for removal of heat of compression, a thermal expansion valve and
refrigeration coil with refrigerant return to the compressor, wherein
the second ducting means of the pre-conditioner has a supplemental
heat section in which the said heating means is exposed together
with a condenser section comprised of a substantial portion of the
said refrigerant condenser, whereby refrigerant heat of compression
is applied to the regeneration air and supplemented by the heating
means for maintaining a regeneration temperature, and reducing energy
to cool applied by the refrigeration air conditioner.
14. The desiccant assisted air pre-conditioner as set forth in
claim 5 and in combination with at least one refrigeration air conditioner
system comprised of a refrigerant compressor, a refrigerant condenser
for removal of heat of compression, a thermal expansion valve and
refrigeration coil with refrigerant return to the compressor, wherein
the second ducting means of the pre-conditioner has as a supplemental
heat section in which the said heating means is exposed together
with a condenser section comprised of a substantial portion of the
said refrigerant condenser, whereby refrigerant heat of compression
is applied to the regeneration air and supplemented by the heating
means for maintaining a regeneration temperature, and reducing energy
to cool applied by the refrigeration air conditioner.
15. The desiccant assisted air pre-conditioner as set forth in
claim 2 and in combination with at least one refrigeration air conditioner
system comprised of a refrigerant compressor, a refrigerant condenser
for removal of heat of compression, a thermal expansion valve and
refrigeration coil with refrigerant return to the compressor, wherein
the second ducting means of the pre-conditioner has a supplemental
heat section in which the said heating means is exposed together
with a condenser section comprised of a substantial portion of the
condenser circuit in parallel with said refrigerant condenser, whereby
refrigerant heat of compression is applied to the regeneration air
and supplemented by the heating means for maintaining a regeneration
temperature, and reducing energy to cool applied by the refrigeration
air conditioner.
16. The desiccant assisted air pre-conditioner as set forth in
claim 2 and in combination with at least one refrigeration air
conditioner system comprised of a refrigeration compressor, a refrigerant
condenser for removal of heat of compression, a thermal expansion
valve and refrigeration coil with refrigerant return to the compressor,
wherein the second ducting means of the pre-conditioner has a supplemental
heat section in which the said heating means is exposed together
with a condenser section comprised of a substantial portion of the
condenser circuit in series with said refrigerant condenser, whereby
refrigerant heat of compression is applied to the regeneration air
and supplemented by the heating means for maintaining a regeneration
temperature, and reducing energy to cool applied by the refrigeration
air conditioner.
17. The desiccant assisted air pre-conditioner as set forth in
claim 1 wherein useful implementation is by means of a closure
member fixed in said one control means space at the intake end of
the third ducting means and closing the coupler duct means thereto,
a closure member fixed in said at least one flow control means space
at the discharge end of the second ducting means space and closing
the coupler duct means thereto and leaving an open control means
space, a closure member fixed in said at least one control means
space at the discharge end of the third ducting means and leaving
an open flow control means space, there being a fourth ducting means
attached to the second ducting means and in open communication between
the open flow control space at the discharge end of the third ducting
means and the open flow control means space at the intake end of
the second ducting means, whereby dehumidified air flows from the
discharge end of the first ducting means at reduced temperature
assisted by the transfer of heat of absorption to the column of
air through the fourth ducting means as regeneration air through
the second ducting means and through the dehumidifying means exposed
therein for regenerating weakened desiccant.
18. The desiccant assisted air pre-conditioner and refrigeration
air conditioner combination as set forth in claim 17 wherein the
desiccant dehumidifying means is of wheel configuration having a
dehumidifying segment exposed into the air column in the first ducting
means and having a regenerating segment exposed into the air column
in the second ducting means, and with motor means for revolving
the same.
19. The desiccant assisted air pre-conditioner and refrigeration
air conditioner combination as set forth in claim 17 wherein the
heat transfer means is comprised of at least one heat pipe having
a hot end exposed in the first ducting means downstream of the dehumidifying
means for absorbing heat, and having a cold end exposed in the third
ducting means for dissipating said heat.
20. The desiccant assisted air pre-conditioner and refrigeration
air conditioner combination as set forth in claim 19 there being
an air flow control means space intermediate the intake and discharge
ends of the third ducting means and upstream of the heat means exposed
therein, and wherein an evaporative cooler means is fixed in said
last mentioned control means space for assisting the cold end of
the heat pipe to dissipate heat.
21. The desiccant assisted air pre-conditioner and refrigeration
air conditioner combination as set forth in claim 17 wherein a
first fan means at the intake end of the first ducting means transports
conditioned air therethrough, and a second fan means at the intake
end of the third ducting means transports regeneration air therethrough.
22. The desiccant assisted air pre-conditioner and refrigeration
air conditioner combination as set forth in claim 17 wherein the
refrigeration air conditioner is comprised of a refrigerant compressor,
a refrigerant condenser for removal of heat of compression, a thermal
expansion valve and refrigeration coil with refrigerant return to
the compressor, wherein the second ducting means of the pre-conditioner
has a supplemental heat section in which the said heating means
is exposed together with a condenser section comprised of a substantial
portion of the said refrigerant condenser, whereby refrigerant heat
of compression is applied to the regeneration air and supplemented
by the heating means for maintaining a regeneration temperature,
and reducing energy to cool applied by the refrigeration compressor-condenser
unit.
23. The desiccant assisted air pre-conditioner and refrigeration
air conditioner combination as set forth in claim 17 wherein the
refrigeration air conditioner is comprised of a refrigerant compressor,
a refrigerant condenser for removal of heat of compression, a thermal
expansion valve and refrigeration coil with refrigerant return to
the compressor, wherein the second ducting means of the pre-conditioner
has a supplemental heat section in which the said heating means
is exposed together with a condenser section comprised of a substantial
portion of the condenser circuit in parallel with said refrigerant
condenser, whereby refrigerant heat of compression is applied to
the regeneration air and supplemented by the heating means for maintaining
a regeneration temperature, and reducing energy to cool applied
by the refrigeration air compressor-condenser unit.
24. The desiccant assisted air pre-conditioner and refrigeration
air conditioner combination as set forth in claim 17 wherein the
refrigeration air conditioner is comprised of a refrigerant compressor,
a refrigerant condenser for removal of heat of compression a thermal
expansion valve and refrigeration coil with refrigerant return to
the compressor, wherein the second ducting means of the pre-conditioner
has a supplemental heat section in which the said heating means
is exposed together with a condenser section comprised of a substantial
portion of the condenser circuit in series with said refrigerant
condenser, whereby refrigerant heat of compression is applied to
the regeneration air and supplemented by the heating means for maintaining
a regeneration temperature, and reducing energy to cool applied
by the refrigeration air compressor-condenser unit.
25. A desiccant assisted air pre-conditioner implemented to pre-condition
outside air delivered to a multiplicity of refrigeration air conditioner
units and each of which is comprised of a refrigerant compressor,
a refrigerant condenser for removal of heat of compression, a thermal
expansion valve and refrigeration coil with refrigerant return to
the compressor, the air pre-conditioner including;
a first ducting means dedicated to dehumidification of incoming
outside air with discharge ducting to each of said multiplicity
of refrigeration air conditioner units,
a second ducting means dedicated to desiccant regeneration by means
of return air therethrough to exhausting from the air space conditioned
by said multiplicity of refrigeration conditioner units,
a third ducting means for receiving said return air and delivering
it to said second ducting means,
a desiccant dehumidifying means exposed into the first ducting
means for dehumidifying the air flow therethrough and exposed into
the second ducting means for regeneration of weakened desiccant,
a heat transfer means exposed to the air flow from the dehumidifying
means exposed into said first ducting means to absorb heat and exposed
into the air flow through the third ducting means to dissipate heat
into the air flow therethrough,
a substantial portion of said refrigerant condenser of one of said
multiplicity of refrigeration air conditioner units being exposed
in the second ducting means for dissipating heat of compression
to the regeneration air flow therethrough,
and a heater means exposed in the second ducting means for supplementing
said heat transfer means heat dissipation and said heat of compression
condenser portion dissipation to maintain regeneration temperature.
26. A desiccant assisted air pre-conditioner implemented to pre-condition
outside air delivered to a multiplicity of refrigeration compressor
units and each of which is comprised of a refrigerant compressor,
a refrigerant condenser for removal of heat of compression for delivery
to separate fan-coil units comprised of a thermal expansion valve,
a refrigeration coil and ductless fan and with refrigerant return
to the compressor, the air pre-conditioner including;
a first ducting means dedicated to dehumidification of incoming
outside air with discharge ducting to each of said multiplicity
of fan-coil units,
a second ducting means dedicated to desiccant regeneration by means
of return air therethrough and to exhausting from the air space
conditioned by said multiplicity of fan-coil units,
a third ducting means for receiving said return air and delivering
it to said second ducting means,
a desiccant dehumidifying means exposed into the first ducting
means for dehumidifying the air flow therethrough and exposed into
the second ducting means for regeneration of weakened desiccant,
a heat transfer means exposed to the air flow from the dehumidifying
means exposed into said first ducting means to absorb heat and exposed
into the air flow through the third ducting means to dissipate heat
into the air flow therethrough,
a substantial portion of said refrigerant condenser of one of said
multiplicity of compressor units being exposed in the second ducting
means for dissipating heat of compression to the regeneration therethrough,
and heater means exposed in the second ducting means for supplementing
said heat transfer means heat dissipation and said heat of compression
condenser portion dissipation to maintain regeneration temperature.
Description PREFERRED EMBODIMENT
This invention relates to a versatile multi-use stand-alone dehumidifier
unit adapted to pre-condition air in conjunction with, but not necessarily
with refrigeration systems, whereby optimum humidity is attained
in differing climatic conditions, waste heat being used when available
for efficiency in the operation of both the dehumidification means
and the refrigeration air conditioning means when combined therewith.
Humidity has its effect upon building construction, as high humidity
reduces the presence of mold and mildew, and can be controlled to
levels which contribute to the elimination of bacteria propagating
environments, For example, refrigeration air conditioner systems
in humid environments are often inadequate with respect to acceptable
humidity control, with or without refrigeration incorporated therein.
And, in wet environments refrigeration air conditioner systems utilizing
refrigerant cooled air coils are often overtaxed and their efficiency
adversely affected. Humidity control becomes an important factor,
not only as related to human comfort, health and to structural deterioration
etc., but also as to adequacy of dehumidification and its efficient
application. Accordingly, it is a general object of this invention
to provide a versatile humidification controlling heat recovery
unit adaptable to efficient operation in diverse climatic conditions,
standing alone and/or in combination with air refrigeration systems.
A feature of this stand-alone air pre-conditioner unit when combined
with air conditioned refrigeration systems is increased efficiency
of the refrigeration system while recovering waste heat therefrom
that is advantageously employed in the efficient operation of said
stand-alone air pre-conditioner unit.
State of the art practice for smaller commercial, institutional
and industrial use buildings is to split the conventional package
air conditioning system into small separately functioning units,
with regard to the air handling, one section including circulating
fan, filter, expansion valve and coil, and known as a fan-coil unit,
and the other section involving the refrigeration machinery including
compressor, condenser, receiver and the fixed piping, and known
as the compressor unit. The condensers can be air cooled or water
cooled, this practice of separation being known in the industry
as "Ductless" or "Mini-Split" systems. And,
in carrying out this practice, the air handling fan-coil unit and
the compressor-condenser unit are separated, in order to facilitate
installation and maintenance thereof. Thus, the fan-coil unit is
readily adapted to optimum placement proximate to the conditioned
space, while the compressor-condenser unit is adapted to optimum
(remote) placement for noise abatement and servicing access. Accordingly,
it is an object of this invention to provide a dehumidifier/humidifier
with so-called Ductless or Mini-Split installations, and in the
form of stand-alone air pre-conditioner units. That is, the air
pre-conditioner unit or units disclosed herein is each a complete
dehumidifier that is convertible to various air conditioning forms.
Being "stand-alone" this pre-conditioner unit is operable
independently, or it is operable in combination with refrigeration
air conditioner systems. Characteristically, this stand-alone air
pre-conditioner is adapted to be converted in its air ducting and
in its heat source application, it being an object to provide internal
ducting modifications that are compatible with variations in the
application of outside air and exhaust air, as circumstances require
with regard to prevailing environmental conditions.
It is an object of this invention to provide a basic dehumidifier,
preferably of the desiccant type, wherein there are at least two
columns of air, a first column of air that is dehumidified, and
a second column of air for regeneration. Also, a third column of
air split off from incoming blower air for removal of heat and exhausted.
Accordingly, it is another object of this invention to provide said
basic unit with permanent ducting that is convertible to implement
usable combinations of said three columns of air. And, it is still
another object of this invention to provide selectively installed
partitions that convert said permanent ducting to the usable combination
of said three columns of air. In practice for example, efficient
and effective dehumidification in a hot dry climate will require
implementation of said third air column that directly exhausts heat
removed from the first mentioned column of dehumidified air, whereas
a wet humid climate will require utilization of said heat removal
in the aforesaid regeneration column of air. A feature is the permanent
unchanged ducting in this basic stand-alone pre-conditioner unit
that is converted by the selective use of partitions of special
configuration and each for a specific functional purpose, as shown
and hereinafter described.
The process of dehumidification with desiccant adds heat to the
column of air being treated, it being an object to remove this heat
before it reaches the refrigeration cooling coil, and for this purpose
a heat pipe is employed with its hot end in the dehumidified air
side of the desiccant, in this embodiment a desiccant wheel. The
cold side of the heat pipe is in the aforesaid second or third column
of air and the heat absorbed therefrom and exhausted. In accordance
with this invention, evaporative cooling of said second or third
column of air can precede the heat pipe adsorption of heat extracted
from the first column of supply air.
During a winter heating cycle, the desiccant wheel absorbs moisture
from exhaust air and humidifies outside incoming air, and the heat
pipe will automatically reverse its direction of heat flow and extracts
heat from exhaust air and using it to pre-heat incoming cold air.
The process of dehumidifying with desiccant requires the regeneration
or strengthening of the weakened moisture laden desiccant. This
process requires the application of heat to said second column of
regeneration air, heat being available from the heat pipe that transfers
heat from said first column of dehumidified air to said second column
of regeneration air (or the third air column) and/or from any supplementary
heat source. In carrying out this invention, there are two supplementary
heat sources, one a heater means per se, and the other a waste heat
transfer means from combined equipment. In practice, said heater
means is a direct gas fired heater or an electric heater, and said
waste heat transfer means is a condenser coil of a refrigeration
compressor-condenser unit used in combination with this or a number
of these stand-alone air pre-conditioner units. It is an object
of this invention to advantageously employ this waste heat for the
benefit of both the air pre-conditioner unit herein disclosed and
also the compressor-condenser unit from which the heat is taken.
That is, efficiency of both units is enhanced, utilizing condenser
coils in parallel and preferably in series, and one of which is
in the aforementioned second regeneration air column.
A primary objective of this invention is to provide an air pre-conditioner
unit that is convertible so as to have the capability of several
ducting configurations, to be employed as circumstances require.
Accordingly, there is a first ducting assigned solely to the aforesaid
first column of air that is dehumidified, there is a second ducting
for desiccant regeneration and exhausted, there is a third ducting
for utilizing and/or removal of heat from the dehumidified air column,
and there is a fourth ducting that is shared with the aforesaid
second and third ducting; the second ducting column solely for desiccant
regeneration, and the third column solely for removal of heat and
exhausted. In carrying out this invention, the above stated ducting
conversions are achieved by providing partitions applied to the
permanent duct structures, as will be described, to rout the air
columns as required. There are no partitions applied to the first
mentioned air column. However, partitions are applied to the second,
third and fourth mentioned ductings. The second and third mentioned
air column ductings are partitioned as shown in FIG. 10 so as to
implement split outside air flow continuity through the third mentioned
ducting to exhaust, and parallel flow through the second mentioned
ducting to exhaust, said split outside air rejoining for exhaust.
The same second and third mentioned air column ductings are partitioned
as shown in FIG. 11 so as to implement outside air flow continuity
through the third mentioned ducting, then through the fourth mentioned
ducting and then through the second mentioned ducting to exhaust.
The basic convertible air pre-conditioner unit is shown in FIG.
1 without the partitions, fourth duct and modules that are employed
to implement the operative configurations shown in FIGS. 10 and
11.
By using the condenser coils in parallel, the size of the refrigeration
unit or compressor unit condenser coil is substantially reduced,
which is a cost saving feature. And, by using the condenser coils
in series, the total refrigerant flow is diverted, first to be cooled
by the aforementioned second column of regeneration air for maximized
heat absorption and then to the compressor unit condenser coil of
substantially reduced and smaller size, whereby considerably less
energy is expended to complete the condensing-cooling process and
with a comensurate cost saving in the use of energy.
An object of this invention is to advantageously combine the instant
air pre-conditioner unit with refrigeration-condenser units that
supply usable refrigerant to fan-coil units. With the present invention,
efficiency of the compressor-condenser unit is increased while removing
waste heat of compression therefrom. Said waste heat is then supplemented
in the air pre-conditioner unit and used for regenerating the dilute
desiccant. A feature of this refrigerant circuit is the second condenser
in parallel or in series, the latter being preferred and having
the advantage of removing heat so that the compressor-condenser
unit operates more efficiently by rejecting heat at lower condenser
temperature and pressure, and with the result that a smaller condenser
coil can be used. This waste heat use circuit is applicable to both
conventional fan-coil and compressor units, and to separate min-split
units, as shown herein.
The air pre-conditioner unit is versatile in its application to
both old and new construction, with or without refrigeration air
conditioning, and with or without dehumidification, it being an
object of this invention to provide dehumidification where it is
desired or previously difficient, and in whatever climatic condition.
Return air from the air conditioned space together with a minimum
of outside air is pre-conditioned and a maximum of outside air is
returned through fan-coil refrigeration units. It is an object of
this invention to provide a pre-conditioner unit that coordinates
the air flow columns while dehumidifying the air delivered through
the fan-coil refrigeration units in the air conditioned space.
Another feature of this invention is the use of evaporative cooling
to improve the heat pipe function of removing heat from the first
mentioned ducting. This feature is implemented when relatively dry
outside or return air is available. An evaporation module is installed
as will be described, to close an access opening provided therefor.
SUMMARY OF THE INVENTION
The inventive concept herein disclosed provides a versatile air
pre-conditioner that is adapted to be implemented in various configurations
as a stand-alone unit, in that it is self sufficient, if need be,
to humidify or dehumidify incoming air. Outside air and/or return
air from conditioned space is processed, with or without refrigeration,
to be dehumidified in hot-wet climate, and humidified in cold-dry
climate conditions. The structural configuration of this air pre-conditioner
can vary widely, as to size, shape and disposition of the ducting
means therein, and characterized by two dedicated ducting means,
and at least one additional ducting means that processes waste heat
from the desiccant dehumification process employed therein, the
quantity of said waste heat being adequate but lacking in temperature.
Accordingly, a supplemental heater means is provided to furnish
the difference for effective regeneration of weakened desiccant.
The need for supplemental heat is greatly reduced when this air
pre-conditioner is combined with a refrigeration system wherein
substantial amount of heat is available from the waste heat of compression.
To this end, a maximum amount of heat is taken from the condenser
circuit of the refrigeration system, by placing a second condenser
coil in parallel or preferably in series therewith, the advantage
of which has been described.
A feature of this invention is the singular unit design that is
convertible to many installation requirements and situations, a
compact design without wasted space and utilized to best advantage
with energy savings by maximum use of waste heat from whatever heat
source and especially from the condenser circuit of the associated
refrigeration air conditioning system.
The foregoing and various other objects and features of this invention
will be apparent and fully understood from the following detailed
description of the typical preferred forms and applications thereof,
throughout which description reference is made to the accompanying
drawings.
THE DRAWINGS
FIG. 1 is a longitudinal side view of the basic multi-use air pre-conditioner
in its non implemented condition, this and the following drawing
figures being schematic.
FIGS. 2 3 and 4 are sectional views taken as indicated by lines
2--2 3--3 and 4--4 on FIG. 1.
FIG. 5 is a longitudinal side view of a duct (ducting means D)
that is adapted to the basic structure of FIG. 1 to rout regeneration
air as may be required.
FIGS. 6 and 7 are sectional views taken as indicated by lines 6--6
and 7--7 on FIG. 5 and similar to FIGS. 3 and 4 in that they include
the corresponding structure of FIG. 1.
FIG. 8 is a perspective fragmentary section of a heat pipe configuration
employed herein as the heat transfer means; and P FIG. 9 is an enlarged
fragmentary sectional view showing an improved finned heat pipe
and its internal heat flow.
FIGS. 10 and 11 are each longitudinal side views of the basic structure
of FIG. 1 illustrating the two conversions of this pre-conditioner
as they are implemented by the partitions, ducts, and modules applied
thereto.
FIG. 12 is an illustration of a desiccant wheel as it is used herein,
to show the movement and areas thereof applied to dehumification
and to regeneration (normal application).
FIG. 13 is a view of the pre-conditioner implemented as it is in
FIG. 10 showing it in working combination with a fan-coil compressor
package unit air conditioner, and with a second condenser coil in
parallel with the condenser coil of the compressor section of the
package unit.
FIG. 14 is an enlarged view of the evaporative cooler module as
it is shown employed in FIGS. 11 13 and 15.
FIG. 15 is a view of the pre-conditioner implemented as it is in
FIG. 11 showing it in working combination with a ductless or mini-split
combination of a fan unit and a compressor-condenser unit, and with
a second condenser coil in series with the condenser coil of the
latter unit thereof.
FIG. 16 is a schematic of a typical system installation involving
fan-coil compressor package units as shown in FIG. 13 the air pre-conditioner
being implemented as shown in FIG. 13.
And FIG. 17 is a schematic of a typical system installation involving
ductless or mini-split units as shown in FIG. 15 the air pre-conditioner
being implemented as shown in FIG. 15.
PREFERRED EMBODIMENT
Referring now to FIGS. 1-4 of the drawings, the multi-use air pre-conditioner
PC is shown in its basic non implemented and ready to operate condition,
comprised generally of a first ducting means A dedicated to humidification
and dehumidification of a column of air, a second ducting means
B dedicated to regenerating weakened desiccant when operating in
the dehumidification mode, a third ducting means C utilized with
a heat transfer means T to remove heat from the first mentioned
ducting means, and a fourth adaptable ducting means D that is shared
with ducting means B and C and utilized with said heat transfer
means T and return air through ducting means C and ducting means
B for regeneration. The second ducting means B houses heater means
H that supplements the waste heat of absorption from heat transfer
means T, and from the refrigeration condenser coil when it is implemented.
An evaporative cooling means E is provided for insertion into the
ducting means C so as to increase the effectiveness of the heat
transfer means T. Placement spaces for opening and closures therefor,
and for ducting means D and module E are provided in the ducting
means B and C, as will be described as they are incorporated in
each of said means to implement the functions required. Desiccant
dehumidification is carried out by a desiccant wheel W with diametrically
opposite segments thereof rotated by motor means M through the cross
sections of ducts A and B, as shown. In carrying out this invention
and it its preferred form, there are basically two columns of air
reversely transported through ducting means A and B by means of
blowers or fans F1 and F2 as shown. Implementation of this air
pre-conditioner is by installation therein of predetermined closure
partitions, duct means D and module E as may be required and as
clearly shown in FIGS. 10 and 11.
The ducting means A dedicated to the dehumidification of a column
of air (in a normal dehumidifying mode) is clearly shown in FIG.
1 as a longitudinally disposed through duct for left to right air
flow. In order to carry out the air pre-conditioning process involved,
the ducting means A has an intake section 10 an air processing
section 11 a heat transfer section 12 and a discharge section
13. The intake section is open to receive outside air or to receive
return air from the conditioned air space, and either receives blower
air or preferably houses the intake fan F1 for delivery of an air
column through the desiccant wheel W and heat transfer means T and
discharge from section 13 as supply air to conditioned space.
The ducting means B dedicated to regeneration by a column of air
(in a normal dehumidification mode) is clearly shown in FIG. 1 as
a longitudinally through duct for reverse right to left air flow.
A feature of this invention is that the ducting means B is contiguous
to and disposed alongside the ducting means A and is substantially
coextensive with said ducting means A. In order to carry out the
air pre-conditioning process involved, the ducting means B has an
intake section 15 alongside section 13 of means A, an air processing
section 16 alongside section 11 of means A, and a discharge section
17 alongside section 10 of means A. And, in accordance with this
invention, ducting means B has a waste heat section 18 and a supplemental
heat section 19 intermediate the sections 15 and 16 thereof. The
section 18 houses the heater means T and the section 19 houses the
supplemental heater means H. Whereas the ducting means A is essentially
an imperforate duct, the ducting means B is characterized by flow
control means spaces for openings, and closures, and air column
directing means, as follows:
The intake section 15 is open laterally in at least one and preferably
two directions, a first direction to receive blower air from duct
C, and a second direction to receive recirculated waste heat air
through duct D. As shown, the ducting means B overlies the ducting
means A, and the ducting means C, next described, underlies said
ducting means A, in which case the intake section 15 has a first
downwardly disposed flow control means 21 space (see FIG. 2) which
is initially open or can be opened to the duct C and/or to an intake
fan F2. And, the intake section 15 has a second upwardly disposed
flow control means 22 space (see FIG. 4) which is initially open
or can be opened to the duct D for recirculation of waste heat from
duct C and driven by said intake fan F2 as will be described. The
discharge section 17 of ducting means B is an imperforate duct directed
downwardly alongside the intake section 10 of means A to exhaust
at 23 (see FIG. 2).
The ducting means C transports the regeneration air column either
directly through the ducting means B or indirectly though the waste
heat transfer means T, and alternately to exhaust at 23' (see FIG.
1). Means C is a longitudinally disposed duct for reverse right
to left flow and is contiguous to and disposed alongside of the
ducting means A and is substantially coextensive with said ducting
means A. In order to carry out this air pre-conditioning process,
the ducting means C has an intake section 25 alongside section 13
of means A, a heat transfer section 26 and a discharge section
27 alongside section 10 of means A. The intake section 25 is open
to receive outside air or to receive return air from the conditioned
air space, and either receives blower air or preferably houses the
intake fan F2 for delivery of the regeneration air column through
the desiccant wheel W, and alternately through the heat transfer
means T to discharge from exhaust at 23 or 23'. Like the means B,
ducting means C is characterized by placement spaces for openings
and closures, and air column directors, and air processing modules,
as follows:
The intake section 25 is open laterally and/or endwise in at least
one and preferably several places, to split off blower air from
fan F2 and to exhaust air at 23', or to recirculate said blower
air through duct D next described. As shown, the ducting means C
underlies the ducting means A and has a first laterally disposed
flow control means 28 space (see FIG. 4) which is initially open
or can be opened to duct B, at the delivery side of fan F2. The
discharge 23' at section 27 is disposed alongside the duct B discharge
23 there being a second flow control means 29 space (see FIGS.
2 and 3) which is initially open or can be opened to exhaust at
23', and there being a third flow control means space 30 (see FIGS.
2 and 3) which is initially open or can be opened to recirculate
regeneration air from duct C through duct D to duct B. The flow
control means 30 space is indicated by a bracket in FIG. 1 the
exhausts at 23 and 23' discharging side by side as shown in FIG.
3.
The ducting means C and ducting means B are initially in open or
can be in open communication through a coupler duct means 31 that
extends between the flow means 28 space of duct C and the means
21 space of duct B (see FIGS. 1 2 and 4).
The ducting means D recirculates regeneration air from ducting
means C to the ducting means B for the addition thereto of supplemental
heat by means H and waste compressor heat. The recirculated air
first absorbs heat at the waste heat transfer means T. Ducting means
D is a longitudinally disposed duct for left to right flow of an
air column and is contiguous to and disposed alongside of the ducting
means B and is substantially coextensive with said ducting means
B. Means D is essentially an air transfer duct that wraps around
the left end of ducting means A and C and coextensively overlies
the ducting means B. The ducting means D is characterized by an
intake section 32 alongside the discharge section 27 of means C,
and a discharge section 33 alongside of the intake section 15 of
means B. Like the means B and C, ducting means D is characterized
by flow control means spaces for openings and closures, and for
air column directors, as follows:
The intake section 32 is open endwise and/or laterally into a vertical
riser 34 that turns right into a horizontal duct 35 overlying the
duct B. The discharge section 33 continues from duct 35 and opens
downwardly at the top of section 15 of duct B. A feature is the
replaceability of means D, essentially an attachment used as and
when required.
Humidity conditioning herein is by a desiccant dehumidifying means,
preferably of the wheel type W as shown. Wheel W can vary in form
as may be required, and is shown as a rotating cylinder 36 of the
regenerating type having a dehumidifying segment 37 in the intake
air ducting means A, and having a regenerating segment 38 in the
exhaust air ducting means B. Proportionate use of these two segments
is variable and depends upon the volumetric flow ratio of the two
opposing air streams and the available temperature of regeneration
air immediately prior to entering the regenerating segment 38 (see
FIG. 12). The higher the regeneration temperature, the smaller the
area needed for segment 38 for regeneration and the larger is the
available area of segment 37 for enhanced flow capacity at a given
face velocity. Where this ratio is 2 to 1 as shown in FIG. 12
approximately two thirds of the desiccant wheel is devoted to segment
37 for dehumidification by absorbing moisture, while one third is
devoted to segment 38 for regeneration of the weakened moisture
saturated desiccant. Regeneration of weakened desiccant is by means
of heated or tempered air delivered through ducting means B, wherein
waste heat is recovered from the refrigeration means and supplemental
heat is applied by heating means H as needed to achieve the desired
inlet regenerating air temperature to segment 38. The desiccant
wheel W is shown in FIG. 12 as a packed-type cylinder comprising
a suitable air permeable desiccant material of, for example, alumina,
silica gel, lithium chloride or suitable hygroscopic polymers, and
the like.
The heat transfer means T removes the heat resulting from absorption
of moisture into the desiccant and is positioned immediately downstream
from the desiccant wheel section 37. The means T is in the form
of heat pipes 42 characterized by a hot end 40 for the absorption
of heat, and by a cold end 41 for the dissipation of heat. In other
words, there is a "heat in" end 40 and a "heat out"
end 41. In carrying out this invention, the heat-in end 40 is placed
in the ducting means A following moisture absorption by the desiccant,
while the heat-out end 41 is placed in the ducting means C for dissipation
of heat into exhaust air at 23'. Accordingly, there is a heat transfer
that occurs between ducting means A and ducting means C, by means
of a bank comprised of a multiplicity of heat pipes 42 the hot
ends 41 in the form of heat absorbers, and the cold ends in the
form of heat dissipators. In practice, the heat pipes 42 are short
lengths of heat conductive tubing sealed at their opposite ends,
having fitting tubular wick lining 43 and charged with a refrigerant
44 a gas-liquid. A temperature differential between the ends of
each pipe 42 causes the refrigerant 44 therein to migrate by capillary
action to the warmer end where evaporation thereof takes place and
absorbs heat. The resultant refrigerant vapor then returns through
the hollow tube center of the wick lining 43 and to the cooler end
41 of the pipe 42 where it gives up the heat carried thereby, by
condensing into the wick lining 43 and repeating the cycle. The
heat transfer process is efficient, as the heat pipes 42 are sealed
and have no moving parts, and require little or no maintenance.
As shown in FIG. 9 the heat pipes 42 are finned at 45 for efficient
heat energy transfer.
The heater means H completes the heating requirement for effective
regeneration of the desiccant in segment 37 of the desiccant wheel
W. Means H is a gas fired or an electric powered furnace that heats
the column of air passing through duct B and through the regenerative
segment of the wheel W. Means H is thermostatically controlled and
brings the column of air to regenerating temperature, whether pre-heated
by waste heat or not. The amount of available waste heat will determine
the required capacity of the heater means H, and in practice the
application of waste heat at section 18 of the ducting means B preceeds
the application of supplemental heat by said means H.
The evaporative cooler means E conditions the cold ends of the
heat pipes 42 for effective dissipation of heat energy absorbed
by the hot ends 41 thereof. As shown in FIG. 14 the means E involves
a spray bar 46 supplied with an evaporative liquid, water, by a
pump 47 drawing said liquid from a sump 48. The sump 48 provides
a closure for a flow control means 49 space provided therefor in
the bottom side of ducting means C, and supports the spray bar 46
upstream of the bank of heat pipes 42 to evaporatively cool the
cold "heat-out" ends 41 thereof. The evaporative cooler
module E is installed as and when required.
During the summer and similar warm weather, the heat pipes 42 function
as shown in the drawings to support the dehumidification process
performed by this air pre-conditioner. However, during the winter
and similar cold weather, the heat pipes 42 function automatically
in a reverse direction of heat transfer, achieved by deactivating
the heater means H and also the evaporative cooling module E, but
retaining full operation of the desiccant wheel W, thereby pre-heating
and humidifying incoming air through ducting means A.
A basic condition 1 implementation of the air pre-conditioner PC
is shown in FIG. 10 of the drawings, wherein the structural combination
of ducting means A, B and C is made functional for stand-alone operation
of the unit to dehumidify a conditioned space. Accordingly, outside
air (OSA) is delivered to ducting means C by the fan F2 a flow
splitter member 50 being installed in the flow means space 28 to
divert a portion of the air flow into the coupler duct means 31
for delivery through flow means 21 space and into the intake section
15 of ducting means B. The ducting means A is dedicated to and dehumidifies
the conditioned air space, taking in return air at intake section
10 and delivering supply air (SA) at discharge section 13. The
flow means 22 space of ducting means B is closed by a corner member
51 that turns the split off portion of the fan driven air column
to flow through the heater means H and regeneration segment 37 of
the desiccant wheel W. The remaining portion of the split air flow
is driven through the bank of heat pipes 42 of the heat transfer
means T to remove heat of absorption from the dehumidification process
in ducting means A. Air flow through and exhaust from the ducting
means C is by means of a closure member 52 installed in the flow
means 49 space, and by a corner member 53 installed in the flow
means 30 space. Accordingly, discharge of duct C is at exhaust 23'.
A condition 2 dehumidification heat recovery implementation of
the air pre-conditioner PC is shown in FIG. 11 of the drawings,
wherein the structural combination of ducting means A, B, C and
D is made functional for stand-alone operation of the unit to dehumidify
an air conditioned space. Additionally, waste heat recovery is assisted
by the evaporative cooler module E. The ducting means A is dedicated
to and dehumidifies the conditioned air space, taking in return
air (RA) or outside air (OSA) at air intake section 10 and delivering
supply air (SA) at discharge section 13. Accordingly, outside air
(OSA), or return air (RA) is delivered to ducting means C by the
fan F2 a closure member 54 being installed in flow means 28 space,
and a closure member 55 being installed in flow means 29 space,
so as to confine air flow through the duct C and through the bank
of heat pipes 42 dissipating waste heat from the dehumidifying process.
The ducting means D is incorporated in the unit structure, or installed
as an attachment, with its intake section 32 open from the flow
means 30 space, and with its discharge section 33 open into the
flow means 22 space of the ducting means B. Thus, all of the air
delivered by fan F2 is passed through the heat dissipating ends
41 of the heat pipes and through the waste heat section 18 of duct
B. A corner member 56 is installed in the flow control means 21
space to close the coupling duct 31 and to direct air flow through
the supplemental heater means H and through the regeneration segment
of the desiccant wheel W. The discharge section 17 discharges the
air flow alongside the discharge section 27 of duct C for exhaust
at 23 alongside the exhaust of duct C at 23'.
The evaporative cooler module E is installed in the placement space
49 closing the same, and operating to evaporatively cool the heat
dissipating ends 41 of the heat pipes 42 so as to enhance their
efficient operation.
A package air conditioner combination utilizing basic implementation
is shown in FIG. 13 of the drawings, wherein refrigeration waste
heat of compression assists the desiccant regeneration process,
with recovery of waste heat of absorption in the dehumidification
process. In this embodiment the use of placement spaces and splitter
member 50 and corner member 51 and 53 is as above described and
shown in the embodiment of FIG. 10 and the evaporative cooler module
E is installed as a closure for placement space 49 as in the embodiment
of FIG. 11. This is another basic implementation wherein heat of
compression from the package unit air conditioner, an A/C unit,
is advantageously employed as a primary source of heat for regenerating
weakened desiccant. As shown, the A/C unit is self contained and
includes a fan F3 driven by a motor M1 for drawing return air (RA)
from the air conditioned space. A portion of said return air is
split off at 55 and delivered by fan F3 to the ducting means B and
C, as above described, and subsequently exhausted at 23 and 23'.
The compressor 57 delivers hot compressed refrigerant fluid through
a primary condenser coil 58 for maximum heat extraction in the waste
heat section 18 of ducting means B. A secondary condenser coil 58'
is in fluid parallel with coil 57 that is in the A/C unit for assuring
complete condensation of said fluid. The condensed fluid is coalesced
in a receiver 59 and then passed through a thermal expansion valve
60 for heat extraction in the refrigeration coil 61. Coil 58' of
reduced size is cooled by a blower 62. Supply air (SA) from the
ducting means A is returned to the air conditioned space through
the A/C unit ahead of its filter 63 and delivered as supply air
(SA) by the fan F3. Maximized heat extraction by coil 57 significantly
reduces the size requirement of the heater means H, the regeneration
air being previously heated by the heat transfer means T.
A split compressor and fan-coil combination utilizing basic implementation
is shown in FIG. 15 of the drawings, wherein refrigeration waste
heat of compression assists the desiccant regeneration process,
with recovery of waste heat of absorption in the dehumidification
process. In this embodiment the use of placement spaces and closure
members 54 and 55 and corner member 56 is as above described and
shown in the embodiment of FIG. 11 and the evaporative cooler module
E is installed as a closure for placement space 29 as in the embodiment
of FIG. 11. This is another basic implementation wherein heat of
compression from the mini-split compressor unit 65 is advantageously
employed as a primary source of heat for regenerating weakened desiccant.
As shown, the refrigeration system is split into the compressor
unit 65 and the fan-coil unit 65' with a fan F4 driven by a motor
M2 for drawing return air (RA) from the air conditioned space. A
portion of said return air is split off at 55 and delivered by fan
F2 to the ducting means C, as above described, and subsequently
exhausted at 23. The compressor 66 delivers hot compressed refrigerant
fluid through a primary condenser coil 67 for maximum heat extraction
in the waste heat section 18 of ducting means B. A secondary condenser
coil 68 is in fluid series with coil 67 and is of substantially
reduced size in the compressor unit 65 for assuring complete condensation
of said fluid. The condensed fluid is coalesced in a receiver 69
and then passed through a thermal expansion valve 70 for heat extraction
in the refrigeration coil 71. The coil 68 is cooled by a blower
72. Supply air (SA) from the ducting means A is returned to the
air conditioned space through the fan-coil unit 65' ahead of its
filter 73 and delivered as supply air (SA) by the fan F4 thereof.
Maximized heat extraction by coil 67 significantly reduces the size
requirement of the heater means H, the regeneration air being previously
heated by the heat transfer means T. Further, a feature of this
series condenser configuration is that the maximum heat extraction
at coil 67 minimizes the size requirement for the compressor unit
coil 68 with a comensurate reduction in energy required of the
compressor unit to cool the same.
In accordance with this invention, the air pre-conditioner PC as
it is shown in FIG. 1 and as implemented in FIG. 10 is combined
with a multiplicity of package air conditioners A/C as shown in
FIG. 16 of the drawings. In practice, one pre-conditioner PC can
serve at least three A/C units. The FIG. 10 implementation takes
in outside air OSA by means of fan F1 to be dehumidified and discharged
as supply air SA; and takes in return air RA by means of fan F2
for transfer of heat out of said supply air and discharged as exhaust
air at 23'. It is to be understood that the implementation of FIG.
11 can be substituted for the basic FIG. 10 implementation, as it
is later described. The air pre-conditioner PC now under consideration
is in fluid circuit, in parallel as shown, with one of the multiplicity
of air refrigeration package unit A/C via a pressure and a return
line 70 and 71. Supply air SA from the pre-conditioner PC is delivered
to each A/C package unit via a duct 72 where it is refrigerated
for discharge into an air conditioned space S1-S3 via supply air
ducts 73. Distribution ducts 74 are employed if and when required.
In practice, a minimum of outside air OSA enters through the air
pre-conditioner PC; and as and when required a maximum of outside
air OSA is supplemented by a blower fan F4. Return air RA from air
space S1-S3 is via ducting 75 to the intake fan F2 of the pre-conditioner
PC for heat dissipation and exhaust at 23'.
In accordance with this invention, the air pre-conditioner PC as
it is shown in FIG. 1 and as implemented in FIG. 11 is combined
with a multiplicity of "ductless" or "Mini-split"
refrigeration air conditioning systems comprised of separate compressor
units C/C and fan-coil units F/C, as shown in FIG. 17 of the drawings.
In practice, one pre-conditioner PC can serve at least three mini-split
systems as shown. The FIG. 11 implementation takes in outside air
OSA by means of fan F1 to be dehumidified and discharged as supply
air SA; and takes in return air RA by means of fan F2 for transfer
of heat out of supply air SA and for absorption of waste heat of
compression from a compressor unit C/C, and discharge or exhaust
at 23. It is to be understood that the implementation of FIG. 10
can be substituted for the basic FIG. 11 implementation, as it is
previously described. The air pre-conditioner PC now under consideration
is in fluid circuit, series as shown, with one of the multiplicity
of compressor units C/C via a pressure line and return line 80 and
81. Supply air SA from the pre-conditioner PC is delivered to each
fan-coil unit F/C via a duct 82 where it is refrigerated for discharge
directly into an air conditioned space S1-S3 via its discharge 83.
distribution ducts are not required. In practice, a minimum of outside
air OSA enters through the air pre-conditioner PC; and as and when
required a maximum of outside air OSA is supplemented by a blower
fan F5. Return air RA from air space S1-S3 is via ducting 85 to
the intake fan F2 of the pre-conditioner PC for heat dissipation
and exhaust at 23.
Although the mini-split C/C-F/C and A/C package configurations
are described as "air conditioners", some or all in a
given building system can also be operated as heat pumps. Heat pumps
are known to provide capability for reversing cycle, as by means
of a reversing valve (not shown) reversing flow between the evaporator
and condensing coils. Since the pre-conditioner PC conditions outside
air OSA, and since the heating winter cycle will require humidification
of outside air, refrigerant waste heat from the condenser coil at
the compressor of unit C/C will extract heat by connecting it as
a heat pump, the hook-up of FIG. 13 is preferred over the series
hook-up of FIG. 15 for this reverse operation, since the pre-conditioner
PC coil 57 can be isolated. When humidification is not required
and operating reversely as a heat pump, return air will serve as
an additional heat source prior to its discharge at the exhaust.
Note that this air pre-conditioning and refrigeration air conditioning
system works equally well with either air-cooled or liquid cooled
condeners. And, control means (not shown) for the air pre-conditioner
PC can be a suitable microprocessor humidistat, to control the desiccant
wheel, evaporative sprays, heater H application, and compressor
waste heat, and also the air circulation fans F1-F5. This pre-conditioned
air alone or as combined with the several types of refrigeration
air conditioners, will benefit economically by employing the total
availability of waste heat and by applying dehumification where
it increases efficiency in both the dehumification and refrigeration
processes.
Having described only the typical preferred forms and applications
of my invention, I do not wish to be limited or restricted to the
specific details herein set forth, but wish to reserve to myself
any modifications or variations that may appear to those skilled
in the art, as set forth within the limits of the following claims.
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