US20050076665A1

US20050076665A1 - Cooling assembly

Info

Publication number: US20050076665A1
Application number: US10/963,188
Authority: US
Inventors: Roger Pruitt
Original assignee: Individual
Current assignee: GPM Inc
Priority date: 2002-08-23
Filing date: 2004-10-12
Publication date: 2005-04-14

Abstract

A process and the required apparatus for air conditioning the interior of a structure is shown which can be run entirely off a DC power source, such as a storage battery. A shell and tube heat exchanger is combined with a mechanical refrigeration system to provide a wet shell side and a dry tube side of the apparatus. In the operation of the air conditioner, a mass of distributed water is established on the wet shell side, and a flow of ambient air is passed through the wet shell side to form a resulting stream of moist air. A flow of ambient air is passed through the dry tube side and a resulting stream of dry cooled air is recovered. The streams of most and cooled air can either be combined or routed separately depending primarily upon the humidity of the surrounding environment to be cooled. The air conditioning unit is not hermetically sealed and the water consumption rate is generally less than that required for a conventional evaporative cooler.

Description

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a continuation-in-part of my earlier filed application Ser. No. 10/629,121, filed Jul. 28, 2003, and which claimed the benefit of U.S. Provisional Application No. 60/405,584, filed Aug. 23, 2002.

BACKGROUND OF THE INVENTION

1. Field of the Invention
The present invention relates in general to low power air conditioning systems, and, in particular, to a low power air conditioning system employing a tube and shell heat exchanger for use in arid conditions and to a combination direct/indirect evaporative cooler with refrigerated sump water for use in other environments.
2. Description of the Prior Art
In one embodiment, the present invention provides air conditioning for structures that are located in arid, high temperature environments, such as deserts. Such environmental control is essential to enjoying a good quality of life, and, in some instances, is essential to supporting life. This is true for both humans and livestock.
In desert environments, daytime temperatures often reach well above 100 degrees Fahrenheit while at the same time the relative humidity is often below 20 percent. Typically, conventional evaporative cooling based air conditioning systems, so called “swamp coolers”, are effective in such conditions, because of the low humidity. A source of electrical power is required to operate such systems, so the cost of operation is a limitation on their use. Conventional evaporative coolers consume considerable quantities of water so their use is limited to areas where water is available. Sufficient quantities of water are not always available in desert environments. Other types of air conditioning systems require sealed buildings, expensive and high maintenance equipment, and are expensive to operate. Some dwellings and particularly buildings in which livestock may be kept are not well sealed or insulated so there is little impediment to the interiors of such structures reaching thermal equilibrium with the exterior environment. Typically, such structures are not provided with air conditioning systems because of the cost of operating them and the general ineffectiveness of air conditioning systems in such structures. Most air conditioning systems operate on electricity, and electricity is not always available, or is not available at a reasonable price where the structures are located. It would be greatly beneficial to both human beings and livestock if an effective, simple, self-contained air conditioning system could be provided for desert environments that would operate inexpensively in unsealed structures.
It would also be advantageous to provide an air conditioning system which could be powered on direct current, either by batteries or solar panels, or both, which system had the previously described advantages while at the same time being operable over wider humidity ranges including tropical and semi-tropical climates.
It would be a further advantage to provide such a system which utilized both a relatively wet airstream and a relatively dry airstream, which airstreams could be selectively routed to the interior of a structure to be cooled, either by combining the streams in a predetermined ratio or by selecting, for example, only the relatively dry airstream to be delivered to the space to be cooled in the presence of high humidity.
In its simplest form evaporative cooling of buildings has been accomplished by injecting a fog or mist of water into a moving stream of air. See, for example, Atkins, U.S. Pat. No. 5,146,762. One problem with this system is that it causes excess humidity within the building resulting in algae and bacteria problems. Atkins proposes to minimize some of these problems by placing exhaust fans at one end of a building widely spaced from fogger nozzles at the opposite end of the building. The disclosed rate of water consumption is very high. In excess of 95 percent of the water supplied to the fogger nozzles is consumed. Atkins' evaporative cooling system is said to produce a temperature drop of approximately 20 degrees.
Conventional evaporative cooling systems have been combined into more elaborate systems that include heating means. See, for example, Grant et al. U.S. Pat. No. 4,773,471. Conventional evaporative cooling systems have also been combined into elaborate systems with refrigerated air systems. See, for example, Conner U.S. Pat. No. 5,911,745.
Urch U.S. Pat. No. 6,434,963 discloses an air cooler with two air flow paths, namely, an inlet path for outside air and an outlet path for stale air. A heat exchanger pre-cools the fresh air with heat extracted from the stale air, and further cooling is achieved by means of an evaporative cooler that spans the two air flow paths.
Those concerned with these problems recognize the need for an improved air conditioning system.

SUMMARY OF THE INVENTION

In one embodiment, the air conditioning assembly according to the present invention comprises a shell and tube heat exchanger wherein ambient air is forced through both sides and discharged approximately together into the interior of the structure that is to be cooled. For convenience, the air streams from the two sides can be combined into one combined stream before being discharged into the interior of the structure, or they may be discharged separately into the structure. This heat exchanger is particularly suited for use in the high heat and low humidity conditions that are typically found during the summer months in deserts. The air conditioning assembly is particularly effective in situations where the temperature is above approximately 80 degrees Fahrenheit, and the relative humidity is below approximately 40 percent, and, preferably, below approximately 35 percent. The assembly is suitably operable even in situations where the structure to be air conditioned is not tightly sealed, that is where there may be openings through the structure that are substantially unobstructed to air flow having as much as, for example, six square inches to a square foot or two of area. Barns, tents, temporary structures and the like are provided with an efficient, reliable, economical, simple, and effective air conditioning system according to the present invention. The air conditioning system according to the present invention does not require an elaborate or expensive installation for its functioning. It can be easily transported to and set up inside of a temporary structure such as, for example, a tent.
The shell side of the heat exchanger is preferably wet with a shower or weep of a liquid such as water, and the air flow is turbulent through the shell side. The stream of flowing air is directed from the shell side to an outlet. The air flowing through the tube side is cooled by contact with the walls of the tubes, and is discharged to an outlet. Preferably the air streams from the shell and tube sides are combined and discharged into the interior of the structure that is to be cooled. These air streams can be combined after discharge into the interior of the structure, if desired. Preferably, the intake and discharge of the air streams are all within the interior of the structure.
In another embodiment, the present invention comprises a direct/indirect evaporative cooler with refrigerated chilled sump water. The cooler is preferably designed as a stacked arrangement. A refrigeration compressor and storage batteries occupy a top section of the design and rest on a top shelf. The top shelf forms the top wall of an exhaust air plenum. A forced-air evaporative cooling chamber, located below the exhaust air plenum, occupies the middle section of the design and comprises about 65% of the total height of the unit in one embodiment. A cold water sump and an intake air plenum occupy the bottom floor of the cooling chamber. The bottom floor of the cooling chamber also comprises the top wall of an intake plenum which houses an intake fan. The intake fan draws air upwardly through a plurality of riser tubes which connect the intake plenum with the exhaust plenum and which pass through the cooling chamber.
Water in the cold water sump is refrigerated by the refrigeration compressor located in the top section of the design. Cold water from the cold water sump is introduced into the evaporative cooling chamber through a distribution header. The cold water saturates an evaporative media which surrounds or otherwise contacts the riser tubes in the cooling chamber. Air is introduced into the cooling chamber by means of oppositely arranged fans mounted on sidewalls of the cooling chamber which create a turbulent air flow in the cooling chamber and which enhance the evaporative cooling process. Cooled air from the cooling chamber can be discharged through a suitable duct to the interior of the structure to be cooled.
Air is also being drawn into the intake plenum by the intake fan, which air flow is forced upwardly through the riser tubes in the cooling chamber. The riser tubes pass though the cold water sump and also contact the evaporative media in the cooling chamber, whereby the outside of the tubes are cooled. The air within the tubes is cooled by conduction through the tubes. This relatively drier air can be directed through a suitable duct to the interior of the structure to be cooled and can be combined with the more moist, cooled air from the cooling chamber, if desired.
In this latter embodiment of the invention, air is being cooled using two simultaneous processes. Air is cooled by direct contact with water in the evaporative cooling chamber, raising the absolute humidity of the air cooled in this manner. Additional air is also being cooled by conductive heat transfer within the riser tubes. The absolute humidity of this additional air is either unchanged or only slightly changed, or decreases slightly, due to condensation on the inside of the riser tubes. If desired, the two air flows can be combined into a discharge duct so that the discharged air consists of a mixture of relatively humid air from the evaporative process and air with near ambient humidity. Control over the humidity of the discharged air can be obtained by regulating the ratio of the two previously described air flows.
The cold water sump at the bottom of the cooling chamber serves as a cooling mass, as well as a water storage sump. The water in the sump is refrigerated to near freezing by means of a low temperature compressor similar to that used on an ice machine. The compressor can be AC or DC operated, but is preferably DC operated. The electric fans used in the intake plenum and on the cooling chamber are preferably DC fans which can be driven by solar cells or storage batteries.
Other objects, advantages, and novel features of the present invention will become apparent from the following detailed description of the invention when considered in conjunction with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention provides its benefits across a broad spectrum of structures. While the description which follows hereinafter is meant to be representative of a number of such applications, it is not exhaustive. As those skilled in the art will recognize, the basic methods and apparatus taught herein can be readily adapted to many uses. It is applicant's intent that this specification and the claims appended hereto be accorded a breadth in keeping with the scope and spirit of the invention being disclosed despite what might appear to be limiting language imposed by the requirements of referring to the specific examples disclosed.
Referring particularly to the drawings for the purposes of illustration only and not limitation:
FIG. 1 is a diagrammatic view of one embodiment of a tube and shell heat exchanger according to the present invention.
FIG. 2 is a cross-sectional view taken along line 2-2 In FIG. 1.
FIG. 3 is a diagrammatic cross-sectional view taken through the shell plenum of a further embodiment according to the present invention showing a liquid spray system.
FIG. 4 is a diagrammatic cross-sectional view taken through the shell plenum of a further embodiment according to the present invention showing the tubes fully enclosed in blankets.
FIG. 5 is a plan view of a structure in which a tube and shell heat exchanger air conditioning system according to the present invention has been installed.
FIG. 6 is a cross-sectional view of the heat exchanger of FIG. 5 taken through the shell plenum.
FIG. 7 is a chart of the temperature and relative humidity readings recorded in Tables 4 and 5 at locations 116 and 120 in FIG. 5.
FIG. 8 is a perspective view of another embodiment of the device of the invention which features combined direct/indirect evaporative cooling with refrigerated chilled sump water.
FIG. 9 is a rear view of the device of FIG. 8 with the rear wall removed for ease of illustration of the internal components of the device.
FIG. 10 is an isolated view of the cooling chamber and refrigeration manifold used in the device of FIGS. 8 and 9.
FIG. 11 is a perspective view of the device of FIG. 8 with the rear wall removed for ease of illustration of the internal components of the device.
FIG. 12 is a view of the top wall of the cooling chamber which also serves as a tube sheet for the riser tubes.
FIG. 13 is an isolated view of the cooling chamber of the device of FIG. 8.
FIG. 14 is a side view of the cooling chamber showing the location of the water distribution array.
FIG. 15 is an isolated view of the air intake plenum and air intake fan.
FIG. 16 is an isolated view of the refrigeration manifold used in the cold water sump of the device of FIG. 8.
FIG. 16A is a cross sectional view taken along lines 16A-16A in FIG. 16.
FIG. 16B is a simplified end view of the manifold of FIG. 8 showing the cross-over piping arrangement used to produce the interlayered flow pattern.
FIG. 17 is a simplified, schematic view of an auxiliary heat exchange unit which can be operated off the chilled water in the cold water sump of the device of the invention.
FIG. 18 is a cross-sectional view of a cable used to connect the auxiliary heat exchange unit of FIG. 17 with the main cooling assembly shown in FIGS. 8-15.

DETAILED DESCRIPTION OF THE INVENTION

The detailed description of the invention will now be provided with respect to two different preferred embodiments:
Low Humidity Air Conditioner Embodiment:
Referring now to the drawings wherein like reference numerals designate identical or corresponding parts throughout the several views, there is illustrated generally at 10 a tube and shell heat exchanger, which is particularly adapted for use as a low power air conditioning unit in high temperature, low humidity conditions with structures that are not hermetically sealed. The floor plan of such a structure is indicated generally at 64 in FIG. 5.
Heat exchanger 10 is confined within external case 62. For purposes of illustration, external case 62 is shown as rectangular, but other arcuate, spherical, or cylindrical forms are contemplated within the scope of the present invention.
Air, preferably internal air from near the ceiling of a structure that is to be cooled, is drawn into the tube side of the heat exchanger through inlet port 12 into intake plenum 14 of heat exchanger 10. Air is drawn into inlet port 12 by exhaust fan 46. Air is drawn from intake plenum 14 through heat exchange tubes 34 into exhaust plenum 18. Tube inlet ends 36 are sealingly mounted in inlet tube sheet 60, and tube outlet ends 38 are sealingly mounted in tube outlet sheet 32. Exhaust fan 46 expels the air from the tube side of the heat exchanger into tube side exhaust conduit 22.
The shell side of heat exchanger 10 is in the form of a shell plenum 16 that surrounds heat exchange tubes 34 between inlet tube sheet 60 and outlet tube sheet 32. Heat exchange tubes 34 are shown for the purposes of clarity of illustration as being straight, but, as will be understood by those skilled in the art, other forms such as coiled or looped heat exchange tubes can be used. A body of liquid, preferably water, is disposed within the shell side of heat exchanger 10. The surface of the body of liquid is indicated at 50. The liquid generally occupies less than one-half, and preferably, less than one-quarter of the volume of the shell side of the heat exchanger. The bottom portion of the shell plenum 16 forms a liquid sump in which the liquid resides. At least one, and preferably at least two fans are position to force ambient internal air from within the structure into shell plenum 16 of heat exchanger 10. In FIG. 1, three such shell side input fans are indicated at 40 (first input fan), 42 (second input fan), and 44 (third input fan). These fans together generate substantial turbulence in the air on the shell side of heat exchanger 10. The air from shell plenum 16 is expelled from heat exchanger 10 through shell side exhaust conduit 20.
The liquid in the sump within shell plenum 16 is sprayed over the heat exchange tubes 34. One form of a spray system is illustrated in FIG. 1, and consists of a pump feed line 26 that serves to convey liquid from the liquid sump on the shell side to liquid pump 24. Pump 24 supplies energy to the liquid and discharges it through pump discharge line 28 to spray head 30 where it is sprayed over the shell sides of heat exchange tubes 34. Spray head 30 is typically located at or near the top of the shell side plenum, although this is not necessary to the operation of the system. It is schematically illustrated here on the side of the shell side plenum for ease of illustration. The liquid runs and falls back down into the sump where it is recycled again. The liquid spray enhances the heat transfer between the heat exchange tubes 34 and the liquid, as well as rapidly increasing the humidity of the air in the shell plenum 16. Preferably, the liquid level is automatically maintained at about a constant level by means of a conventional float actuated valve connected to a supply of liquid (not shown).
Heat transfer between the liquid and the heat exchange tubes 34 is further enhanced by the provision of blanketing members, for example, tubular foam blankets 48 (FIG. 4), or loose reticulated foam sheets 104 (FIG. 6) positioned in physical contact with the heat exchange tubes 34. Also, the humidification of the air in shell plenum 16 is enhanced by the presence of blanketing members of some form. The blanketing members hold the liquid against the heat exchange tubes 34, and increase the surface area of the liquid within shell plenum 16. In general the blanketing members comprise inert reticulated material through which liquid and vapor phase liquids flow easily. Numerous such reticulated materials are known, including, for example, many natural and synthetic open pore foams, felts, battings, woven materials, and the like. Conventional commercial swamp cooler pads are generally suitable for use as the blanketing elements. Often such materials include bacteria stats, fungi stats, and the like. The blanketing materials can completely or partially enclose heat exchange tubes 34, as desired. Compare, for example, FIGS. 4 and 6. For the sake of clarity of illustration, these blanketing members are not illustrated in FIGS. 1, 2, and 3, but they are preferably employed in some form.
Various liquid spray systems can be employed. A particularly effective system is illustrated particularly in FIG. 3. Liquid from a suitable source such as, for example, the sump in shell plenum 16, is supplied under pressure to spray header 52 and distributed to spray header branches 56. Liquid is expelled in a shower from spray ports 54. Preferably, spray header 52 is positioned at the normally upper end of shell plenum 16 adjacent to outlet tube sheet 32 so that liquid showers down over the heat exchange tubes 34 and any associated blanket material, and is acted upon by the turbulent air flow from the shell side fans 40, 42, and 44.
The air exhausted from the tube side through exhaust conduit 22 is preferably mixed with the air exhausted from the shell side through exhaust conduit 20. The combined air streams are discharged to the ambient interior of the structure that is being cooled through combined exhaust conduit 58.
The best mode for the first embodiment of the invention presently contemplated is illustrated particularly by reference to FIGS. 5 and 6. An unfinished barn indicated generally at 64 has a rectangular shape about 30 feet wide and 50 feet long. Barn 64 is oriented east to west along its long axis as indicated by the letters N, S, E, W, in FIG. 5. Barn 64 has an uninsulated peaked metal roof, exposed 2 by 4 wooden stud walls, and a stucco exterior finish. The peak of the roof is about 10 feet from the floor, and the exterior walls are about 8 feet high. The interior volume of barn 64 is approximately 13,500 cubic feet. The exterior doors are not weather sealed and the total unsealed area around the exterior doors 66, 68, 70, 72, and 74 combined is from approximately 1 to 2 square feet. No significant pressure differential exists between the interior of barn 64 and the external environment, and any moisture content differential between the interior of barn 64 and the ambient environment tends rapidly towards equilibrium. Stall partitions 82, 84, 86, and 88 are half height, and stall dividers 80 and 78 are full height extending to within approximately 6 inches of the roof. Interior gate 76 is a full height security screen door.
The air conditioning system employed in barn 64 consists of tube and shell heat exchanger 10, combined exhaust conduit 58, air distribution chamber 92, air distribution branches 94 and 96, and air outlet heads 98 and 100. Input fans 42 and 44 supply ambient air from the interior of barn 64 to the shell plenum in heat exchanger 10. The air is typically drawn into the shell side of the heat exchanger from a level well below the level at which air is discharged at 98 and 100. Air is preferably drawn into the tube side of the heat exchanger from the hottest part of the structure adjacent to the uninsulated roof. Air exhausted from the tube side of heat exchanger 10 through tube side exhaust conduit 22 mixes with air exhausted from the shell side through conduit 20, and flows through combined exhaust conduit 58 to air distribution chamber 92. The air stream then splits and flows through each of air distribution branches 94 and 96 to respective air outlet heads 98 and 100. Air is drawn into the tube side of heat exchanger 10 through inlet port 12. Blanket material 104 (FIG. 6) in the form of conventional swamp cooler foam pads is in contact with tubes 34. A spray head of the general configuration shown in FIG. 3 positioned in the top of the shell plenum of heat exchanger 10. Preferably, approximately the lower one-quarter of the shell plenum is filled with water.
The rectangular exterior case of heat exchanger 10 is approximately 3 feet high by 2 feet by 2 feet, and it rests on the floor of barn 64. Input fans 42 and 44, mounted on opposed sides of the case, are 14 inches in diameter, run at 2,200 revolutions per minute, and operate on 12 volts of direct current. The rated amperage of these fans is 4 amps. The tube side exhaust fan 46 (FIG. 1) is a 12 inch, 12 volt, direct current, 4 amp fan. These fans are conventional automotive equipment, and they are typically used in association with conventional radiator cooling systems to pull air through the radiator of a liquid cooled internal combustion engine. The liquid pump 24 (FIG. 1) has a 12 volt, 7 amp, direct current motor, and a rated flow rate of 28 gallons per hour. The dimensions of the tube side intake plenum 14 (FIG. 1) are about 6 inches high by 24 inches by 24 inches. The dimensions of the tube side exhaust plenum 18 (FIG. 1) are about 6 inches by 24 inches by 24 inches. The dimensions of the shell side plenum 16 (FIG. 1) are about 24 by 24 by 24 inches. The heat exchange tubes 34 are straight sections of standard three-quarter inch cylindrical copper tubing having a length between tube sheets 32 and 60 of about 24 inches. There are 100 heat exchange tubes 34 arrayed in a generally regularly spaced rectangular pattern. The total surface area of the tubes 34 within shell plenum 16 is approximately 6,600 square inches. The intake port 12 for the tube side of the heat exchanger has a diameter of about 6 inches as do conduits 20 and 22. Intake port 12 opens upwardly and is positioned approximately 4 inches below the uninsulated metal roof of barn 64 so it is taking in approximately the hottest air within the interior of barn 64. Combined exhaust conduit 58 runs overhead, as do air distribution branches 94 and 96. The diameter of conduit 58 is about 8 inches, and conduit 58 is approximately 14 feet long. Each air distribution branch is approximately 10 feet long and 6 inches in diameter. The distribution box 92 is approximately 2 by 2 by 2 feet. The short leg of conduit 58 that runs into distribution box 92 is approximately 3 feet long. Air outlet heads 98 and 100 discharge downwardly at a height of approximately 9 feet above the floor.
The pump and fans have, for example, direct current motors powered by 5 conventional 12 volt deep cycle lead acid secondary batteries connected in parallel, indicated generally at 106. The batteries are connected through a conventional charging circuit indicated generally 108 to 3 conventional 30 volt, 4 amp hour solar panels indicated generally at 110, 112, and 114. The solar panels are mounted on the south facing pitch of the roof of barn 64. No other power source is required for the full time daylight operation of the air conditioning system. If desired, a conventional AC converter could be used to charge the batteries off of regular 110 volt house current, or some other power from a commercial utility service. This is not necessary, and would add to the cost of operation while limiting the system to use only at locations where commercial utility service is available. Likewise, the motors on the fans and pump could be replaced with conventional motors that would operate on power from a commercial utility service, but the costs of operation would be increased, and the flexibility of the system would be compromised.
The level of water in the sump is preferably maintained at approximately 5 inches. At this level the sump contains approximately 1.67 cubic feet of water. The shell side plenum has a volume of approximately 8 cubic feet, so the water occupies approximately 21 percent of the volume of the shell side plenum 16. This provides an adequate reserve of water to continue operations for more than a day. Other sump volumes can be used if desired, ranging from, for example, approximately 10 to 30 percent of the volume of the shell side plenum chamber 16. The sump need not be within the shell side plenum chamber. An external sump several times larger than the shell side plenum can be used if desired so as to provide for at least a week of unattended operation without replenishing the water supply. Less than a gallon of water is consumed during the course of the daylight hours in a typical summer day.
Barn 64 is located in a desert area where the daytime temperatures typically exceed 100 degrees Fahrenheit for several months during the summer, the relative humidity is often below 20 percent, and the sun shines for most of the daylight hours. Without air conditioning, the temperature at mid-day within barn 64 usually exceeds the outside temperature by at least approximately 10 degrees Fahrenheit.
The operation of the air conditioning system in barn 64 can be automated by providing a conventional thermostat (not shown) connected to the fans and pump circuits. Setting a thermostat at, for example, 74 degrees Fahrenheit, will activate the system early in the morning on a typical summer day, and keep it running well into the evening hours.
A preferred air conditioning assembly according to the present invention is fully self contained. That is, the power supply for the fan and pump motors is at the same location as the rest of the system. The water supply on the shell side of the heat exchanger can be replenished automatically by a float actuated valve on a water line, or manually, as desired. Where no reliable water supply is available, the rate of water consumption is so low that manual replenishment at widely spaced intervals is practical.
The power requirements are so small that a low voltage (12 or 24 volts) battery system coupled with a conventional solar panel driven charging circuit is sufficient to power the system during the daylight hours. The convenience of using a conventional solar panel charged battery system, and the widespread availability of such inexpensive systems, makes practical the unattended air conditioning of a wide variety of structures. Even livestock barns, for example, can be reliably and inexpensively air conditioned according to the present invention. Dwellings occupied by humans can likewise be air conditioned, even where very limited funds are available to devote to this purpose, and the dwellings are poorly sealed and uninsulated. The battery system can also be charged by wind turbines in areas where reliable wind flows are available. Other alternative energy sources can be used, if desired. Combinations of solar panels, wind turbines and other forms of alternative energy are suitable for use in charging the battery system. Since alternative energy sources typically do not deliver a constant level of energy, and the motors employed in the system require a substantially constant energy source, batteries are preferably interposed between the energy source and the air conditioning system. Where an alternative energy source is capable of delivering a constant source of energy, the use of a battery system is optional.

The air conditioning system according to the present invention was turned on in barn 64 at about 6:30 In the morning on a typical sunny summer day, and allowed to run all day. The inside temperature of barn 64 was measured at approximately location 102 (FIG. 5) approximately 4 feet above the ground, and the exterior temperature was measured in the shade under an open awning adjacent to the south side of barn 64 at approximately location 116. Location 116 is at a height of about 5 feet above the ground on a support for a 20 foot wide awning (not shown). The wooden awning is attached to the barn and extends outward from the level of the top of the wall of the barn 64 for about 20 feet. The wooden awning is completely open on three sides, The temperature at 116 is approximately what the temperature would be Inside of barn 64 without the air conditioning system. The temperatures observed were as shown In Table 1 below.

TABLE 1


	Inside temperature	Exterior temperature
Time	at 1.02. in ° F.	at 116, in ° F.

6:30	78	Not Recorded
7:30	72	Not Recorded
8:30	71	Not recorded
9:30	72	98
10:30	72	99
11:30	73	105
12:30	75	104
1:30	75	100
2:30	77	98
3:30	76	98

It has been observed that the temperature difference between the interior and exterior is the greatest when the humidity is the lowest and the outside temperatures are above 100 degrees Fahrenheit.

On a summer day when the sky was mostly overcast and the relative humidity was above approximately 35 percent, the following conditions were observed:

TABLE 2


	Outside temperature	Interior temperature
Time	at 116, in ° F.	at 102, in ° F.

6:30	83	Not Recorded
9:30	85	75
10:30	90	74
11:30	90	82
12:30	92	80
1:30	92	80
2:30	90	79
3:30	91	76

Relative humidity measurements were taken at various locations in and around barn 64 on a sunny summer day commencing about 9:00 a.m.

The readings at the locations indicated by the listed reference numbers in FIG. 5 were recorded in Table 3.

TABLE 3


Measurement Locations As Shown On FIG. 5

Time	98	100	78	116	44	42

9:00	30%	30%	31%	19%	31%	31%
10:00	30%	30%	31%	18%	32%	32%
11:00	34%	34%	32%	18%	31%	30%
12:00	35%	34%	34%	19%	30%	30%
1:00	37%	36%	35%	18%	32%	32%
2:00	34%	34%	35%	17%	31%	31%
3:00	34%	34%	35%	16%	32%	32%
4:00	34%	34%	35%	16%	32%	32%

The relative humidity remains substantially stable and constant throughout the day and throughout the interior of the structure.

Commencing about 9:00 a.m., Temperature and relative humidity measurements (T/H) were taken throughout a sunny day at various locations within and adjacent to barn 64. The readings were taken at the locations indicated by the reference numbers in FIG. 5 and were recorded in Table 4. The measurements at

locations

118 and 120 were taken about 5 feet above the floor. Location 118 gives an indication of the effect of radiation from the exterior wall. Location 124 is on the north side of the barn 64 about 5 feet above the ground. The measurements were as follows:

TABLE 4


Measurement Locations As Shown On FIG. 5

	116	120	98	100
Time	T/H	T/H	T/H	T/H	118 T	122 T	124 T

9:00	78/19	70/30	72.1/30	70.8/30	69.6	64.1	85.5
10:00	82/18	73/30	75.1/30	76.4/30	72.1	65	85.7
11:00	90/18	75/27	77.9/34	79.3/34	75.2	65.2	90.5
12:00	94/19	79.9/37	74.4/35	74.2/34	78.7	65.4	94.3
1:00	100/18	82.1/40	76.3/37	76.1/36	80.9	67.5	98.1
2:00	106/17	83.5/37	77.8/34	77.9/34	83.9	69.8	100.1
3:00	116/16	83.1/37	79.2/34	79.4/34	87	71.9	107
4:00	118/16	85.7/34	80.6/34	80.6/34	89.7	71.4	108
5:00	118/17	86/32	81.2/na	81.2/na	93	71.8	107.3
6:00	112/13	87/32	84.3/na	84.3/na	94.7	72.4	108

The temperature and relative humidity measurements as reported in Table 4 were repeated under higher humidity conditions commencing about 10 a.m. on a somewhat cloudy day. The system was activated by a conventional thermostat set at about 74 degrees Fahrenheit. The results are set forth in Table 5.

TABLE 5


Measurement Locations As Shown On FIG. 5

Time	116 T/H	120 T/H	98 T/H	100 T/H	118 T	122 T	124 T	Volts

10:00	86/33	78.5/44	73.6/31	73.6/31	69.2	81	12
11:00	92/27	79/49	75.7/32	75.7/32	74	68.4	88	11.6
12:00	92/23	79.5/47	76.7/31	77.1/31	75	69.3	89	11.4
1:00	95/23	80.1/47	77.4/31	77.5/31	79	71.2	97	11
2:00	97/20	80.2/45	79.6/33	79.9/32	79	74	98	9.4
3:00	98.3/20	83.0/	81.6/34	81.7/34	80	73.8	98	9.7
		30**
4:00	106/20	84.1/41	81.6/34	81.9/34	92	74.5	99	9.6
5:00	110/22	84.1/42	82.1/34	82.2/31	94	74.2	101	9.1
6:00	110/25	85/43	82.8/35	82.8/35	94	74.4	101	10.3*
7:00	102/33	85/47	81.2/35	81.7/35	91	74.2	100	10.0
8:00	96/42	83.1/47	80.1/35	79.2/35	90	73.6	96	11.1
9:00	84/42	80.1/47	76.3/36	77.1/36	89	72.5	81	12
10:00	77/44	78.1/47	74.1/34	74.7/34	87	71.1	77	12.5
11:00	75/44	76.1/47	74.0/34	74.1/34	83	69.4	74	12.5
12:00	75/44	73.1/46	73.4/32	73.4/32	79	67.1	74	12.5

A conventional 110 volt battery charger was connected to the nominal 12 volt battery system at about 6 p.m. The effectiveness of the solar battery charging system was diminished by occasional cloud cover during the day.

This relative humidity reading is reported here as recorded, but, considered in light of the contemporaneous readings at locations 116, 98, and 100, it is believed to reflect an operator or instrument error, and is not considered to be reliable. It is not reflected in relative humidity curve 120-5 in FIG. 7.
The curves in FIG. 7 are based on the data recorded in Tables 4 and 5 at locations 116 and 120 in FIG. 5. The relative humidity and temperature curves 116-4 in FIG. 7, for example, were drawn based on the data In the column headed “116 T/H” in Table 4, and curves 116-5 were drawn based on the data in the column headed “116 T/H” in Table 5. The last number following the dash indicates which Table the information for the curve is taken from.
A comparison of the temperature differences between temperature curves 120-5 and 116-5 at various relative humidity readings, as shown by relative humidity curve 116-5, indicates that the air conditioning system according to the first embodiment of the present invention is most effective at exterior temperatures above approximately 90 degrees Fahrenheit and relative humidity readings below approximately 40, and preferably below approximately 35 percent. At exterior relative humidity conditions below approximately 20 percent, temperature differences of as much as approximately 35 degrees Fahrenheit were achieved. See, for example, the differences between temperature curves 116-4 and 120-4 and relative humidity curve 116-4 in FIG. 7. While the temperature in the open shade reached almost 120 degrees Fahrenheit, the temperature in barn 64 did not reach over about 87 degrees Fahrenheit. A temperature of 120 degrees is life threatening while a temperature of 87 degrees is generally not. The efficiency of the system is best when the relative humidity is below approximately 25 percent. See, for example, how temperature curves 120-5 and 116-5 quickly converge once the relative humidity exceeds approximately 35 percent, and actually cross at approximately 45 percent relative humidity.
The last column in Table 5 reflects a drop in the voltage of the battery system during the hours of peak demand. This voltage drop is reflected in a decrease in the volume of air that the various fans are able to move through the system. Although Applicant does not wish to be bound by any theory, it appears that there is a small temperature rise (temperature curve 120-5, FIG. 7) that may be correlated with the reduced volume of air moving through the system between approximately 2 p.m. and 6 p.m. The system appears to be relatively insensitive to small changes in the volume of air flowing through the system. Preferably, the voltage should be at least approximately 11 volts for optimum operation of the fan motors. Adding another one or two solar panels to the existing three panel array on the roof of barn 64 would provide enough capacity to hold this voltage during peak demand periods.
The column headed “122 T” in Table 5 indicates the exterior temperature of the shell side of the heat exchanger. The water within the shell side is typically approximately 10 to 15 degrees Fahrenheit cooler than location 122. This affords the opportunity to provide some cooling to objects placed in heat exchange relationship with this water. If access is provided to the shell side, small objects can be cooled somewhat without the expenditure of significant additional amounts of energy. The shelf life of small amounts of heat sensitive food stuffs or medicines can be extended by placing them in heat exchanging relationship with this water. Suitable containers can be placed directly in the water on the shell side, or a cabinet accessible from the outside can be built into the shell side, or a stream of water circulated through, for example, cooling coils external to the shell side, or the like, can be utilized to effect the cooling of objects.
The column headed “118 T” in Table 5 gives a rough indication of the heat that is being radiated into the interior of the structure by the exterior walls. The column headed “124 T” provides a rough indication of the effect of cooling the interior of barn 64 on the temperature of the exterior of the walls. Clearly, a significant amount of heat is being transferred through the uninsulated walls of barn 64. Location 116 is far enough from the adjacent wall that there is very little if any influence on the indicated temperature by reason of the cooling of the interior of the barn 64. Comparison of columns 120, 98, and 100 indicates that the temperature is relatively uniform throughout the interior of barn 64.
It has been found that thermally insulating the case that encloses the heat exchanger improves the efficiency of the system by as much as 10 percent or more. The temperature of the body of water on the shell side tends to be reduced by the presence of the thermal insulation. The degree of thermal insulation is preferably such that the exterior temperature of the shell side of the heat exchanger (Table 5, column 122T) is at least 3, and preferably 5 degrees Fahrenheit warmer than the equivalent uninsulated metal exterior shell side temperature at an ambient air temperature of approximately 80 degrees Fahrenheit. Changing from a metal case (18 gauge steel) to a fiberglass (glass filament reinforced thermosetting resin) case with a thickness of approximately one-eighth inch reduces the temperature by approximately 5 degrees at about 80 degrees Fahrenheit ambient internal air temperature. The efficiency of the air conditioning system also increases. Numerous forms of insulation and methods of application are suitable for this purpose, as will be understood by those skilled in the art.
The rate of water consumption in an air conditioning, system according to the present invention is very low. For example, in the operation of the embodiment described herein with reference to FIG. 5 the rate of water consumption is no more than approximately 5 percent that of a conventional evaporative cooler (commonly described as a swamp cooler) operating under the same conditions. This low rate of water consumption is achieved even though the structure or other confined space is uninsulated, and is so unsealed that it is free to leak substantial volumes of air. In general, the rate of water consumption of a heat exchanger according to the present invention is less than approximately 10 percent, and preferably less than approximately 5 percent that of a conventional direct evaporative cooler (in a conventional evaporative cooler a single stream of air passes through a moist environment and is cooled and humidified by the evaporation of water) operating under substantially the same conditions external to the cooling systems. For comparison's sake, substantially the same external conditions comprise about the same exterior conditions of temperature and relative humidity, and the same structure or other confined space with, for example, the same volume, shape, and insulation. For purposes of comparison, the differences in the results from the operation of the cooling system of this invention as compared to the operation of a conventional evaporative cooler arises from the differences in the cooling systems, and not from the environment external to the coolers or the characteristics of the structure or other confined space. All of the variables, other than those inherent in the two cooling systems, are held constant for comparison purposes. That is, all of the external variables are held substantially constant. This low rate of water consumption is achieved while typically enjoying a humidifying efficiency (dry-bulb temperature drop across the heat exchanger divided by the maximum possible dry-bulb temperature drop as determined from a Psychometric chart) of from approximately 30 to 40 percent.
The relative humidity within the interior of an air conditioned structure according to the first embodiment of the present invention is substantially below that which would be expected from a conventional evaporative cooler. Comparison of, for example, the data in columns “116 1/H” and “120 T/H” in Tables 4 and 5 reveals that when the exterior ambient temperature exceeds approximately 95 degrees Fahrenheit, and the exterior ambient relative humidity falls below approximately 25 percent, the relative humidity within the structure is only approximately twice (200 percent) that in the exterior environment. As the exterior relative humidity falls below approximately 20 percent, and the temperature exceeds approximately 100 degrees Fahrenheit, the interior relative humidity is generally greater than approximately twice that of the ambient exterior environment, but still less than approximately 2.3 times (230 percent) that of the ambient exterior environment. These low interior relative humidities of less than approximately 50 percent are obtained while maintaining the interior ambient temperatures below approximately 85 degrees Fahrenheit despite exterior temperatures of approximately 110 to 120 degrees Fahrenheit. Typical interior relative humidities of less than approximately 60 percent are achieved according to the present invention whereas interior relative humidities in excess of approximately 60 percent are typically found with conventional evaporative coolers operated under the same conditions. This minimizes the growth of mold, and the like, as well as increasing the comfort of the occupants of the structure or other confined space. At these low relative humidities, temperatures of less than approximately 85 degrees Fahrenheit are generally comfortable for most people. As will be recognized by those skilled in the art, achieving these conditions with unsealed, uninsulated structures, and with a very low rate of water consumption using only an ambient energy harvesting system such as, for example, solar or wind energy, as described above, provides a very economical air conditioning system that is highly desirable and beneficial in many ways and for many purposes.
Variable Humidity Embodiment of the Invention:
Referring now to FIGS. 8-18, a variable humidity embodiment of the invention will be described which can be used in high temperature, low humidity environments such as that previously described, but which can also be used in higher humidity environments, including tropical or semi-tropical environments.
With reference to FIG. 8, there is shown an air conditioner 201 which is a combined direct/indirect evaporative cooler with refrigerated chilled sump water. The variable humidity device 201 shown in FIG. 8 has a number of common features with the low humidity device described with reference to FIGS. 1-7. The air conditioner 201 is preferably designed as a stacked arrangement having a top section 203, a middle section 205 and a bottom section 207. A refrigeration compressor 209 and a storage battery 211 (FIG. 9) occupy the top section 203 of the design and rest on a top shelf 213. The top shelf 213 forms the top wall of an exhaust air plenum 215. A forced-air evaporative cooling chamber (217 in FIG. 9) is located below the exhaust air plenum and occupies the middle section of the design. The cooling chamber comprises a shell plenum for the air conditioner and comprises about 65% of the total height of the unit in the particular embodiment illustrated in the drawings. A cold water sump 219 is located in the bottom of the cooling chamber. The bottom floor 223 of the cooling chamber 217 also comprises the top wall of an intake plenum 221 housing an intake fan 225. The intake fan 225 draws air upwardly through a plurality of riser tubes 227 which connect the intake plenum 221 with the exhaust plenum 215 and which pass through the cooling chamber 217.
As shown in FIGS. 10, 12 and 13, the bottom floor 223 of the cooling chamber has a plurality of openings 224 which form a lower tube sheet for the riser tubes 227. Similarly, the top shelf and wall 213 have aligned openings (214 in FIG. 13) which form an upper tube sheet. In the embodiment of the invention illustrated in FIGS. 8-15, there are approximately 49 copper tubes of approximate ¼-{fraction (3/8)} inch diameter arranged vertically within the cooling chamber 217 between the tube sheets. The sizing and arrangement of the tube bundle creates a back pressure effect during operation which acts as a self-regulating thermostat.
Water in the cold water sump 219 is refrigerated by the refrigeration compressor 209 located in the top section of the design. Cold water from the cold water sump 219 is introduced into the evaporative cooling chamber through a distribution header 229. The distribution header in FIG. 9 is a series of PVC pipes which have downwardly directed perforations. The cold water which is sprayed downwardly from the distribution header saturates an evaporative media which surrounds or otherwise contacts the riser tubes 227 in the cooling chamber 217. The evaporative media is removed for ease of illustration in FIGS. 9 and 11 but can comprise any of the media materials previously described with respect to the first embodiment of the invention. Preferably, the evaporative media is supplied as generally rectangular pads which are suspended from a rack (241 in FIG. 14) on the roof of the cooing chamber so that the pads are spaced between and separate the various vertical riser tubes 227.
Air is introduced into the cooling chamber by means of oppositely arranged fans 231, 233. The fans 231, 233 are mounted on louvers (235, 237 in FIG. 11) which can be manually adjusted to direct incoming and exhaust air from the cooling chamber 217 in a circular, vortex type flow path which creates a turbulent air flow in the cooling chamber 217 and which enhances the evaporative cooling process. The vortex effect created by the side louvers 235, 237 causes air moving through the cooling chamber 217 to have an increased residence time within the cooling chamber. This increases the cooling effect and also prevents water droplets from being blow directly out of the shell plenum. Cooled air from the cooling chamber can be discharged through a suitable duct (such as duct 239 in FIG. 8) to the interior of the structure to be cooled or can be discharged to the atmosphere.
Air is also being drawn into the intake plenum 221 by the intake fan 225, which air flow is forced upwardly through the riser tubes 227 located in the cooling chamber. The riser tubes pass though the cold water sump and also contact the evaporative media in the cooling chamber, so that the outside of the tubes are cooled. The air within the tubes 227 is cooled by conduction through the tubes. This relatively drier air can be directed through a suitable duct to the interior of the structure to be cooled and can be combined with the cooled air from the cooling chamber, if desired.
In this latter embodiment of the invention, air is being cooled using two simultaneous processes. Air is cooled by direct contact with water in the evaporative cooling chamber 217, raising the absolute humidity of the air cooled in this manner. Additional air is also being cooled by conductive heat transfer within the riser tubes 227. The absolute humidity of this additional air is either unchanged or only slightly changed, or decreases slightly, due to condensation on the inside of the riser tubes. If desired, the two air flows can be combined into a single discharge duct as described with respect to the first embodiment of the invention, so that the discharged air consists of a mixture of relatively humid air from the evaporative process and air with near ambient humidity. Control over the humidity of the discharged air can therefore be obtained by simply regulating the ratio of the two previously described air flows passing thru the exhaust duct.
The cold water sump (illustrated generally at 219 in FIG. 9) at the bottom of the cooling chamber serves as a cooling mass, as well as a sump. The water in the sump is refrigerated to near freezing by means of a commercially available, low temperature compressor similar to that used on an ice machine and which can be AC or DC operated, but is preferably operable on 12 Volt DC power. In the embodiment of the invention illustrated in FIG. 11, the compressor 209 is battery operated. However, an associated inverter 243, located within the exhaust plenum area 251 allows the unit to be operated off AC current to, for example, charge the batteries, during non-peak hours of operation. Locating the inverter within the chilled exhaust plenum compartment prolongs its life since the operating temperature is reduced. The electric fans used in the intake plenum and on the cooling chamber are also preferably 12 Volt DC fans which can be driven by solar cells or storage batteries. FIGS. 10, 11 and 16, 16A and 16B illustrate a particularly preferred refrigeration manifold 245 which is cooled by the compressor 209 using traditional mechanical refrigeration techniques. While a number of different traditional manifold or coil arrangements could be utilized with the compressor 209 to cool the water in the sump 219, the preferred manifold 245 is especially efficient for the intended application. As best seen in the isolated view of FIG. 16, the manifold 245 is a double stock manifold having a front layer 247 and a rear layer 249. The front and rear layers or coils are spaced apart by means of a plurality of cylindrical spacers 251. The cylindrical spacers 251 are less wide than the total width of the manifold, leaving a distance “d” between adjacent spacers. The cylindrical spacers are also hollow and open at both ends, allowing water in the sump 219 to flow around and through the spacers. As shown in FIG. 11, the manifold 245 is arranged in a generally horizontal plane when in place in the sump region of the cooling chamber.
Refrigerant is supplied to and returned from the manifold layers by a pair of “splits”, shown generally at 253 and 255 in FIG. 16. As shown in FIG. 16B, the top layer of coils is made up of loops 252, 254, 256, 258, 260, 262, 264, and 266. (The loops are shown as broken-away halves for ease of illustration.) The rear layer of loops is made up of loops 268, 270, 272, 274, 276, 278, 280 and 282. The loop halves 252-266 form a continuous coil on the front of the manifold. The loop halve 268-282 similarly from a continuous loop on the rear of the manifold. The points at which the front and rear loops exit or terminate (generally 266,268 in FIG. 16B) are connected by cross-over pipes 284, 286. The cross-over pipes 284, 286 intersect the first loop halves (252, 282, in FIG. 16B) to form the “splits 253, 255. The cross-over piping arrangement and the splits 253 and 255 result in a type of “interlayered flow” through the manifold. For example, refrigerant passing through the split 253 flows through branch 253B (FIG. 16) to the front layer 247 and through branch 253A to the rear layer 249. Refrigerant returning from the front and rear layers 247, 249 meets at the split 255. The double stock manifold with its split flow operation nearly doubles the cooling capacity of the compressor 209.
The following description is taken from an actual test run of the device illustrated in FIGS. 8-15, as described above. Without intending to be limiting, the following test results are intended to illustrate the features of a particularly preferred embodiment of the invention. The case or housing sections of the device were formed of stainless steel. Two 12 volt fans, installed on opposite sides of the unit were used to draw outdoor atmospheric air into the main wet chamber, referred to herein as the “wet side” of the unit. Copper tubes extended through the wet chamber and a single 12 volt fan was used to force air through the tubes on what will be referred to as the “dry side” of the unit. The air supply to the dry side came through a duct that extended into the conditioned space. The two airstreams (dry and wet side) were combined inside the unit and directed to a single outlet. The unit incorporated an integral mechanical refrigeration unit used to chill the water in the sump of the wet chamber. Batteries for 12 volt DC operation of the unit and an invertor were present to allow the operation of the unit from 120 volt AC and for charging of the batteries.
Description of the Test Unit Installation:
The test unit was set up outside an enclosed automotive repair garage in Banning Calif. The air supply for the secondary (wet) side of the unit was taken from the outdoor atmosphere. The garage was approximately 30′ by 35′ with an approximate 14′ high ceiling. The combined outlet airstream and the supply air to the primary (dry) sides of the unit were ducted through a door into the enclosed garage space. Both ducts were approximately 10′ long and straight with no turns. The duct for the combined air outlet of the unit was 10.25″ I.D. (inside diameter) and the duct for the primary (dry) side was 7.0″ I.D.
One door to the garage was left open to air for air to escape the garage and to eliminate any back pressure buildup in the garage space. For the first two tests, the unit was positioned only inches from the door. For the third test, the unit was moved back approximately 10′ from the door but the two ducts still extended through the door into the enclosed space. For all three tests, the unit was located in the shade.

Test Data and Results



Test #

1 For this test the unit was not plugged into AC power and ran off battery power.

Outdoor ambient [also secondary(wet) inlet]	79.8° F., 19% RH, 480 cfm (Ft³/Min)
Primary (dry) inlet condition	68.7° F., 28% RH, 10 cfm
Combined air outlet	63.3° F., 42% RH, 490 cfm
Air flow volume proportion	2% primary (dry) and 98% secondary (wet)
Dry-bulb temperature drop across the unit.	16.3° F. (79.6 − 63.3)
(used weighted average of primary
and secondary air inlet streams)
Theoretical maximum dry-bulb from	23.5° F. (79.6 − 56.1)
psychrometric chart.
Calculated humidifying efficiency.	69% (16.3 ÷ 23.5 × 100)
Sump water temperature	43° F.

Test #

2. For this test, the unit was plugged into AC power and was run off of the invertor.

Outdoor ambient [also secondary (wet) inlet]	79.7° F., 17% RH, 532 cfm (Ft³/Min)
Primary (dry) inlet condition	68.0 F, 30% RH, 10 cfm
Combined air outlet	63.3° F., 31% RH, 542 cfm
Air flow volume proportion	2% primary (dry) and 98% secondary (wet)
Dry-bulb temperature drop across the unit.	15.9° F. (79.5 − 63.6)
(used weighted average of primary
and secondary air inlet streams)
Theoretical maximum dry-bulb from	24.1° F. (79.5 − 55.4)
psychrometric chart.
Calculated humidifying efficiency.	66% (15.9 ÷ 24.1 × 100)
Sump water temperature	45° F.

Test #

3. Same as test #2 except the unit was moved 10′ from door as described above.

Outdoor ambient [also secondary (wet) inlet]	79.5° F., 18% RH, 532 cfm (Ft³/Min)
Primary (dry) inlet condition	68.0° F., 30% RH, 10 cfm
Combined air outlet	66.0° F., 32% RH, 542 cfm
Air flow volume proportion	2% primary (dry) and 98% secondary (wet)
Dry-bulb temperature drop across the unit.	13.3° F. (79.3 − 66.0)
(used weighted average of primary
and secondary air inlet streams)
Theoretical maximum dry-bulb from	23.8° F. (79.5 − 55.4)
psychrometric chart.
Calculated humidifying efficiency.	56% (13.3 ÷ 23.8 × 100)
Sump water temperature	46° F.

Note:
For all three tests the Calculating humidifying efficiency is based on the cfm weighted average dry bulb temperature and relative humidity % of the primary and secondary air inlet streams and the combined output conditions.

As briefly mentioned above, the water within sump region 219 of the cooling chamber of the device is typically approximately 10 to 15 degrees Fahrenheit cooler than the surrounding environment. This provides the opportunity to provide some cooling to objects placed in heat exchange relationship with this water. For example, small objects can be cooled without the expenditure of significant additional amounts of energy. Suitable containers can be placed directly in the water on the shell side, or a cabinet accessible from the outside can be built into the shell side, or a stream of water circulated through, for example, cooling coils external to the shell side, or the like. As illustrated in FIG. 14, the water sump region of the cooling chamber can be provided with one or more pairs of auxiliary refrigeration jacks 257, 259 which can be plugged or capped if not in use. The auxiliary jacks comprise an inlet and outlet point for chilled water in the sump region of the device. The chilled water can easily be pumped to another device in the structure to be cooled, such as another heat exchanger, to provide increased cooling.
FIG. 17 shows one such auxiliary refrigeration device 261. The particular device illustrated is approximately 15″ wide and 24″ high so that it can conveniently be located between the studs of a wall in a residential dwelling. Water from the sump 219 of the air conditioner 201 is sucked through conduit 263 to the intake of a fluid pump 265. Pump 265 discharges chilled water through conduit 267 to coil 269. A 12 volt DC fan 271 located behind a 12 by 12 inch coil forces air over the coil and is used to discharge cool air from the unit into the structure to be cooled. The fan can be identical to the cooling chamber fans 231 and 233 used on the main air conditioner unit. Return water is pulled through conduit 273 back to the pump 265 and recirculated by the pump back to the sump 219 of the main unit through the outlet conduit 275 to be once again chilled by the mechanical refrigeration system of the main unit. A catch pan 274 can also be provided to catch any condensation. In one embodiment of the invention, the inlet and outlet water conduits 263, 275 are packaged into a “cable” arrangement (FIG. 18) having an outer sheath of, for example a suitable polyolefin. The cable 277 could also contain a suitable shielded DC power supply line, illustrated as 279 in FIG. 18, for powering the fan 271 and pump 265.
Those skilled in the relevant arts will understand that various changes and modifications may be made in the preferred embodiments of the invention described above. Typical cooling systems according to the present invention employ a heat exchanger with wet and dry sides that are preferably substantially hermetically sealed from one another. The water supply system on the wet side of the heat exchanger is generally provided primarily to humidify the air on the wet side. As is well understood by those skilled in the art with respect to conventional evaporative coolers, the liquid water on the wet side is divided or distributed by means of a spray or a wetted pad, or the like, so as to increase the surface area of the water, and, thus, the rate of evaporation of the water. Some chilling of the water on the wet side also necessarily occurs.
While the present invention has been described with reference to specific embodiments wherein the shell side of a heat exchanger is the wet side and the tube side is the dry side, those skilled in the art will readily appreciate from a consideration of these teachings that other arrangements are possible, including, for example, the use of a wet tube side and a dry shell side, or the like. Also, those skilled in the art will be taught by the teachings herein that other forms of heat exchangers other than shell and tube can be employed, if desired.
What have been described are preferred embodiments in which modifications and changes may be made without departing from the spirit and scope of the accompanying claims. Many modifications and variations of the present invention are possible in light of the above teachings. It is therefore to be understood that, within the scope of the appended claims, the invention may be practiced otherwise than as specifically described.

Claims

1. A cooling assembly comprising:

a heat exchanger, said heat exchanger including a case member enclosing a wet side in heat exchange relationship with a dry side, said sides being substantially hermetically sealed from one another;

a first air moving member adapted to move air through said dry side to produce a cooled stream of air;

a liquid distributing member within said wet side;

a liquid sump element associated with said wet side and adapted to receive liquid from said wet side and to make said liquid available to said liquid distributing member;

at least two additional air moving members adapted to move air through said wet side from different locations to produce a humidified mass of turbulent air on said wet side;

a mechanical refrigeration unit including a compressor and an associated refrigeration manifold, the refrigeration manifold being located within the liquid sump element for refrigerating liquid contained therein; and

an exhaust duct for conveying cooled air from the dry side of the assembly to the interior of a structure to be cooled.

2. The cooling assembly of claim 1, including an additional conduit which combines the cooled air from the dry side of the assembly with the turbulent air from the wet side and delivers the resultant combined streams to the interior of a structure.

3. The cooling assembly of claim 1, further comprising a DC power source for powering the first and additional air moving members, the DC power source including one or more storage batteries.

4. The cooling assembly of claim 3, further comprising an ambient energy harvesting system operatively associated with the storage batteries for charging the storage batteries.

5. The cooling assembly of claim 3, wherein the DC power source supplies all of the power needs for the cooling assembly.

6. The cooling assembly of claim 4, further comprising an electrical inverter which allows the storage batteries to be charged by an AC power source.

7. The cooling assembly of claim 4, wherein the ambient energy harvesting system includes at least one solar cell.

8. A cooling assembly for cooling the interior of a structure, the assembly comprising:

a heat exchanger, said heat exchanger having a shell side and a tube side;

a first air moving member adapted to move air through said tube side to produce a cooled, relatively dry stream of air;

a liquid dispensing member on said shell side adapted to distribute liquid substantially throughout said shell side;

a liquid sump element associated with said shell side and adapted to receive said liquid from said shell side and to make said liquid available to said liquid dispensing member;

a plurality of air moving members adapted to move air through said shell side from different directions to produce a turbulent mass of air on said shell side;

9. The cooling assembly of claim 8, wherein the tube and shell side air moving members all require electrical power for their operation, the cooling assembly further comprising a battery system, the battery system being adapted to supplying all of the required electrical power for operation of the assembly; and

a solar cell system chargingly associated with the battery system.

10. The cooling assembly of claim 8, further comprising:

a water supply system associated with the liquid sump and liquid dispensing member on the shell side of the assembly, the water supply system including a water pump positioned between the liquid sump and the liquid dispensing member for maintaining the shell side of the assembly wet with water.

11. A cooling assembly for cooling the interior of a structure, the cooling assembly comprising:

a stacked chamber arrangement having a centrally located, forced-air evaporative cooling chamber which separates an exhaust air plenum located above the cooling chamber from an air intake plenum located below the cooling chamber, the cooling chamber having a top wall and a bottom wall and surrounding sidewalls and a plurality of vertically arranged riser tubes which connect the intake plenum with the exhaust air plenum, the bottom wall creating a cold water sump region;

an intake fan, located within the air intake plenum, for drawing air upwardly through the plurality of vertical riser tubes which connect the intake plenum with the exhaust air plenum to thereby produce a cooled stream of air;

a liquid distributing member located in the cooling chamber adjacent the top wall thereof;

a pump for pumping water from the sump region of the cooling chamber to the liquid distributing member;

a pair of oppositely arranged fans mounted on the cooling chamber sidewalls for moving air through the cooling chamber from different locations to produce a humidified mass of turbulent air within the cooling chamber;

a mechanical refrigeration unit including a compressor and an associated refrigeration manifold, the refrigeration manifold being located within the sump region of the cooling chamber for refrigerating water contained therein; and

an exhaust duct for conveying cooled air from the exhaust plenum of the assembly to the interior of a structure to be cooled.

12. The cooling assembly of claim 11, wherein the oppositely arranged fans on the cooling chamber sidewalls are mounted over louvers, the louvers being adjustable to direct air in a circular vortex within the cooling chamber, thereby contributing to the turbulence of the air within the cooling chamber.

13. The cooling assembly of claim 11, wherein the vertically arranged riser tubes located within the cooling chamber are copper tubes which are less than about ½ inch in diameter.

14. The cooling assembly of claim 13, wherein the vertically arranged riser tubes are in the range from about ¼ to {fraction (3/8)} inches in diameter.

15. The cooling assembly of claim 11, wherein the refrigeration manifold is a double stock manifold having a front coil layer and a rear coil layer, the front and rear coil layers being spaced apart by means of a plurality of cylindrical spacers.

16. The cooling assembly of claim 15, wherein the cylindrical spacers are less wide than the total width of the manifold, leaving a distance between adjacent spacers, and wherein the cylindrical spacers are also hollow and open at both ends, allowing water in the sump region to flow around and through the spacers.

17. The cooling assembly of claim 16, wherein the double manifold is arranged in a generally horizontal plane within the sump region and wherein the front and rear coil layers of the double manifold contain a pair of flow path splits which act to distribute refrigerant which is communicated from the compressor to the coils.

18. A direct/indirect evaporative cooling assembly with refrigerated chilled water sump for cooling the interior of a structure, the cooling assembly comprising:

a stacked chamber arrangement having a centrally located, forced-air evaporative cooling chamber which separates an exhaust air plenum located above the cooling chamber from an air intake plenum located below the cooling chamber, the cooling chamber, intake plenum and exhaust plenum comprising a shell and tube heat exchanger which encloses a wet side in heat exchange relationship with a dry side, the sides being substantially hermetically sealed from one another; the cooling chamber having a top wall and a bottom wall and surrounding sidewalls and a plurality of vertically arranged riser tubes, the bottom wall creating a cold water sump region as well as the top wall of the air intake plenum and a lower tubesheet for the riser tubes, the top wall of the cooling chamber forming the bottom wall of the exhaust air plenum and an upper tubesheet for the riser tubes;

an intake fan, located within the air intake plenum, for drawing air upwardly through the plurality of vertical riser tubes which connect the intake plenum with the exhaust air plenum to thereby produce a cooled stream of air from the dry side of the assembly;

a liquid distributing member located on the wet side of the cooling chamber adjacent the top wall thereof;

a pair of oppositely arranged fans mounted on the cooling chamber sidewalls for moving air through the wet side from different locations to produce a humidified mass of turbulent air on the wet side;

19. The cooling assembly of claim 18, including an additional conduit which combines the cooled air from the dry side of the assembly with the turbulent air from the wet side and delivers the resultant combined streams to the interior of a structure.

20. The cooling assembly of claim 18, further comprising a DC power source for powering the intake and additionally arranged fans, the DC power source including one or more storage batteries.

21. The cooling assembly of claim 20, further comprising an ambient energy harvesting system operatively associated with the storage batteries for charging the storage batteries.

22. The cooling assembly of claim 20, wherein the DC power source supplies all of the power needs for the cooling assembly.

23. The cooling assembly of claim 18, further comprising an electrical inverter which allows the storage batteries to be charged by an AC power source.

24. The cooling assembly of claim 21, wherein the ambient energy harvesting system includes at least one solar cell.

25. The cooling assembly of claim 18, wherein the refrigeration compressor is a DC compressor which is located in a storage area on top of the exhaust plenum of the assembly.

26. The cooling assembly of claim 18, wherein the liquid distributing member includes a distribution header located in the cooling chamber adjacent the top wall thereof, and wherein the cooling chamber further includes pads of evaporative media arranged in the chamber between the vertical riser tubes to surround and contact the tubes, whereby cold water is introduced from the sump region of the cooling chamber and pumped through the distribution header onto the evaporative media to thereby cool the riser tubes in the cooling chamber.

27. The cooling assembly of claim 18, wherein the compressor and refrigeration manifold are operated to cool the water in the sump region to near freezing temperature.

28. The cooling assembly of claim 18, wherein an electrical inverter is located within the exhaust plenum of the assembly which allows the unit to be operated off AC current, the location of the inverter within the chilled exhaust plenum serving to prolong its useful life by lowering its operating temperature.

29. A cooling assembly for cooling the interior of a structure, the cooling assembly comprising:

an evaporative media located in the cooling chamber surrounding and contacting the vertical riser tubes, the evaporative media being wet by water pumped through the liquid distributing member;

a mechanical refrigeration unit including a compressor and an associated refrigeration manifold, the refrigeration manifold being located within the sump region of the cooling chamber for refrigerating water contained therein;

an exhaust duct for conveying cooled air from the exhaust plenum of the assembly to the interior of a structure to be cooled;

wherein the cooling chamber has a pair of auxiliary refrigeration jacks which comprise an inlet and outlet point for chilled water in the sump region of the assembly; and

wherein the auxiliary refrigeration jacks are connected by a suitable conduit to an auxiliary heat exchange device located at a remote location within the structure to be cooled.

30. The cooling assembly of claim 29, wherein the auxiliary heat exchange device is a housing containing a fluid pump, a heat exchange coil and a fan, water from the cold water sump of the cooling assembly being pumped through the coil and circulated back to the sump, the fan creating an exhaust air flow over the coil to provide additional cooling to the structure.

31. The cooling assembly of claim 30, wherein the pump and fan both operate off DC power, and wherein the conduit which connects the auxiliary heat exchange device to the cooling assembly also has associated therewith a power line for supplying DC current from the main cooling unit to the auxiliary heat exchange device.

32. The cooling assembly of claim 31, wherein the inlet and outlet water conduits and DC power line are all contained within a common sheath which is run from the main cooling assembly to the auxiliary heat exchange device.