JP2008516188A - Cooling assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a low power air conditioner suitable for air conditioning a structure which is not sealed and insulated in a high temperature and low humidity environment.
An apparatus for air-conditioning the inside of a structure that is operated by a DC power source such as a storage battery. A shell and tube heat exchanger is combined with a mechanical refrigeration system and comprises a wet shell side and a dry tube side of the device. In the operation of the air conditioner, a large amount of distributed water is provided on the shell side, the atmosphere flow passes through the dry tube side, and a dry and cooled air flow is generated. Most cooled air is mixed or sent separately, depending mainly on the humidity of the ambient environment being cooled.
[Selection] Figure 11

Description

  The present invention relates to a low-power air conditioner system, and in particular, a low-power air conditioner using a shell-and-tube heat exchanger for use in a dry state, or sampled water cooled for use in other environments. The present invention relates to a direct / indirect evaporative cooler using

  In certain embodiments, the present invention provides air conditioning for structures that are installed in desert-like dry and hot environments. Such environmental control is necessary to lead a high quality of life, and sometimes necessary to maintain life. This is true for both humans and livestock.

  In desert environments, daytime temperatures often rise above 100 degrees Fahrenheit (38 ° C.), while humidity is often below 20%. A so-called “Swamp cooler”, which is a conventional air conditioning system based on evaporative cooling, is effective because it is in an environment with low humidity. In order to operate such systems, a power source is required, and the cost that can be used to operate them is limited. Conventional evaporative coolers consume a large amount of water, but the area where water can be used is limited. In a desert environment, a sufficient amount of water is not always available. Other types of air conditioning systems require the building to be sealed, expensive, expensive to maintain, and expensive to operate. Houses, especially buildings for livestock, are not sealed or insulated and nothing prevents the interior of such buildings from reaching thermal equilibrium with the external environment. In general, an air conditioning system is not provided in such a building because of the operating cost of the air conditioning system in such a building and the lack of effectiveness. Most air conditioning systems are powered by electricity, but depending on where the building is built, electricity is not always available or inexpensive. If an effective and simple built-in air conditioning system that can be operated at low cost in an unsealed building can be provided to the desert environment, it is very beneficial for both humans and livestock. In addition to the advantages described above, air conditioning systems powered by batteries or solar panels, or both, or cheaper direct currents can operate in a wider range of humidity, including tropical and subtropical areas.

  In addition, such air conditioning systems can utilize both relatively humid and relatively dry airflow, and can selectively route the airflow within the building to be cooled. . Then, by combining these airflows according to a predetermined ratio or selection, for example, only a relatively dry airflow can be sent to a space where the humidity is high and it is desired to cool.

  The simplest form of evaporative cooling of a building is achieved by blowing water fog or mist into a moving air stream (for example, Patent Document 1). One problem with this system is that the humidity is too high in the building, generating algae and bacteria. In order to minimize these problems, in Patent Document 1, an exhaust fan is provided at the other end of a wide space from the spray nozzle provided at one end of the building. The proportion of water consumed is very high. More than 95% of the water supplied to the spray nozzle is consumed. The vaporization cooling system of Patent Document 1 is said to produce a temperature effect of about 20 degrees.

  The conventional evaporative cooling system has been combined with a complicated system including a heating means (for example, Patent Document 2). Conventional evaporative cooling systems have also been combined with complex systems having a cooling air system (eg, US Pat.

An air conditioner having two air flow paths, that is, an inlet path for inputting external air and an outlet path for discharging stagnant air has been disclosed (for example, Patent Document 4). The heat exchanger precools fresh air with the heat removed from the stagnant air, which is further cooled by a vaporization cooler across the two airflow paths. Matters concerning these problems are recognized as necessary for improving the air conditioning system.
US 5,146,762 US 4,773,471 US 5,911,745 US 6,434,963

In one embodiment, an air conditioning assembly according to the present invention includes a shell and tube heat exchanger, in which outside air is forced to pass through the shell side and the tube side for cooling, inside the structure. Released at the same time. For convenience, the airflow from both sides is mixed into one airflow before being released into the structure or separated into the structure. This heat exchanger is particularly suitable for use in high temperature and low humidity conditions, such as those found during the hot summer months in desert areas. The air conditioning assembly is particularly effective in situations where the temperature is above about 80 degrees Fahrenheit (27 ° C.) and the relative humidity is about 40% or less, more preferably about 35% or less. The assembly may operate properly even in conditions where the air-conditioned structure has an opening through the structure and is not tightly sealed. The structure basically does not block airflow, for example, from 6 square inches (0.004 m ² ) to 1 or 2 square feet (0.09 to 0.18 m ² ). The air conditioning system according to the present invention having high efficiency, reliability, economy, simplicity, and effect can be provided in a warehouse, a tent, a temporary structure, or the like. The air conditioning system according to the present invention does not require a complicated or effective device to perform its function, is easy to transport, and can be assembled inside a temporary structure such as a tent.

  The shell side of the heat exchanger is preferably wetted with a liquid such as water or drops dripped down, and the airflow passes through the shell side as turbulent flow. The airflow passing through the tube side is cooled by coming into contact with the wall of the tube and discharged to the outlet. Preferably, the airflow from the shell and tube side is mixed and discharged into the interior to cool the structure. If necessary, the air stream is mixed after being released into the structure. Preferably, the intake and release of the airflow are all performed inside the structure.

  In other embodiments, the present invention constitutes a direct / indirect evaporative cooler that uses cooled cold sump water. The cooler is preferably designed in a stacked arrangement. The refrigeration compressor and storage battery occupy the top area of the structure and are based on the top shelf. The top shelf forms the upper wall of the exhaust plenum. The forced evaporative cooling chamber located below the exhaust plenum occupies the middle region of the structure and constitutes about 65% of the total unit height in the embodiment. The cold water sump and the intake plenum occupy the lower layers of the cooling chamber. The lower layer of the cooling chamber also includes the upper wall of the intake plenum that houses the intake fan. The intake fan connects the intake plenum and the exhaust plenum, and draws air upward through a plurality of rising tubes that pass through the cooling chamber.

  The water in the cold water sump is cooled by a refrigeration compressor located in the upper region of the structure. Cold water from the cold water sump passes through the distribution header and is introduced into the vaporizer cooler chamber. The cold water saturates the evaporation medium around or in contact with the riser tube in the cooling chamber. Air is introduced into the cooling chamber by opposed fans mounted on the side walls of the cooling chamber to generate turbulence in the cooling chamber. The fan enhances the evaporative cooling process. Cooled air from the cooling chamber is discharged through a suitable duct into the interior of the structure to be cooled.

  Air is also drawn into the intake plenum by an intake fan that directs air flow up the cooling chamber and through the tube and up. As the riser tube passes through the cold water sump and contacts the evaporation medium in the cooling chamber, the outside of the tube is cooled. The air inside the tube is cooled by heat transfer from the tube. This relatively dry air is directed through a suitable duct into the interior of the structure to be cooled, and if necessary, mixed with wetter cooling air from the cooling chamber.

  In the latter embodiment according to the invention, the air is cooled by two simultaneous processes. In this method, air is cooled by direct contact with water in the evaporative cooling chamber, increasing the absolute humidity of the cooled air. The additional air is also cooled by conductive heat transfer inside the riser tube. If necessary, the two air streams are mixed in the discharge duct and the discharged air consists of a mixture of relatively humid air from the evaporation process and air close to external humidity. The cold water sump at the bottom of the cooling chamber acts as a cooling group, similar to the water storage sump. The water in the sump is cooled to a temperature near the freezing point by a low-temperature compressor similar to that used in ice makers. The compressor can be operated with an AC or DC power source. The electric fan used in the intake plenum of the cooling chamber is preferably a DC fan driven by a solar cell or a storage battery.

  In high humidity environments, the additional refrigeration manifold may be placed in the wet chamber around the discharge outlet from the wet chamber. The additional refrigeration manifold may be supplied with refrigerant from a conventional mechanical refrigeration system used to cool the sump water in the wet chamber. The pump downstream valve controls the flow of refrigerant to the additional manifold so that the manifold is cooled only when the opposed fans mounted on the side walls are operating.

  The air entering the wet chamber is connected by a duct to introduce outdoor air or to introduce room air from the lower dry chamber of the assembly. The air conditioning assembly may be installed inside a room having a ceiling vent that is used to move stagnant air into the attic space for subsequent discharge of the cooled structure to the outside.

  Other objects, advantages and novel aspects of the present invention will become apparent upon consideration of the following detailed description of the invention and the accompanying drawings.

  Two different preferred embodiments according to the invention will be described in detail.

<Low humidity air conditioner>
Reference is made to the figures which contain reference numerals designated individually or through corresponding parts in several figures. 10 is a shell-and-tube heat exchanger, which is hermetically sealed, especially in high temperature and low humidity conditions. Represents a low power air conditioning unit used in a structure that is not included. A plan view of such a structure is shown at 64 in FIG.

  The heat exchanger 10 is surrounded by the outer case 62. The outer case 62 is shown as a rectangle for the purpose of explanation, and other shapes such as an arc, a circle, and a cylinder are also contemplated within the scope of the present invention. Air, preferably internal air from near the ceiling of the structure to be cooled, is drawn through the inlet port 12 to the intake plenum 14 of the heat exchanger 10 to the tube side of the heat exchanger. Air is drawn into the inlet port 12 by the exhaust fan 46. Air is drawn from the intake plenum 14 through the heat exchange tube 34 and into the exhaust plenum 18. The tube inlet end 36 is hermetically provided on the inlet tube plate 60, and the tube outlet end 38 is hermetically provided on the outlet tube plate 32. The exhaust fan 46 exhausts air from the tube side of the heat exchanger to the exhaust line 22 on the tube side.

  The shell side of the heat exchanger 10 has a shape of a shell plenum 16 that surrounds the heat exchange tube 34 between the inlet tube plate 60 and the outlet tube plate 32. The heat exchange tube 34 is shown in a straight line for clarity of explanation, but other shapes such as coils or loops may be used as the heat exchanger tube, as will be appreciated by those skilled in the art. You can also. A liquid body, preferably water, is disposed on the shell side of the heat exchanger 10. The surface of the liquid is 50. The liquid occupies less than half of the volume on the shell side of the heat exchanger, preferably less than ¼. The bottom of the shell plenum 16 forms a liquid sump where liquid is present. At least one or more, preferably at least two or more fans are provided to push ambient internal air from the structure to the shell plenum 16 of the heat exchanger 10. As shown in FIG. 1, three shell side input fans 40 (first input fan), 42 (second input fan), and 44 (third input fan) are provided. These fans simultaneously generate substantial turbulence in the air on the shell side of the heat exchanger 10. The air from the shell plenum 16 is exhausted from the heat exchanger 10 through the shell side exhaust pipe 20.

  The liquid in the sump in the shell plenum 16 is sprayed over the heat exchange tube 34. As shown in FIG. 1, one form of the spray system includes a pump feed line 26 that is used to transport liquid from a shell-side liquid sump to a liquid pump 24. The pump 24 supplies energy to the liquid and discharges the liquid through the pump discharge pipe 28 to the spray head 30 that sprays upward on the shell side of the heat exchange tube 34. The spray head 30 is not essential for the operation of the present system, but is generally installed at or near the top of the shell-side plenum. FIG. 1 is schematically illustrated on the side of the shell side plenum for ease of explanation. The liquid flows down into the liquid sump so that it can be recycled again. The liquid spray rapidly increases the humidity of the air in the shell plenum 16 and enhances heat exchange between the heat exchange tube 34 and the liquid. Preferably, the liquid level is automatically maintained at approximately a constant level by connecting a prior art float actuated valve to the liquid source (not shown).

  For example, the heat exchange between the liquid and the heat exchange tube 34 is physically performed on the heat exchange tube 34 such as a tube-shaped blanket 48 (see FIG. 4) or a slack mesh-shaped sheet member 104 (see FIG. 6). This can be further enhanced by the use of a member covering the tube placed in contact with the tube. Also, the humidification of the air in the shell plenum 16 is enhanced by the presence of some form of covering member. The covering member holds the liquid against the heat exchange tube 34 and increases the surface area of the liquid in the shell plenum 16. In general, the covering member is made of an inactive reticulated substance through which a liquid or vapor phase liquid easily flows. Many such reticulated materials are known, for example, many natural and synthetic vent foams, felts, stuffing, woven fabrics and the like. Conventional commercially available swamp cooler pads are generally suitable for use as covering members. Such members often have antibacterial and antibacterial properties. The covering member can cover the heat exchange tube 34 in whole or in part as desired. As an example, refer to FIGS. The covering member is not shown in FIGS. 1, 2 and 3 for the purpose of clarifying the explanation, but is preferably used in some form.

  Various liquid spray systems are used. A generally effective system is shown in FIG. For example, liquid from a suitable liquid source, such as a liquid sump of the shell plenum 16, is supplied to the spray header 52 under pressure and distributed to the spray header branch 56. The liquid pours from the spray port 54. Preferably, the spray header 52 is provided at the upper end of the shell plenum 16, generally adjacent the outlet tube plate 32, so that the liquid flows down over the heat exchange tubes 34 and the combined sheathing member. , 42 and 44 are affected by the turbulent airflow.

  The air exhausted from the tube side through the exhaust line 22 is preferably mixed with the air exhausted from the shell side through the exhaust line 20. The mixed air stream passes through the mixed exhaust line 58 and is released to the internal outside air of the structure to be cooled.

The currently planned best mode for the first embodiment of the present invention is described in particular in FIGS. The unpainted warehouse 64 has a rectangular shape that is approximately 30 feet (9.1 m) wide and 50 feet (15.2 m) long. The warehouse 64 is arranged such that the major axis of the warehouse 64 is along the east and west, as indicated by the letters N, S, E, and W described in FIG. The warehouse 64 has an eaves-free eaves metal roof and a bare two-by-four large wooden wall with a stucco exterior finish. The tip of the roof is about 10 feet (3.0 m) from the floor and the height of the outer wall is about 8 feet (2.4 m). The internal volume of the warehouse 64 is approximately 13,5000 cubic feet (3,820 m ³ ). The outer doors do not block the outside air, and all of the unsealed areas around the outer doors 66, 68, 70, 72 and 74 are approximately 1-2 square feet (0.1-0.2 m ^2). ). There is no large pressure difference between the warehouse interior 64 and the external environment, and the humidity difference between the warehouse interior 64 and the external environment quickly reaches equilibrium. The partition walls 82, 84, 86 and 88 are half the height of the ceiling, and the room dividers extend up to 6 inches (0.15m) to the roof. . The inner gate 76 is an inspection gate for a screen door that extends straight.

  The air conditioning system used for the warehouse 64 includes a shell and tube heat exchanger 10, a mixed exhaust line 58, an air distribution chamber 92, air distribution branches 94 and 96, and air outlet heads 98 and 100. . The input fans 42 and 44 supply outside air from the inside of the warehouse 64 to the shell plenum of the heat exchanger 10. Air is drawn into the shell side of the heat exchanger from a height generally lower than the height at which the air is released from 98 and 100. Moreover, it is preferable that air is drawn into the tube side of the heat exchanger from the hottest portion of the structure near the ceiling that is not insulated. The air exhausted from the tube side of the heat exchanger 10 through the tube side exhaust pipe 22 is mixed with the air exhausted from the shell side through the pipe line 20 and passed through the mixed exhaust pipe 58. Flow into the distribution chamber 92. The air flow is then split and flows through each air distribution branch 94, 96 to each air outlet head 98, 100. Air is drawn into the tube side of the heat exchanger 10 through the inlet port 12. A blanket member 104 (FIG. 6) in the form of a foam pad of a conventional swamp cooler is in contact with the tube. The spray head of the general form shown in FIG. 3 is arrange | positioned at the upper part of the shell plenum of the heat exchanger 10. FIG. It is preferable that 1/4 or less of the shell plenum is filled with water.

The rectangular outer case of the heat exchanger 10 is approximately 2 feet long (0.61 m), 2 feet wide (0.61 m) and 3 feet high (0.91 m), and is installed on the floor of the warehouse 64. Yes. The input fans 42 and 44 mounted on opposite sides of the case have a diameter of 14 inches (0.36 m), rotate 2,200 times per minute, and have an operating voltage of 12 V DC. The rated current of the fan is 4A. The tube-side exhaust fan 46 (FIG. 1) has a diameter of 12 inches (0.31 m) and an operating voltage of 12 V DC. The rated current of the fan is 4A. These fans are conventional vehicular devices and are typically used in combination with conventional radiator cooling systems to draw air into the internal combustion engine liquid cooling radiator. The liquid pump 24 (FIG. 1) has a 12V, 7A DC motor with a rated flow rate of 28 gallons per hour (106 L). The size of the tube-side intake plenum 14 (FIG. 1) is 6 inches (0.15 m) high, 24 inches (0.61 m) long, and 24 inches (0.61 m) wide. The size of the tube side exhaust plenum 18 (FIG. 1) is 6 inches (0.15 m) high, 24 inches (0.61 m) long, and 24 inches (0.61 m) wide. The size of the shell side plenum 16 (FIG. 1) is approximately 24 inches (0.61 m) in length, 24 inches (0.61 m) in width, and 24 inches (0.61 m) in height. The heat exchange tube 34 is a standard 3/4 inch (1.9 cm) diameter cylindrical copper tube having a length equivalent to that between 24 inch (0.61 m) square tube sheets 32 and 60. 100 heat exchange tubes 34 are regularly arranged in a rectangular shape. The total surface area of the tube 34 within the shell plenum 16 is approximately 6,600 square inches (4,3 m ² ). The intake port 12 on the tube side of the heat exchanger has a diameter of about 6 inches (0.15 m), similar to lines 20 and 22. The intake port 12 is open upward and is provided approximately 4 inches (0.10 m) below the uninsulated metal roof of the warehouse 64. Therefore, the hottest atmosphere inside the warehouse 64 can be acquired. The mixed exhaust line 58 is placed overhead, similar to the air distribution branches 94 and 96. The diameter of the conduit 58 is about 8 inches (0.20 m) and the length is about 14 feet (4.3 m). Each air distribution branch is about 10 feet (3.0 m) in length and about 6 inches (0.15 m) in diameter. The distribution chamber 92 is approximately 2 feet long, 2 feet wide, and 2 feet high (0.6 m long, 0.6 m wide, 0.6 m high). The length of the short portion of the conduit 58 that connects to the distribution chamber 92 is about 3 feet (0.91 m). Air outlet heads 98, 100 are provided approximately 9 feet (2.7 m) above the floor and discharge downward.

  A pump and a fan are provided in the place shown by 106, for example, and have a direct-current motor which receives electric power by a general 12V deep cycle lead acid battery (secondary accumulator) in which five are connected in parallel. The battery is connected to three common 30 V, 4 Ah solar panels 110, 112, 114 through a general charging circuit 108. The solar panel is attached to the slope facing the south side of the roof of the warehouse 64. No other energy source is needed in the operation of the daytime air conditioning system. If necessary, a common AC converter may be used to charge from a 110V household power source or other commercially available power source. This is not required, and using it alone in a region where commercial utilities are available increases operating costs. Similarly, the motors used for fans and pumps can be replaced by motors that can be powered by power from general commercial utility services, but the operating costs increase and the flexibility of the system decreases.

  The liquid sump water level is preferably maintained at about 5 inches (0.13 m). At this water level, the liquid sump contains approximately 1.67 cubic feet (47.3 L) of water. The shell side plenum has a volume of about 8 cubic feet (226.5 L), and water accounts for about 21% of the volume of the shell side plenum 16. This is the amount of water needed to continue operation for more than one day. If necessary, the volume of the liquid sump can be varied in the range of about 10-30% by volume of the shell-side plenum chamber 16. The liquid sump need not be provided inside the shell side plenum chamber. An external liquid sump that is several times larger than the shell-side plenum can be used if necessary for unattended operation without water supply for at least a week. Less than one gallon (3.8 L) of water is consumed during normal summer days.

  Warehouse 64 is a desert area where the daytime temperature is over 100 degrees Fahrenheit (38 ° C) for several months in the summer, the relative humidity is often less than 20%, and the sun is shining for most of the daytime. Is installed. Without air conditioning, the daytime temperature inside the warehouse 64 is approximately 10 degrees Fahrenheit (corresponding to 5.6 degrees Celsius) higher than the outside temperature.

  The operation of the air conditioning system in the warehouse 64 is automated by a general thermostat (not shown) connected to a fan and pump circuit. The thermostat is set to 74 degrees Fahrenheit (23 ° C.), for example, and the system is operated early in the morning on a normal summer day, and is maintained until the evening.

  The preferred air conditioning assembly according to the present invention is fully self contained. The power supply to the fan and pump motors is provided at the same location as the system. The water supply to the shell side of the heat exchanger is performed automatically by a float operating valve provided in the water supply or manually as required. Even in regions where water supply is unstable, manual replenishment may be performed at long intervals because of the slow water consumption rate.

  Since the power required is small, a low voltage (12 or 24V) battery system combined with a typical solar panel driving the charging circuit is sufficient to power the daytime system. Because of the benefits of using a battery system that is charged by a common solar panel and the wide availability of such an inexpensive system, a wide variety of structures can be unconditionally air conditioned. Even in a livestock barn, it is possible to implement highly reliable and inexpensive air conditioning by the present invention. In addition, it is possible to air-condition a house where a fund for air-conditioning is restricted or a house where a house is poorly sealed and a person who is not insulated is living. The battery system can be charged by a wind turbine in an area where a certain amount of airflow is available. If necessary, other alternative energy sources can be utilized. Combinations of solar panels, wind turbines, and other types of alternative energy sources are suitable for use in charging battery systems. Alternative energy sources generally cannot deliver constant energy, but since the motors used in the system basically require a constant energy source, a battery is provided between the energy source and the air conditioning system. It is desirable. If the alternative energy source is available as a constant energy source, the use of the battery system becomes additional.

  The air conditioning system according to the present invention is operated at 6:30 in the morning of a general summer day in the warehouse 64 and is operated all day. The internal temperature of the warehouse 64 is measured at location 102 (FIG. 5), which is 4 feet (1.2 m) above the ground, and the external temperature is at location 116, which is shaded under the awning adjacent to the south side of the warehouse 64. Measured. Position 116 is at a height of 5 feet (1.5 m) above the ground supporting a 20 foot (6.1 m) wide awning (not shown). The wooden awning is attached to the warehouse and extends approximately 20 feet (6.1 m) outward from the top of the warehouse 64 wall. The wooden awning is fully open on three sides, and the temperature at location 116 is approximately the same as the internal temperature of warehouse 64 without the air conditioning system. The measured temperatures are shown in Table 1 below.

  It was observed that the temperature difference between the interior and exterior was maximized when the humidity was at a minimum and the exterior temperature exceeded 100 degrees Fahrenheit (38 ° C.).

  In summer, when most of the sky was covered with clouds and the relative humidity was about 35% or more, the conditions shown in Table 2 below were observed.

  Relative humidity measurements were taken at various locations inside and around warehouse 64 from 9:00 am in summer. Table 3 shows the measurement results at the positions indicated by the numbers shown in FIG.

  The relative humidity is basically stable and constant throughout the day at all locations within the structure.

  Beginning at 9:00 am, temperature and relative humidity (T / H) were measured throughout the sunny day at various locations within and adjacent to the warehouse 64. Measurements at positions 118 and 120 were taken at about 5 feet (1.5 m) above the floor. Location 118 is used to show the effect of radiation from the outer wall. Location 124 is on the north side of warehouse 64 and is about 5 feet (1.5 m) above the ground. The measurement results are shown in Table 4 below.

  The temperature and relative humidity measurements listed in Table 4 started at 10:00 am on a slightly cloudy day and were repeated under high humidity conditions. The results when the system was operated using a typical thermostat set at approximately 74 degrees Fahrenheit (23 ° C.) are shown in Table 5.

  (* In Table 5) A general 110V battery charger is connected to a 12V battery system from around 6:00 pm. The effectiveness of the solar battery charging system is reduced by occasional cloudiness during the day.

  (** in Table 5) This relative humidity is listed here as data, but considering simultaneous data at positions 116, 98 and 100, it is considered an operator or device error. , Not reliable. Therefore, it is not reflected in the relative humidity curve 120-5 described in FIG.

  The curves in FIG. 7 are based on the data described in Tables 4 and 5 at positions 116 and 120 in FIG. For example, the relative humidity and temperature curve 116-4 of FIG. 7 is drawn based on the data in the column heading “116T / H” in Table 4, and the curve 116-5 is the column heading “116T / H” in Table 5. "Is drawn based on the data. The last number following the syllabary represents the table from which the curve information was obtained.

  The comparison of the temperature difference between the temperature curve 120-5 and the temperature curve 116-5 at various relative humidity levels represented by the relative humidity curve 116-5 is the same as that of the air conditioning system according to the first embodiment of the present invention. It is shown that it is most effective when it is over about 90 degrees Fahrenheit (32 ° C.) and the relative humidity is about 40% or less, preferably 35% or less. When the external relative humidity was 20% or less, a temperature difference of approximately 35 degrees Fahrenheit (corresponding to 14 degrees Celsius) was achieved. For example, refer to the difference between the temperature curves 116-4 and 120-4 in FIG. 7 and the relative humidity curve 116-4. The outdoor shade temperature has reached about 120 degrees Fahrenheit (49 ° C), but the temperature in the warehouse 64 has not reached about 87 degrees Fahrenheit (31 ° C). 120 degrees Fahrenheit (49 ° C) is life-threatening, but 87 degrees Fahrenheit (31 ° C) is generally not a problem. The efficiency of the system is best when the relative humidity is about 25% or less. For example, when the relative humidity exceeds about 35% and actually exceeds about 45%, the temperature curves 120-5 and 116-5 immediately converge to one.

  The last column of Table 5 shows the battery voltage drop during operating hours with peak demand. This voltage drop indicates a decrease in the volume of air that is carried through the system by the various fans. Applicant does not want to be bound by theory, but a small temperature rise appears (corresponding to the temperature curve 120-in FIG. 7), corresponding to a decrease in the amount of air passing through the system between approximately 2 pm and 6 pm. 5). The system has been shown to be relatively sensitive to small changes in air flow through the system. The voltage is desirably at least 11 V or more in order to optimize the operation of the fan motor. The addition of one or two additional solar panels to the three panels provided on the roof of the warehouse 64 has sufficient capacity to maintain this voltage during peak demand periods.

  The column heading “122T” in Table 5 indicates the external temperature on the shell side of the heat exchanger. The temperature of the water inside the shell side is generally about 10 to 15 degrees Fahrenheit (6 to 9 ° C.) lower than the temperature at location 122. Thereby, the thing in the relationship of heat exchange with this water is cooled. If close to the shell side, a small object can be cooled without requiring large additional energy. The shelf life of a small quantity of food and medicines that are vulnerable to heat can be extended by placing the inventory in a location that exchanges heat with this water. A suitable container is placed directly in the water on the shell side, or a storage shelf that can be reached from the outside is assembled in the shell side, or for example water that circulates through a cooling coil that runs from the shell side to the outside A flow or the like is used to cool the object.

  The column heading “118T” in Table 5 is a measure of the heat radiated into the structure by the outer wall. The column heading “124T” indicates the cooling effect inside the warehouse 64 based on the temperature outside the wall. Clearly, a large amount of heat is moving through the uninsulated walls of the warehouse 64. Since the position 116 is sufficiently away from the adjacent wall, even if there is a temperature effect due to cooling of the interior of the warehouse 64, the position 116 is very small. A comparison of columns 120, 98 and 100 shows that the temperature is relatively uniform throughout the interior of warehouse 64.

  It has been found that a heat insulating case that seals the heat exchanger improves the efficiency of the system by more than 10%. The temperature of the water body on the shell side tends to decrease due to the presence of thermal insulation. The degree of thermal insulation is preferably the external temperature on the shell side of the heat exchanger, preferably from the equilibrium temperature on the metal shell side where insulation is not performed when the ambient air is 80 degrees Fahrenheit (27 ° C.). The column 122T in Table 5 is at least 3 degrees Fahrenheit (1 ° C), more preferably 5 degrees Fahrenheit (2 ° C) higher. By changing from a metal case (18 gauge steel) to a glass fiber (glass filament reinforced thermosetting resin) case with a thickness of about 1/8 inch (3.2 mm), the ambient internal air temperature is approximately 80 degrees Fahrenheit. At (27 ° C.), the temperature can be decreased by about 5 degrees Fahrenheit (2 ° C.). The efficiency of the air conditioning system will also increase. As will be appreciated by those skilled in the art, a number of thermal insulation forms and application methods can be applied for this purpose.

  The consumption rate of water in the air conditioning system according to the present invention is extremely small. For example, the water consumption rate during operation of the embodiment described herein in connection with FIG. 5 is about 5% when a conventional evaporative cooler (common sump cooler) is operated under similar conditions. Only. Even when the structure and other sealed spaces are not insulated and are not sealed, the amount of water consumption is low even in a state where a considerable amount of air leaks freely. Normally, the water consumption rate of the heat exchanger according to the present invention is the same as that of a conventional direct vaporizer The external state of the air conditioning system) is basically about 10% or less, more preferably about 5% or less for operation under the same state. For comparison purposes, basically the same external state is constituted by an external state with similar temperature and relative humidity, and the same structure and other enclosed space with the same volume and shape, insulation, for example. ing. For comparison purposes, the difference in the results of comparing the operation of the conventional vaporizer and the operation of the cooling system of the present invention is caused by the difference in the cooling system, the environment and structure outside the cooler and other sealings. Does not arise from the characteristics of the space created. All changes in the two cooling systems other than the original are constant for comparison purposes. That is, all external changes are basically constant. Water consumption rate while achieving a humidification efficiency of about 30-40% (dry bulb temperature drop after passing through heat exchanger divided by maximum possible dry bulb temperature drop determined from air diagram) Is kept low.

  The relative humidity inside the air-conditioned structure according to the first embodiment of the present invention is generally lower than expected from a conventional evaporative cooler. For example, comparing the data in columns “116 T / H” and “120 T / H” in Tables 4 and 5, the outside air temperature exceeds 95 degrees Fahrenheit and the relative humidity of the outside air is reduced to about 25% or less. In this case, the relative humidity in the structure is about twice (200%) the relative humidity of the external environment. When the external relative humidity drops below about 20% and the temperature exceeds approximately 100 degrees Fahrenheit (38 ° C), the internal relative humidity is about twice or more that of the external environment, but about 2.3 times ( 230%) or less. Even when the outside air temperature is approximately 110 to 120 degrees Fahrenheit (43 to 49 ° C.), even when the internal atmosphere temperature is maintained at 85 degrees Fahrenheit (29 ° C.) or less, the internal relative humidity is 50 % Or less. When a conventional evaporative cooler is used under similar conditions, the internal relative humidity is about 60% or less according to the present invention, although the internal relative humidity is usually about 60% or more. This minimizes the occurrence of mold and the like and improves the comfort of the occupant of the structure and other sealed spaces. Due to the low relative humidity, temperatures below 85 degrees Fahrenheit (29 ° C.) are generally comfortable for most people. As will be appreciated by those skilled in the art, an air conditioning system that is open to non-insulated structures, with very low water consumption and using the energy collection system described above, for example, solar or wind energy. Achieving is preferred and beneficial for many methods and purposes.

<Humidity variable embodiment according to the present invention>
With reference to FIGS. 8 to 21, a humidity variable embodiment according to the present invention used in a high temperature, a low humidity environment as described above, and a high humidity environment including a tropical or subtropical environment will be described. FIG. 8 shows an air conditioner 201 which is a direct / indirect evaporative cooler integrated with cooled sump water. As shown in FIG. 8, the variable humidity device 201 has many common points with the low humidity device described in FIGS. 1 to 7. The air conditioner 201 is preferably designed to have a stacked arrangement with an upper portion 203, a middle portion 205, and a bottom portion 207. As shown in FIG. 9, the refrigeration compressor 209, the condenser unit 210 associated with the refrigeration compressor, and the storage battery 211 are provided on the upper part 203 of the structure and placed on the top shelf 213. Yes. The top shelf 213 forms an upper wall opposite the wall 216 of the exhaust plenum 215. A forced air evaporative cooling chamber (217 in FIG. 9) is located below the exhaust plenum and occupies the middle of the structure. The cooling chamber constitutes a shell plenum for air conditioning and constitutes about 65% of the total height of the unit in the embodiment described in the drawings. A cooling water sump 219 (indicated by the dotted line in FIG. 9) is located at the bottom of the cooling chamber. The bottom floor 223 of the cooling chamber 217 constitutes the upper wall of the intake plenum 221 including the intake fan 225. The intake fan 225 is connected to the intake plenum 221 and the exhaust plenum 215, and draws air upward through a plurality of rising tubes 227 that pass through the cooling chamber 217.

  As shown in FIG. 12, the bottom floor 223 of the cooling chamber has a plurality of openings 224 that form a lower tube sheet for the rising tube 227. Similarly, opposing walls 216 have aligned openings (214 in FIGS. 10 and 13) that form the upper tubesheet. As shown in FIGS. 8-15, in an embodiment according to the present invention, about 1/4 to 3/8 inch diameter (6.4 to 9.5 mm) arranged vertically in the cooling chamber 217 between the tube plates. ) About 49 copper tubes are provided. The sizing and placement of tube bundles can be influenced by back pressure during operation operated by an automatically controlled thermostat.

  The operation of the humidity variable embodiment according to the present invention will be briefly described. Cooling water from the cooling water sump 219 (FIG. 9) is introduced into the vaporization cooling chamber through the distribution header 229. The distribution header shown in FIG. 9 is a continuous PVC pipe having a hole penetrating downward. Cooling water sprayed downward from the distribution header saturates the evaporating medium that surrounds or contacts the riser tube 227 in the cooling chamber 217. The evaporation medium has been removed in FIGS. 9 and 11 to simplify the description, but includes some of the medium materials described above with respect to the first embodiment of the present invention. Preferably, the evaporation medium is supplied as a rectangular pad suspended from a rack (241 in FIG. 14) provided on the ceiling of the cooling chamber, and is installed between a number of vertical rising tubes 227.

  Air is introduced into the cooling chamber by fans 231 and 233 arranged opposite to each other. The fans 231 and 233 are mounted on louvers (235 and 237 in FIG. 9). The louvers manually and directly adjust the air that is introduced and exhausted from the cooling chamber 217 in the circulation and vortex channels that create turbulence in the cooling chamber 217 and enhance the evaporative cooling process. The vortex effect produced by the side louvers 235, 237 causes the movement of air through the cooling chamber 217 and increases the residence time in the cooling chamber. For this reason, the cooling effect is increased and water droplets are prevented from being directly blown out of the shell plenum. Cooling air from the cooling chamber is expelled through a suitable grid (such as grid 239 in FIG. 8) into the structure for cooling, or to a predetermined area within the structure to be cooled. Sent through a suitable duct.

  Air is also drawn into the intake plenum 221 by the intake fan 225 and the air flow is directed upward through a riser tube 227 disposed in the cooling chamber. As the riser tube passes through the cold water sump in the cooling chamber and contacts the evaporation medium, the outside of the tube is cooled. The air inside the tube 227 is cooled by conduction through the tube. This relatively dry air is routed through a suitable duct into the cooled structure and, if necessary, mixed with the cooled air from the cooling chamber.

  In this latter embodiment according to the invention, the air is cooled by using two simultaneous processes. The air is cooled by direct contact with the water in the evaporative cooling chamber 217, increasing the absolute humidity of the air cooled in this manner. Additional air is also cooled by conductive heat transfer in the riser tube 227. The absolute humidity of this additional air does not change, increases slightly or decreases slightly. This is because it is condensed inside the rising tube. If necessary, the two air streams have been described with respect to the first embodiment of the invention so that the released air comprises a mixture of relatively moist air from the evaporation process and air that is close to external humidity. It can be mixed inside a single discharge duct.

  The cold water sump (219 in FIG. 9) at the bottom of the cooling chamber acts as a cooling group, similar to the sump. The water in the sump is cooled until it is almost frozen by a commercial cold compressor. The cryocompressor is similar to that used in ice makers and is operated by AC or DC, preferably by a 12V DC power source. As shown in FIG. 11, in the embodiment of the present invention, the compressor 209 is operated by a battery. However, in the present embodiment, the inverter 243 (FIG. 11) arranged in the exhaust plenum region 215 charges the battery, for example, during a non-peak time period, thereby causing the apparatus to turn off AC current. By reducing the operating temperature by placing the inverter in a cooled exhaust plenum compartment, the life of the inverter is extended. The electric fan used for the intake plenum and the cooling chamber is preferably a 12V fan driven by solar cells or accumulators.

  10, 11, 16, 16A, 16B show a generally preferred refrigeration manifold 245 that is cooled by a compressor 209 and a condenser 210 associated with the compressor using conventional mechanical refrigeration techniques. Although many different conventional manifolds and coil arrangements are utilized with the compressor 209 to cool the water in the sump 219, the preferred manifold 245 is particularly effective for the intended use. As shown in FIG. 16, the manifold 245 is a “double shock” manifold having a front layer 247 and a rear layer 249. The front and rear layers, or coils, are spaced apart by a plurality of cylindrical spacers 251. The cylindrical spacer 251 is shorter than the entire width of the manifold and has a distance d between adjacent spacers. The cylindrical spacer is also hollow in the sump 219 and open at both ends so that water can flow around or through the spacer. As shown in FIG. 11, the manifold 245 is typically placed in a horizontal plane within the sump of the cooling chamber.

  The refrigerant is supplied to the pair of divided manifold layers indicated by 253 and 255 in FIG. 16 and returns. As shown in FIG. 16B, the upper layer of the coil is formed by loops 252, 254, 256, 258, 260, 262, 264 and 266 (the loop is shown as a cross section for simplicity of explanation). The lower layer of the coil is formed by loops 268, 270, 272, 274, 276, 278, 280 and 282. Loop portions 252 through 266 form a continuous coil of the front layer of the manifold. The loop portions 268-282 form a continuous coil of the front layer of the manifold. The loop portions 268-282 similarly form a continuous loop in the rear layer of the manifold. The points exiting or ending from the front and rear loops (266 and 268 in FIG. 16B) are connected by crossover pipes 284 and 286. Crossover pipes 284, 286 traverse the first loop portion (252, 282 in FIG. 16B) to form branches 253, 255. As a result of the arrangement of the crossover pipes and the branches 253 and 255, an intermediate laminar flow passing through the manifold is formed. For example, the refrigerant flowing through the branch 253 flows to the front layer 247 through the branch 253B (FIG. 16), and flows to the rear layer 249 through the branch 253A. The refrigerant returning from the front and rear layers 247 and 249 merges at the branch 255. A double shock manifold with a split flow approximately doubles the cooling capacity of the compressor 209.

  The following description is obtained from an actual operation test of the apparatus described in FIGS. 8 to 16B described above. The following test results are not intended to be limiting and are intended to illustrate features of particularly preferred embodiments of the invention. The case or housing of the device is made of stainless steel. Two 12V fans mounted on opposite sides of the device are used to draw the external atmosphere into the central wet chamber. Wet chamber is referred to herein as the “wet side” of the device. A copper tube and a single 12V fan extending into the wet chamber are used to pass air through the tube of the part referred to as the “dry side” of the device. Air is supplied to the dry side through a duct extending inside the air-conditioned space. The two air streams (dry and wet side) are mixed inside the device and directed to one outlet. The device is combined with a stacked mechanical refrigeration device used to cool the water in the wet chamber sump. In order to allow the operation of the unit by a 120V AC power source and to charge the battery, a battery and an inverter for 12V DC operation of the apparatus are provided.

<Explanation of test equipment introduction>
The test equipment is located outside a closed auto repair shop in Banning, California. The air supply on the second (wet) side of the device is obtained from an outdoor atmosphere. The garage is approximately 30 feet (9.1 m) long, 35 feet (10.7 m) wide and has a 14-foot (4.3 m) high roof. The mixing outlet air flow of the device and the supply air to the first (dry) side pass through a duct that passes through the door and enters a sealed car repair shop space. Both ducts are 10 feet (3.0 m), straight and unfolded. The duct for the mixing air outlet of the apparatus has an inner diameter of 10.25 inches (0.26 m) and the duct for the first (dry) side has an inner diameter of 7.0 inches (0.18 m).

  One door of the car repair shop is left open to the outside air to avoid air escaping from the car repair shop and increasing back pressure in the car repair shop space. In the first two tests, the device was placed a few inches from the door. In the third test, the device was moved to about 10 feet (3.1 m) from the door, but the two ducts still extend through the door into a sealed space. For the third test, the device is placed in the shade.

<Test data and results>
<Test # 1>
In this test, the device is not connected to an AC power source and is running on battery power.

<Test # 2>
In this test, the device is connected to an AC power source and is operated by an inverter.

<Test # 3>
Similar to Test # 2 except that the device is 10 feet (3.1 m) away from the door as described above.

  Note: The humidification efficiency calculations in all three tests are based on the cfm weighted average of the dry bulb temperature and the relative humidity (%) of the first and second inlet air streams and the mixing outlet.

  The above test results show that a humidification effect was achieved in the dry state in a dry climate zone as found in Southern California. However, it is generally attractive to obtain humidity from this system even in climatic zones that are not very dry. FIG. 19 shows an additional refrigeration manifold (evaporator) 260 installed in a wet chamber (217 in FIG. 9) located in front of the discharge outlet 262 from the wet chamber. The additional refrigeration manifold 260 may be supplied with refrigerant from a conventional mechanical refrigeration system used to cool the sump water in the wet chamber described above.

  FIG. 19 shows a simplified concept of a conventional compressor 264 and condenser 266 used to supply refrigerant between the high side 268 and low side 270 of the double shock manifold 245 provided in the sump portion of the wet chamber 217. FIG. The conventional dryer 272 and the expansion device 274 are arranged in the circulation refrigerant path as in the conventional method. The expansion device 274 may be a conventional expansion valve known in the industry, or other convenient expansion device that transports from high pressure steam to low pressure steam through the coils of the double shock manifold 245 to produce a cooling effect. good.

  To accommodate the additional refrigeration manifold 260, the compressor 264 is adapted to a high side line 276 and a low side line 278 that supply refrigerant through the expansion device 280 to the evaporation coil 282 of the additional manifold. A commercially available flow control valve 284 controls the return of refrigerant from the low shock sides 270 and 278 of the double shock manifold 245 and the additional refrigeration manifold 260 to the compressor 264, respectively.

  The refrigeration circuit also includes valves 288 and 291 downstream of the 12V pump that control the supply of refrigerant to the high side 268 and 276 of the manifold, respectively. Since the pump downstream valves 288 and 291 are connected to the same electric circuit as the fans 231 and 233 on the wet chamber 217 side, the refrigerant is supplied to the additional manifold only when the fans 231 and 233 are operating. The compressor 264 includes a thermostat that maintains the sump water at or near 35 degrees Fahrenheit (1.7 ° C.). Because it has a fan and a refrigerant that circulates through the additional manifold 260, for example, air blowing across the additional manifold at approximately 45 degrees Fahrenheit (7.2 ° C.) is cooled, water droplets in the air are condensed, and the water droplets are collected into the wet chamber. Drop to sump section 219 of 217. Under certain conditions, the agglomerates that are generated eliminate the need to refill the sump section of the device. The condensation of moisture by this method acts to dehumidify the air released from the wet chamber 217.

  FIG. 20 shows an air conditioner 301 according to the present invention installed inside a structure for cooling. The device 301 has an external duct 303 connected to the outdoor environment from one of the fan inlets 305 of the wet chamber to take in outdoor air. Opposing fan inlets 307 are connected to a duct 309 which is part of the return air system for the room. The discharge outlet 311 from the wet and dry chambers (or only from the wet chamber) is connected by a duct to a cool air outlet 313 in the room. The device provided with the additional refrigeration manifold 260 condenses the moisture flowing through the wet chamber 217. The condensate is filtered from contaminants and released from 315 or circulated through the system. The room also includes one or more overhead automatic vents 317, 319 that open when the room door is open and open when the room door is closed. The vents act to discharge a certain amount of essentially stagnant air from the room to the attic. The attic is provided with a conventional exhaust hole 321 for releasing hot air to the outside of the structure. In this manner, the system can operate to release stagnant air to the exterior of the structure even if there is no duct 303 to the exterior of the structure. This is in contrast to typical vaporizers that retain approximately 100% of the air, or conventional air conditioning systems that circulate air that retains only 1%.

  FIG. 21 illustrates an additional method of controlling the inlet air to the device to further adjust the outlet temperature and / or humidity. In this adjustment, the fan inlet 305 to the wet chamber is provided with a duct 323 that connects to the bottom chamber (intake plenum) 221 of the apparatus. A thermostatically controlled door or gate valve mechanism can be activated to draw air from the bottom chamber 221. If air is drawn from the chamber 221, the second door or gate valve 327 blocks the air drawn from the outside through the duct 303. For example, when the outdoor air temperature is 110 degrees Fahrenheit (43 ° C.), it is preferable to close the valve 327 and draw only indoor air that is, for example, 80 degrees Fahrenheit (26.7 ° C.).

  As briefly mentioned above, the water in the sump section 219 of the cooling chamber of the apparatus is typically at least approximately 10 to 15 degrees Fahrenheit (5.5 to 8.3 ° C.) cooler than the surrounding environment. For this reason, the object placed in a place that exchanges heat with water is cooled. For example, small objects can be cooled without requiring large additional energy. A suitable container is placed directly in the water on the shell side, or a storage shelf that can be reached from the outside is assembled in the shell side, or for example water that circulates through a cooling coil that runs from the shell side to the outside Flow or the like is used to cool the object. As shown in FIG. 14, the sump water portion of the cooling chamber is provided with one or more sets of auxiliary cooling jackets 257, 259 that are filled and capped when not in use. The auxiliary jacket includes an inlet and an outlet for water in the sump portion of the device. The cooling water can be easily connected to other devices such as other heat exchangers in the structure to be cooled to enhance cooling capacity.

  FIG. 17 shows the auxiliary refrigeration apparatus 261. A typical device is about 15 inches (0.38 m) wide and 24 inches (0.61 m) high and is convenient to be placed between pillars in a residential wall. Water from the sump 219 of the air conditioner 201 passes through the pipe 263 and is sucked into the water intake port of the fluid pump 265. The pump 265 passes the cold water through the pipe line 267 and discharges the cold water to the coil 269. A 12V DC fan 271 located on the back of a 12x12 inch (0.31mx0.31m) coil is used to pass the coil through the air and to release the cooled air from the device to the cooled structure. Is done. The fans are independent of the cooling chamber fans 231 and 233 used in the main air conditioner. The return water returns to pump 265 through line 273 and is cooled again by the main unit mechanical refrigeration system and is therefore recirculated through outlet line 275 by the pump to main unit sump 219. In addition, a tray 274 is provided for receiving the aggregate. In an embodiment of the invention, the inlet and outlet water lines 263, 275 are packaged in a cable arrangement (FIG. 18) having a suitable polyolefin sheath, for example. Cable 277 also includes a suitably shielded DC power supply line (279 in FIG. 18) to supply power to fan 271 and pump 265.

  The invention provides several advantages. The cooling system according to the present invention is manufactured relatively inexpensively. The system produces a difference of more than 30 degrees Fahrenheit (17 ° C.) between the temperature of inhaled and released air. The system can be operated in dry climates with DC power obtained from solar panels and windmills. The inverter allows the device to be connected to an AC power source during non-peak hours to charge the DC battery source. The device is operated with an AC power supply of 20 amps or less even under peak conditions. The vortex nature of the wet chamber inevitably removes airborne contaminants such as pollen and dust. Since the contaminants fall into the sump part of the apparatus and are discharged, the apparatus works not only as an air conditioner but also as an air purifier. The humidification of the system is adjusted in several different ways depending on the application purpose of the device.

  As will be appreciated by those skilled in the relevant arts, many variations and modifications can be made to the above-described optimal embodiments of the present invention. Although the present invention has been described herein in connection with a particular embodiment in which the shell side of the heat exchanger is the wet side and the tube side is the dry side, those skilled in the art will recognize, for example, a wet tube side and a dry shell side, etc. It can be readily recognized by considering the disclosure that other arrangements including are possible. One skilled in the art can recognize from the disclosure that heat exchangers other than shell and tube can be used if desired.

  What has been described is a preferred embodiment that can be modified and changed without departing from the spirit and scope of the appended claims. Many modifications and variations in the present invention are possible within the scope of the above teachings. Therefore, it will be understood that, within the scope of the appended claims, the invention may be practiced other than as specifically described.

It is the schematic which concerns on embodiment of the shell and tube type heat exchanger which concerns on this invention. It is sectional drawing seen along line 2-2 of FIG. 1 is a schematic cross-sectional view of an embodiment of a shell plenum showing a liquid spray system. 1 is a schematic cross-sectional view of an embodiment of a shell plenum according to the present invention showing a tube entirely surrounded by a blanket. It is a top view of the structure in which the air-conditioning system using the shell and tube heat exchanger concerning the present invention was installed in the inside. It is sectional drawing of the shell plenum of the heat exchanger of FIG. 6 is a graph showing the temperature and relative humidity shown in Tables 4 and 5 at positions 116 and 120 in FIG. 5. FIG. 6 is a perspective view of another embodiment of the apparatus according to the present invention characterized by the combination of direct / indirect evaporative cooling and cooled sump water. FIG. 9 is a rear view of the device of FIG. 8 with the rear wall removed to facilitate description of the internal elements of the device. FIG. 10 is an exploded perspective view showing a cooling chamber and a refrigeration manifold used in the apparatus of FIGS. 8 and 9. FIG. 9 is a perspective view of the device of FIG. 8 with the rear wall removed to facilitate description of the internal elements of the device. It is a top view of the upper wall of the cooling chamber that also serves as a tube plate for the riser tube. FIG. 9 is an exploded perspective view of a cooling chamber of the apparatus of FIG. 8. FIG. 3 is a side view of a cooling chamber showing the arrangement of the water distribution array. It is a disassembled perspective view which shows an intake plenum and an intake fan. It is a disassembled perspective view of the freezing manifold used in the cold water sump of the apparatus of FIG. It is sectional drawing along line 16A-16A of FIG. FIG. 9 is a simplified manifold end view of the manifold of FIG. 8 showing the crossover piping used to create the interlayer flow pattern. It is the schematic of the auxiliary heat exchange apparatus which moves apart from the cold water in the cold water sump of the apparatus of this invention. FIG. 18 is a cross-sectional view of a cable used to connect the auxiliary heat exchange device of FIG. 17 and the main cooling assembly shown in FIGS. It is the schematic which shows the additional freezing manifold installed in the wet chamber of the high humidity version of the air-conditioning system which concerns on this invention along the freezing circuit relevant to this manifold. It is the schematic which shows the air flow which passes the structure utilized for the air conditioning system which concerns on this invention. FIG. 6 is a schematic diagram showing an alternative duct arrangement for air flow to a wet chamber of an apparatus according to the present invention.

Claims (11)

A cooling assembly,
A heat exchanger that includes a case member that seals the wet side in heat exchange relationship with the dry side, wherein both sides are substantially hermetically sealed to each other;
A first air moving member adapted to flow cooled air through the dry side;
A liquid distribution member provided inside the wet side;
A liquid sump element attached to the wet side, adapted to receive liquid from the wet side and to provide the liquid to the liquid distribution member;
At least two or more additional air moving members adapted to cause air to flow through the wet side from different locations to create a turbulent high-humidity air mass on the wet side;
A mechanical refrigeration apparatus comprising a compressor and a refrigeration manifold disposed in the liquid sump for cooling liquid stored in the liquid sump element in association with the compressor;
An additional manifold disposed within the sealed wet side of the case member of the heat exchanger. A cooling assembly for cooling the interior of the structure,
The cooling assembly includes
A stacked chamber assembly with a forced air vaporization cooling chamber located in the center of the assembly;
The cooling chamber separates an exhaust air plenum located above the cooling chamber from an intake plenum located below the cooling chamber, and includes a top wall, a bottom wall forming a cold water sump portion, and a surrounding side wall; A plurality of vertically arranged rising tubes connecting the intake plenum and the exhaust plenum;
The cooling assembly further includes
An intake fan disposed in the intake plenum to draw air cooled upward through the plurality of vertical risers connecting the intake plenum and the exhaust plenum;
A liquid distribution member disposed in the cooling chamber adjacent to the upper wall;
A pump for feeding water from the sump portion of the cooling chamber to the liquid distribution member;
A pair of opposed arrangements attached to the side walls of the cooling chamber to move air through the cooling chamber from different locations to produce turbulent high humidity air bubbles inside the cooling chamber. With fans
A discharge outlet for discharging air from the cooling chamber;
A mechanical refrigeration apparatus comprising: a compressor; and a refrigeration manifold disposed in the sump of the cooling chamber to cool water stored in the liquid sump section associated with the compressor;
A cooling assembly including an additional refrigeration manifold disposed in front of the discharge outlet of the cooling chamber to dehumidify the turbulent air mass passing through the discharge outlet.   The cooling assembly of claim 2, wherein the additional refrigeration manifold is cooled by the same compressor as the mechanical refrigeration device used to cool the sump portion of the cooling chamber. The mechanical refrigeration apparatus is
A condenser,
A conduit for circulating refrigerant between the high and low sides of the evaporation coil in connection with the condenser;
The associated line has a pump downstream valve installed in the associated line to control the flow of the refrigerant to the evaporation coil;
The pump downstream valve is opened when the face-to-face fan mounted on the side wall of the cooling chamber is on and running and closed when the fan is off. Item 4. The cooling assembly according to Item 3. A direct / indirect evaporative cooling assembly having a cooled cold water sump for cooling the interior of the structure,
A laminated chamber assembly comprising a forced air vaporization cooling chamber located in the middle of the assembly;
The cooling chamber includes an upper wall, a bottom wall, a peripheral side wall, and a plurality of vertically arranged rising tubes, and an exhaust plenum located above the cooling chamber is located below the cooling chamber. Separate from the intake plenum,
The cooling chamber, the intake plenum, and the exhaust plenum constitute a shell and tube heat exchanger in which a wet side in a heat exchange relationship with a dry side is sealed,
The two sides are substantially weld-sealed to each other;
The bottom wall forms a cold water sump portion with the upper wall of the intake plenum and the lower tube plate for the rising tube,
An upper wall of the cooling chamber forms an upper tube sheet for the lower wall of the exhaust plenum and the riser tube;
The direct / indirect evaporative cooling assembly further includes
In the intake plenum to draw air upward through the plurality of vertical risers connecting the intake plenum and the exhaust plenum to produce a cooled air flow from the dry side of the assembly. An intake fan located in the
A liquid distribution member disposed on the wet side of the cooling chamber so as to be adjacent to the upper wall;
A pump for feeding water from the sump portion of the cooling chamber to the liquid distribution member;
A pair of opposed arrangements attached to the side walls of the cooling chamber to move air through the wet side from different locations to create a turbulent high humidity air mass on the wet side With fans,
A discharge outlet for discharging air from the cooling chamber;
A mechanical refrigeration apparatus comprising: a compressor; and a refrigeration manifold disposed in the sump of the cooling chamber to cool water stored in the sump section associated with the compressor;
A direct / indirect evaporative cooling assembly comprising an additional refrigeration manifold disposed in front of the discharge outlet of the cooling chamber to dehumidify the turbulent air mass passing through the discharge outlet.   6. The direct / indirect evaporative cooling assembly of claim 5, wherein the additional refrigeration manifold is cooled by the same compressor as the mechanical refrigeration device used to cool the sump portion of the cooling chamber. The mechanical refrigeration apparatus is
A condenser,
A conduit for circulating a refrigerant between the high and low sides of the evaporation coil in relation to the condenser;
The associated line has a pump downstream valve installed in the associated line to control the flow of the refrigerant to the evaporation coil;
The pump downstream valve is opened when the face-to-face fan mounted on the side wall of the cooling chamber is on and running and closed when the fan is off. Item 7. The direct / indirect evaporative cooling assembly according to item 6. The cooling assembly is installed inside a cooled structure having a ceiling and an attic;
The structure has at least one ceiling vent that opens and closes to allow air to pass from the structure to the attic;
The attic has an exhaust hole for discharging air from the attic,
6. The direct / indirect evaporative cooling assembly of claim 5, wherein stagnant air inside the structure is released periodically. The opposed fans of the cooling chamber are
Have a fan inlet,
9. The direct / indirect evaporative cooling assembly according to claim 8, wherein at least one or more of the fan inlets are connected to a duct leading to the exterior of the structure for allowing outdoor air to enter the cooling chamber. .   6. Direct / in accordance with claim 5, characterized in that the sump part of the cooling chamber is connected to a discharge line for releasing contaminants collected in the water that stops in the sump part. Indirect evaporative cooling assembly. An additional duct connects the intake plenum and the cooling chamber;
6. Direct / indirect vaporization according to claim 5, wherein the duct has a valve controlled by a thermostat attached to the duct to control air flow from the intake plenum to the cooling chamber. Cooling assembly.

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