Abstract:
A desalination system in the form of a submerged gas evaporator that includes a vessel, a gas delivery tube partially disposed within the vessel to deliver a gas into the vessel and a fluid inlet that provides a fluid to the vessel at a rate sufficient to maintain a controlled constant level of fluid within the vessel. A weir is disposed within the vessel adjacent the gas delivery tube to form a first fluid circulation path between a first weir end and a wall of the vessel and a second fluid circulation path between a second weir end and an upper end of the vessel. During operation, gas introduced through the tube mixes with the fluid and the combined gas and fluid flow at a high rate with a high degree of turbulence along the first and second circulation paths defined around the weir, thereby promoting vigorous mixing and intimate contact between the gas and the fluid. This turbulent flow develops a significant amount of inter facial surface area between the gas and the fluid resulting in a reduction of the required residence time of the gas within the fluid to achieve thermal equilibrium which leads to a more efficient and complete evaporation. Additionally, vapor exiting the submerged gas evaporator is condensed in a condensing unit thus precipitating vapor into a liquid for removal.

Description:
RELATED APPLICATIONS 
       [0001]    This application is a continuation-in-part of U.S. patent application Ser. No. 11/186,459, filed on Jul. 21, 2005, the entire specification of which is hereby incorporated by reference. 
     
    
     FIELD OF THE DISCLOSURE 
       [0002]    The present disclosure relates generally to desalination systems and liquids, and more specifically, to desalination systems including submerged gas evaporators. 
       BACKGROUND 
       [0003]    Desalination systems are systems that remove salt or other dissolved solids from water, most often to produce potable water. Currently, several methods of desalination are employed by commercial desalination systems. The most popular methods of commercial desalination are reverse osmosis and flash vaporization. Both of these methods have large energy requirements and certain components that wear out frequently. For example, reverse osmosis systems force water through membranes and these membranes become clogged and torn, thus necessitating frequent replacement. Similarly, flash vaporization systems have corrosion and erosion problems due to the spraying of hot brine within these systems. The energy requirements for a reverse osmosis system may be approximately 6 kWh of electricity per cubic meter of water, while a flash vaporization, system may require as much as 200 kWh per cubic meter of water. Due to the high energy inputs and frequent maintenance, desalination of water on a large scale basis has been relatively expensive, often more expensive than finding alternate sources of groundwater. 
         [0004]    Submerged gas evaporator systems in which gas is dispersed into a continuous liquid phase, referred to generally herein as submerged gas evaporators, are well known types of devices used to perform evaporation processes with respect to various constituents. U.S. Pat. No. 5,342,482, the entire specification of which is hereby incorporated by reference, discloses a common type of submerged combustion gas evaporator, in which combustion gas is generated and delivered though an inlet pipe to a dispersal unit submerged within the liquid to be evaporated. The dispersal unit includes a number of spaced-apart gas delivery pipes extending radially outward from the inlet pipe, each of the gas delivery pipes having small holes spaced apart at various locations on the surface of the gas delivery pipe to disperse the combustion gas as small bubbles as uniformly as practical across the cross-sectional area of the liquid held within the processing vessel. According to current understanding within the prior art, this design provides desirable intimate contact between the liquid and the combustion gas over a large interfacial surface area while also promoting thorough agitation of the liquid within the processing vessel. 
         [0005]    Because submerged gas evaporators disperse gas into a continuous liquid phase, these devices provide a significant advantage when compared to conventional evaporators when contact between a liquid stream and a gas stream is desirable. In fact, submerged gas evaporators are especially advantageous when the desired result is to highly concentrate a liquid stream by means of evaporation. 
         [0006]    However, during the evaporation process, dissolved solids within the continuous liquid phase become more concentrated often leading to the formation of precipitates that are difficult to handle. These precipitates may include substances that form deposits on the solid surfaces of heat exchangers within flash vaporization systems or on the membranes of reverse osmosis systems, and substances that tend to form large crystals or agglomerates that can block passages within processing equipment, such as the gas exit holes in the system described in U.S. Pat. No. 5,342,482. Generally speaking, feed streams that cause deposits to form on surfaces and create blockages within process equipment are called fouling fluids. 
         [0007]    Deposits of precipitated solids create chemical fouling or buildup on fill or packing within conventional desalination systems that increases available surface area and also create stagnant flow areas that leads to biological fouling of these surfaces by promoting growth of bacteria and algae. Biological growth leads to the formation of slime within a desalination system that further reduces desalination efficiency and can also foul heat exchangers within equipment which employs the circulating liquid from the desalination system as an evaporative medium. 
         [0008]    These common problems adversely affect the efficiency and costs of conventional desalination systems in that they necessitate frequent cleaning cycles and/or the addition of chemical control agents to the evaporative fluid to avoid loss of efficiency and to avoid sudden failures within the evaporation equipment. 
         [0009]    Additionally, most evaporation systems that rely on intimate contact between gases and liquids are prone to problems related to carryover of entrained liquid droplets that form as the vapor phase disengages from the liquid phase. For this reason, most evaporator systems that require intimate contact of gas with liquid include one or more devices to minimize entrainment of liquid droplets and/or to capture entrained liquid droplets while allowing for separation of the entrained liquid droplets from the exhaust gas flowing out of the evaporation zone. Droplets within the vapor are particularly troublesome if the process is applied to produce potable water in that the entrained droplets contain the salts, minerals and other contaminants that were in the feed liquid. 
         [0010]    Unlike conventional evaporators where heat and mass are transferred from the liquid phase as it flows over the extended surface of the heat exchangers, heat and mass transfer within submerged gas processors lake place at the interface of a discontinuous gas phase dispersed within a continuous liquid phase and there are no solid surfaces upon which deposits can accumulate. 
         [0011]    Submerged gas evaporators also tend to mitigate the formation of large crystals because dispersing the gas beneath the liquid surface promotes vigorous agitation within the evaporation vessel, which is a less desirable environment for crystal growth than a more quiescent zone. Further, active mixing within an evaporation vessel tends to maintain precipitated solids in suspension and thereby mitigates blockages that are related to settling and/or agglomeration of suspended solids. 
         [0012]    However, mitigation of crystal growth and settlement is dependent on the degree of mixing achieved within a particular submerged gas evaporator, and not all submerged gas evaporator designs provide adequate mixing to prevent large crystal growth and related blockages. Therefore, while the dynamic renewable heat transfer surface area feature of submerged gas evaporators eliminates the potential for fouling liquids to coat extended surfaces, conventional submerged gas evaporators are still subject to potential blockages and carryover of entrained liquid within the exhaust gas flowing away from the evaporation zone. 
       SUMMARY OF THE DISCLOSURE 
       [0013]    A desalination system includes an evaporator vessel, one or more tubes partially disposed within the evaporator vessel which are adapted to transport a gas into the interior of the evaporator vessel, an evaporative fluid inlet adapted to transport an evaporative fluid into the evaporator vessel at a rate that maintains the evaporative fluid inside the evaporator vessel at a predetermined level and an exhaust stack that allows vapor to flow away from the evaporator vessel. In addition, the desalination system evaporator includes one or more weirs that at least partially surround the tube(s) and are at least partially submerged in the evaporative fluid to create a fluid circulation path formed by the space between the weir(s) and the walls of the evaporation vessel and gas tube(s). In one embodiment, each weir is open at both ends and forms a lower circulation gap between a first one of the weir ends and a bottom wall of the evaporator vessel and an upper circulation gap between a second one of the weir ends and a normal evaporative fluid operating level. 
         [0014]    During operation, gas introduced through the tube or tubes mixes with the evaporative fluid in a first confined volume formed by the weir or the weir and a wall of the evaporation vessel and the tube(s) and the fluid mixture of gas and liquid flows at high volume with a high degree of turbulence along the circulation path defined around the weir(s), thereby causing a high degree of mixing between the gas and the evaporative fluid and any suspended particles within the evaporative fluid. Shear forces within this two-phase or three-phase turbulent flow region that result from the high density liquid phase overrunning the low density gas phase create extensive interfacial surface area between the gas and the evaporative fluid that favors minimum residence time for mass and heat transfer between the liquid and gas phases to come to equilibrium compared to conventional gas dispersion techniques. Still further, vigorous mixing created by the turbulent flow hinders the formation of large crystals of precipitates within the evaporative fluid and, because the system does not use small holes or other ports to introduce the gas into the evaporative fluid, clogging and fouling associated with other evaporators are significantly reduced or entirely eliminated. Still further, the predominantly horizontal flow direction of the liquid and gas mixture over the top of the weir and along the surface of the evaporative fluid within the evaporation vessel enables the gas phase to disengage from the process fluid with minimal entrainment of liquid due to the significantly greater momentum of the much higher density liquid that is directed primarily horizontally compared to the low density gas with a relatively weak but constant vertical momentum component due to buoyancy. 
         [0015]    In addition, a method of desalination using a submerged gas evaporator includes providing a evaporative fluid to an evaporator vessel of a submerged gas evaporator at a rate sufficient to maintain the evaporative fluid level at a predetermined level within the evaporator vessel, supplying a gas to the evaporator vessel, and mixing the gas and evaporative fluid within the evaporator vessel by causing the gas and evaporative fluid to flow around a weir or weirs within the submerged gas processor to thereby transfer heat energy and mass between the gas and liquid phases of a mixture. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0016]      FIG. 1  is across-sectional view of a desalination system evaporator constructed in accordance with the teachings of the disclosure. 
           [0017]      FIG. 2  is a cross-sectional view of a desalination system evaporator including a baffle. 
           [0018]      FIG. 3  is a cross-sectional view of a desalination system evaporator having a tubular shaped weir. 
           [0019]      FIG. 4  is a top plan view of the desalination system evaporator of  FIG. 3 . 
           [0020]      FIG. 5  is a cross-sectional view of a desalination system evaporator connected to a source of waste heat. 
           [0021]      FIG. 6  is a cross-sectional view of a desalination system including a cooling/condensing unit. 
           [0022]      FIG. 7  is a cross-sectional view of a desalination system evaporator having multiple weirs and multiple gas inlet tubes. 
       
    
    
     DETAILED DESCRIPTION 
       [0023]    The performance of desalination systems according to the disclosure depends on the moisture content and temperature of the gas and the thermodynamic properties of the evaporative fluid, which are usually ambient air and water. As with conventional desalination systems, equations developed by Merkel that are based the enthalpy potential difference between the evaporative fluid and air, may be used to closely define the performance of a desalination system that is constructed according to the invention for a particular application. Desalination systems according to the disclosure can be substituted for conventional desalination systems. Conventional means of controlling the flow of evaporative fluid through the desalination system may be employed. Likewise, conventional means of controlling desalination systems to meet the requirements of a particular desalination system application may be employed. Multiple desalination systems according to the invention may be connected in series or parallel configurations to meet the desalination demand of a particular application. 
         [0024]    Referring to  FIG. 1 , a desalination system evaporator  10 , includes a fan/blower  20  and a gas supply tube or gas inlet tube  22  having sparge or gas exit ports  24  at or near an end  26  thereof. The gas inlet tube  22  supplies gas under positive pressure to an evaporator vessel  30  having a bottom wall  31  and an evaporative fluid outlet port  32 . An evaporative fluid inlet port  34  is disposed in one side of the vessel  30  and enables an evaporative fluid  35  to be provided into the interior of the evaporator vessel  30 . Additionally, a weir  40 , which is illustrated in  FIG. 1  as a flat or solid plate member having a first or lower end  41  and a second or upper end  42 , is disposed within the evaporator vessel  30  adjacent the gas inlet tube  22 . Although the evaporator vessel  30  and gas inlet tube  22  are generally shown herein as cylindrical in shape, one skilled in the art will realize that many other shapes may be employed for these elements. The weir  40  defines and separates two volumes  70  and  71  within the evaporator vessel  30 . As illustrated in  FIG. 1 , a gas exit port  60  disposed in the top of the vessel  30  enables gas (vapor) to exit from the interior of the evaporator vessel  30 . Disposed near a junction of the gas exit port  60  and the evaporator vessel  30  is a demister  61 . The demister  61  removes droplets of evaporative fluid that are entrained in the gas phase as the gas disengages from the liquid phase at the surface  80  of the liquid. The demister  61  may be a vane-type demister, a mesh pad-type demister, or any combination of commercially available demister elements. Further, a vane-type demister may be provided having a coalescing filter to improve demisting performance. The demister  61  may be mounted in any orientation and adapted to a particular evaporator vessel  30  including, but not limited to, horizontal and vertical orientations. 
         [0025]    In the desalination system evaporator of  FIG. 1 , the fan/blower  20  is supplied with gas through a line  51 . Moreover, the evaporative fluid  35  may be supplied through the fluid inlet  34  by a pump (not shown in  FIG. 1 ) at a rate sufficient to maintain a surface  80  of the evaporative fluid  35  within the evaporator vessel  30  at a predetermined level, which may be set by a user. A level sensor and control (not shown in  FIG. 1 ) may be used to determine and control the rate that the evaporative fluid  35  is supplied through the inlet port  34 . 
         [0026]    As illustrated in  FIG. 1 , the weir  40  is mounted within the evaporator vessel  30  to form a lower circulation gap  36  between the first end  41  of the weir  40  and the bottom wall  31  of the evaporator vessel  30  and to form an upper circulation gap  37  between the second end  42  of the weir  40  and the surface  80  of the evaporative fluid  35  (or a top wall of the evaporator vessel  30 ). As will be understood, the upper end  42  of the weir  40  is preferably set to be at or below the surface level  80  of the evaporative fluid  35  when the evaporative fluid  35  is at rest (i.e., when no gas is being introduced into the evaporator vessel  30  via the gas inlet tube  22 ). As illustrated in  FIG. 1 , the weir  40  also defines and separates the confined volume or space  70  in which the sparge ports  24  are located from the volume or space  71 . If desired, the weir  40  may be mounted to the evaporator vessel  30  via welding, bolts or other fasteners attached to internal side walls of the evaporator vessel  30 . 
         [0027]    During operation, gas from the line  51  is forced to flow under pressure into and through the gas inlet tube  22  to the sparge or exit ports  24 . The gas exits the gas inlet tube  22  through the sparge ports  24  into the confined volume  70  formed between the weir  40  and the gas inlet tube  22 , causing the gas to be dispersed into the continuous liquid phase of the evaporative fluid within the evaporator vessel  30 . Generally speaking, gas exiting from the sparge ports  24  mixes with the liquid phase of the evaporative fluid within the confined volume  70  and causes a high volume flow pattern to develop around the weir  40 . The velocity of the flow pattern and hence the turbulence associated with the flow pattern is highest within the confined volume  70  and at the locations where the evaporative liquid flows through the upper gap  37  and the lower gap  36  of the weir  40 . The turbulence within the confined volumes  70  and  71  significantly enhances the dispersion of the gas into the evaporative fluid which, in turn, provides for efficient heat and mass transfer between the gas and the evaporative fluid. In particular, after exiting the sparge ports  24 , the gas is dispersed as a discontinuous phase into a continuous liquid phase of the evaporative fluid forming a gas/liquid mixture within the confined volume  70 . The mass per unit volume of the gas/liquid mixture in the confined volume  70  is significantly less than that of the average mass per unit volume of the continuous liquid phase of the evaporative fluid in the volume  71 , due to the large difference in mass per unit volume of the liquid compared to the gas, typically on the order of approximately 1000 to 1. This difference in mass per unit volume creates a difference in static hydraulic pressure between the gas/liquid mixture in the confined volume  70  and the liquid phase in the volume  71  at all elevations. This imbalance in static hydraulic pressure forces the evaporative fluid to flow from the higher pressure region, i.e., the volume  71 , to the lower pressure region, i.e., the confined volume  70 , at a rate that overcomes the impressed static hydraulic pressure imbalance and creates flow upward through the confined volume  70 . 
         [0028]    Put another way, the dispersion of gas into the evaporative fluid  35  within the confined volume  70  at the sparge ports  24  develops a continuous flow pattern that draws evaporative fluid  35  under the bottom edge  41  of the weir  40  through the lower circulation gap  36 , and causes the mixture of gas and evaporative fluid  35  to move through the confined volume  70  and toward the surface  80  of the evaporative fluid  35 . Near the surface  80 , the gas/liquid mixture reaches a point of balance at which the imbalance of static hydraulic pressure is eliminated. Generally speaking, this point is at or near the tipper circulation gap  37  formed between the second end  42  of the weir  40  and the evaporative fluid surface  80 . At the balance point, the force of gravity, which becomes the primary outside force acting on the gas/fluid mixture, gradually reduces the vertical momentum of the gas/liquid mixture to near zero. This reduced vertical momentum, in turn, causes the gas/liquid mixture to flow in a predominantly horizontal direction over the second end  42  of the weir  40  (through the circulation gap  37  defined at or near the surface  80  of the evaporative fluid  35 ) and into the liquid phase of the evaporative fluid  35  within the volume  71 . 
         [0029]    This flow pattern around and over the weir  40  affects the dispersion of the gas into the continuous liquid phase of the evaporative fluid  35  and, in particular, thoroughly agitates the continuous liquid phase of the evaporative fluid  35  within the evaporator vessel  30  while creating a substantially horizontal flow pattern of the gas/liquid mixture at and near the surface  80  of the continuous liquid phase of the evaporative fluid  35 . This horizontal flow pattern significantly mitigates the potential for entrained liquid droplets to he carried vertically upward along with the dispersed gas phase as the dispersed gas phase rises through the liquid phase due to buoyancy and finally disengages from the continuous liquid phase of the evaporative fluid at the surface  80  of the evaporative fluid  35 . 
         [0030]    Also, the mixing action created by the induced flow of liquid and liquid/gas mixtures within both the confined volume  70  and the volume  71  hinders the formation of large crystals of precipitates (e.g., salt), which generally requires a quiescent environment. By selectively favoring the production of relatively small incipient particles of precipitates, the mixing action within evaporator vessel  30  helps to ensure that suspended particles formed in the submerged gas evaporation process may be maintained in suspension within the liquid phase circulating around the weir  40 , which effectively mitigates the formation of blockages and fouling within the desalination system evaporator  10 . Likewise, because relatively small particles that are readily maintained in suspension are formed through precipitation, the efficiency of the evaporator is improved over conventional evaporation systems in terms of freedom from clogging and fouling and the degree to which the feed liquid may be concentrated. 
         [0031]    In addition, as the circulating liquid phase within volume  71  approaches the bottom wall  31  of the vessel  30 , the liquid phase is forced to flow in a predominantly horizontal direction and through the lower gap  36  into the confined volume  70 . This predominantly horizontal flow pattern near the bottom wall  31  of the evaporator vessel  30  creates a scouring action at and above the interior surface of the bottom wall  31  which maintains particles of solids including precipitates in suspension within the circulating liquid while the desalination system is operating. The scouring action at and near the bottom wall  31  of the evaporator vessel  30  also provides means to re-suspend settled particles of solids whenever the desalination system is re-started after having been shutdown for a period of time sufficient to allow suspended particles to settle on or near the bottom wall  31 . 
         [0032]    As is known, submerged gas evaporation is a process that affects evaporation by contacting a gas with a liquid or liquid mixture, which may be a compound, a solution or slurry. Within a submerged gas evaporator heat and mass transfer operations occur simultaneously at the interface formed by the dynamic boundaries of the discontinuous gas and continuous liquid phases. Thus, all submerged gas evaporators include some method to disperse gas within a continuous liquid phase. The system shown in  FIG. 1  however integrates the functions of dispersing the gas into the liquid phase, providing thorough agitation of the liquid phase, and mitigating entrainment of liquid droplets with the gas phase as the gas disengages from the liquid. Additionally, the turbulence and mixing that occurs within the evaporator vessel  30  due to the flow pattern created by dispersion of gas into liquid within the confined volume  70  reduces the formation of large crystals of precipitates and/or large agglomerates of smaller particles within the evaporator vessel  30 . 
         [0033]      FIG. 2  illustrates a second embodiment of a desalination system evaporator  110 , which is very similar to the desalination system evaporator  10  of  FIG. 1  and in which elements shown in  FIG. 2  are assigned reference numbers being exactly 100 greater than the corresponding elements of  FIG. 1 . Unlike the device of  FIG. 1 , the desalination system evaporator  110  includes a baffle or a shield  138  disposed within the evaporator vessel  130  at a location slightly above or slightly below the evaporative fluid surface  180  and above the second end  142  of the weir  140 . The baffle or shield  138  may be a generally flat plate shaped and sized to conform generally to the horizontal cross-sectional area of the confined volume  170 . Additionally, if desired, the baffle  138  may be mounted to any of the gas inlet tube  122 , the evaporator vessel  130  or the weir  140 . The baffle  138  augments the force of gravity near the balance point by presenting a physical barrier that abruptly and positively eliminates the vertical components of velocity and hence, momentum, of the gas/liquid mixture, thereby assisting the mixture to flow horizontally outward and over the weir  140  at the upper circulation gap  137 . The baffle enhances mitigation of entrained liquid droplets within the gas phase as the gas disengages from the liquid phase. Furthermore, the blower  120  is disposed on the gas exit port  160  in this embodiment thereby providing gas to the evaporation vessel  130  under negative pressure, i.e., via suction. 
         [0034]    As will be understood, the weirs  40  and  140  of  FIGS. 1 and 2  may be generally flat plates or may be curved plates that surround the gas tubes  22 ,  122  and/or that extend across the interior of the evaporator vessel  30  between different, such as opposite, sides of the evaporator vessel  30 . Basically, the weirs  40  and  140  create a wall within the evaporator vessels  30 ,  130  defining and separating the volumes  70  and  71  (and  170  and  171 ). While the weirs  40  and  140  are preferably solid in nature they may, in some cases, be perforated, for instance, with slots or holes to modify the flow pattern within the evaporator vessel  30  or  130 , or to attain a particular desired mixing result within the volume  71  or  171  while still providing a substantial barrier between the volumes  70  and  71  or  170  and  171 . Additionally, while the weirs  40  and  140  may extend across the evaporator vessels  30  and  130  between opposite walls of the evaporator vessels  30  and  130 , they may be formed into any desired shape so long as a substantial vertical barrier is formed to isolate one volume  70  (or  170 ) closest to the gas inlet tube  22  from the volume  71  (or  171 ) on the opposite side of the weir  40 ,  140 . 
         [0035]      FIG. 3  illustrates a cross-sectional view of a further desalination system evaporator  210  having a weir  240  that extends around a gas inlet tube  222 . The desalination system evaporator  210 , generally speaking, has evaporative capacity equivalent to approximately 10,000 gallons per day on the basis of evaporating water from an evaporative liquid. A fan/blower (not shown in  FIG. 3 ) delivers hot gas which could be approximately 12,300 actual cubic feet per minute (acfm) at 1,400° F. to the gas inlet tube  222 . While the dimensions of the desalination system evaporator  210  are exemplary only, the ratios between these dimensions may serve as a guide for those skilled in the art to achieve a desirable balance between three desirable evaporation results including: 1) preventing the formation of large crystals of precipitates and/or agglomerates of solid particles while maintaining solid particles as a homogeneous suspension within the process liquid by controlling the degree of overall mixing within vessel  230 ; 2) enhancing the rates of heat and mass transfer by controlling the turbulence and hence interfacial surface area created between the gas and liquid phases within confined volume  270 ; and 3) mitigating the potential of entraining liquid droplets in the gas as the gas stream disengages from the liquid phase at the liquid surface  280  by maintaining a desirable and predominately horizontal velocity component for the gas/liquid mixture flowing outward over the second end  242  of the weir  240  and along the surface of the evaporative liquid  280  within evaporator vessel  230 . As illustrated in  FIG. 3 , the desalination system evaporator  210  includes an evaporator vessel  230  with a dished bottom having an interior volume and a vertical gas inlet tube  222  at least partially disposed within the interior volume of the evaporator vessel  230 . In this case, the gas inlet tube  222  has a diameter of approximately 20 inches and the overall diameter of the evaporation vessel  230  is approximately 120 inches, but these diameters may be more or less based on the design capacity and desired process result as relates to both gas and liquid flow rates and the type of combustion device (not shown in  FIG. 3 ) supplying hot gas to the desalination system evaporator  320 . 
         [0036]    In this example the weir  240  has a diameter of approximately 40 inches with vertical walls approximately 26 inches in length. Thus, the weir  240  forms an annular confined volume  270  within the evaporation vessel  230  between the inner wall of the weir  240  and the outer wall of the gas inlet tube  222  of approximately 6.54 cubic feet. In the embodiment of  FIG. 3 , twelve sparge ports  224  are disposed near the bottom of the gas inlet tube  222 . The sparge ports  224  are substantially rectangular in shape and are, in this example, each approximately 3 inches wide by 7¼ inches high or approximately 0.151 ft 2  in area for a combined total area of approximately 1.81 ft 2  for all twelve sparge ports  224 . 
         [0037]    As will be understood, the gas exits the gas inlet tube  222  through the sparge ports  224  into a confined volume  270  formed between the gas inlet tube  222  and a tubular shaped weir  240 . In this case, the weir  240  has a circular cross-sectional shape and encircles the lower end of the gas inlet tube  222 . Additionally, the weir  240  is located at an elevation which creates a lower circulation gap  236  of approximately 4 inches between a first end  241  of the weir  240  and a bottom dished surface  231  of the evaporator vessel  230 . The second end  242  of the weir  240  is located at an elevation below a normal or at rest operating level of the evaporative fluid within the evaporator vessel  230 . Further, a baffle or shield  238  is disposed within the evaporator vessel  230  approximately 8 inches above the second end  242  of the weir  240 . The baffle  238  is circular in shape and extends radially outwardly from the gas inlet tube  222 . Additionally, the baffle  238  is illustrated as having an outer diameter somewhat greater than the outer diameter of the weir  240  which, in this case, is approximately 46 inches. However, the baffle  238  may have the same, a greater or smaller diameter than the diameter of the weir  240  if desired. Several support brackets  233  are mounted to the bottom surface  231  of the evaporator vessel  230  and are attached to the weir  240  near the first end  241  of the weir  240 . Additionally, a gas inlet tube stabilizer ring  235  is attached to the support brackets  233  and substantially surrounds the bottom end  226  of the gas inlet lube  222  to stabilize the gas inlet tube  222  during operation. 
         [0038]    During operation of the desalination system evaporator  210 , the gases are ejected through the sparge ports  224  into the confined volume  270  between the outer wall of the gas inlet tube  222  and the inside wall of the weir  242  creating a mixture of gas and liquid within the confined volume  270  that is significantly reduced in bulk density compared to the average bulk density of the fluid located in the volume  290  outside of the wall of the weir  240 . This reduction in bulk density of the gas/liquid mixture within confined volume  270  creates an imbalance in head pressure at all elevations between the surface  280  of the evaporative liquid within the evaporator vessel  230  and the first end  241  of the weir  240  when comparing the head pressure within the confined volume  270  and head pressure within the volume  290  outside of the wall of the weir  240  at equal elevations. The reduced head pressure within the confined volume  270  induces a flow pattern of liquid from the higher head pressure regions of volume  290  through the circulation gap  236  and into the confined volume  270 . Once established, this induced flow pattern provides vigorous mixing action both within the confined volume  270  and throughout the volume  290  as evaporative liquid from the surface  280  and all locations within the volume  290  is drawn downward through the circulation gap  236  and upward due to buoyancy through the confined volume  270  where the gas/liquid mixture flows outward over the second end  242  of the weir  240  and over the surface  280  confined within the evaporator vessel  230 . 
         [0039]    Within confined volume  270 , the induced flow pattern and resultant vigorous mixing action creates significant shearing forces that are primarily based on the gross difference in specific gravity and hence momentum vectors between the liquid and gas phases at all points on the interfacial surface area of the liquid and gas phases. The shearing forces driven by the significant difference in specific gravity between the liquid and gas phases, which is, generally speaking, of a magnitude of 1000:1 liquid to gas, cause the interfacial surface area between the gas and liquid phases to increase significantly as the average volume of each discrete gas region within the mixture becomes smaller and smaller due to the shearing force of the flowing liquid phase. Thus, as a result of the induced flow pattern and the associated vigorous mixing within the confined area  270 , the total interfacial surface area increases as the gas/liquid mixture flows upward within confined volume  270 . This increase in interfacial surface area or total contact area between the gas and liquid phases favors increased rates of heat and mass transfer between constituents of the gas and liquid phases as the gas/liquid mixture flows upward within confined volume  270  and outward over the second end  242  of the weir  240 . 
         [0040]    At the point where gas/liquid mixture flowing upward within confined volume  270  reaches the elevation of tire evaporative fluid surface  280  and having passed beyond the second edge  242  of the weir  240 , the difference in head pressure between the gas/liquid mixture within the confined volume  270  and the liquid within volume  290  fluid is eliminated. Absent the driving force of differential head pressure and the confining effect of the weir  240 , gravity and the resultant buoyancy of the gas phase within the liquid phase become the primary outside forces affecting the continuing flow patterns of the gas/liquid mixture exiting the confined space  270 . The combination of the force of gravity and the impenetrable barrier created by the baffle  238  eliminates the vertical velocity and momentum components of the flowing gas/liquid mixture at or below the elevation of the bottom of the baffle  238  and causes the velocity and momentum vectors of the flowing gas/liquid mixture to be directed outward through the gap  239  created by the second end  242  of the weir  240  and the bottom surface of the baffle  238  and downwards near the surface  280  within the evaporator vessel  230  causing the continuing flow pattern of the gas/liquid mixture to assume a predominantly horizontal direction. As the gas/liquid mixture flows outwards in a predominantly horizontal direction, the horizontal velocity component continually decreases causing a continual reduction in momentum and a reduction of the resultant shearing forces acting at the interfacial area within the gas/liquid mixture. The reduction in momentum and resultant shearing forces allows the force of buoyancy to become the primary driving force directing the movement of the discontinuous gas regions within the gas/liquid mixture, which causes discrete and discontinuous regions of gas to coalesce and ascend vertically within the continuous liquid phase. As the ascending gas regions within the gas/liquid mixture reach the surface  280  of the evaporative liquid within the evaporator vessel  230 , buoyancy causes the discontinuous gas phase to break through the surface  280  and to coalesce into a continuous gas phase that is directed upward within the confines of the evaporator vessel  230  and into the vapor exhaust duct  260  under the influence of the differential pressure created by the fan/blower (not shown in  FIG. 3 ) supplying gas to the desalination system evaporator  210 . 
         [0041]      FIG. 4  is a top plan view of the desalination system evaporator  210  of  FIG. 3  illustrating the tubular nature of the weir  240 . Specifically, the generally circular gas inlet tube  222  is centrally located and is surrounded by the stabilizer ring  235 . In this embodiment, the stabilizer ring  235  surrounds the gas inlet tube  222  and essentially restricts any significant lateral movement of the gas inlet tube  222  due to surging or vibration such as might occur upon startup of the system. While the stabilizer ring  235  of  FIG. 4  is attached to the support brackets  233  at two locations, more or fewer support brackets  233  maybe employed without affecting the function of the desalination system evaporator  210 . The weir  240 , which surrounds the gas inlet tube  222  and the stabilizer ring  235 , and is disposed co-axially to the gas inlet tube  222  and the stabilizer ring  235 , is also attached to, and is supported by the support brackets  233 . In this embodiment, the confined volume  270  is formed between the weir  240  and the gas inlet tube  222  while the second volume  290  is formed between the weir  240  and the side walls of the evaporator vessel  230 . As will be understood, in this embodiment, the introduction of the gas from the exit ports  224  of the gas inlet tube  220  causes evaporative fluid to flow in an essentially toroidal pattern around the weir  240 . 
         [0042]    Some design factors relating to the design of the desalination system evaporator  210  illustrated in  FIGS. 3 and 4  are summarized below and may be useful in designing larger or smaller desalination system evaporators. The shape of the cross sectional area and length of the gas inlet tube is generally set by the allowable pressure drop, the configuration of the evaporator vessel, the costs of forming suitable material to match the desired cross sectional area, and the characteristics of the fan/blower that is coupled to the desalination system evaporator. However, it is desirable that the outer wall of the gas inlet tube  222  provides adequate surface area for openings of the desired shape and size of the sparge ports which in turn admit the gas to the confined volume  290 . For a typical desalination system evaporator the vertical distance between the top edge  242  of the weir  240  and the top edge of the sparge ports should be not less than about 6 inches and preferably is at least about 17 inches. Selecting the shape and, more particularly, the size of the sparge port  224  openings is a balance between allowable pressure drop and the initial amount of interfacial area created at the point where the gas is dispersed into the flowing liquid phase within confined volume  290 . The open area of the sparge ports  224  is generally more important than the shape, which can he most any configuration including, hut not limited to, rectangular, trapezoidal, triangular, round, oval. In general, the open area of tire sparge ports  224  should be such that the ratio of gas flow to total combined open area of all sparge ports should at least be in the range of 1,000 to 18,000 acfm per ft 2 , preferably in the range of 2,000 to 8,000 acfm/ft 2  and more preferably in the range of 2,000 to 8,000 acfm/ft 2 , where acfm is referenced to the operating temperature within the gas inlet tube. Likewise, the ratio of the gas flow to the cross sectional area of the confined volume  270  should be at least in the range of 400 to 10,000 scfm/ft 2 , preferably in the range of 500 to 4,000 scfm/ft 2  and more preferably in the range of 500 to 2,000 scfm/ft 2 . Additionally, the ratio of the cross sectional area of the evaporator vessel  230  to the cross sectional area of the confined volume  270  ((CSA vessel ) is preferably in the range from three to one (3.0:1) to two-hundred to one (200:1), is more preferably in the range from eight to one (8.0:1) to one-hundred to one (100:1) and is highly preferably in the range of about ten to one (10:1) to fourteen to one (14:1). These ratios are summarized in the table below. Of course, in some circumstances, other ratios for these design criteria could be used as well or instead of those particularly described herein. 
         [0000]    
       
         
               
               
               
               
             
           
               
                 TABLE 1 
               
               
                   
               
               
                   
                 Preferred 
                   
                   
               
               
                 Ratios 
                 Embodiment 
                 Acceptable Range 
                 Preferred Range 
               
               
                   
               
             
             
               
                 acfm:Total/CSA sparge ports   
                 2,000-8,000 acfm/ft 2   
                 1,000-18,000 acfm/ft 2   
                 2,000-10,000 acfm/ft 2   
               
               
                 scfm:/CSA confined volume   
                   500-2,000 scfm/ft 2   
                   400-10,000 scfm/ft 2   
                   500-4,000 scfm/ft 2   
               
               
                 CSA vessel /CSA confined volume : 
                 10:1-14:1 
                 3.0:1-200:1 
                 8.0:1-100:1 
               
               
                   
               
             
          
         
       
     
         [0043]    Turning now to  FIG. 5 , a desalination system evaporator is shown which is similar to the desalination system evaporator of  FIG. 1 , and in which like components are labeled with numbers exactly 300 greater than the corresponding elements of  FIG. 1 . The desalination system evaporator  310  of  FIG. 5  receives hot gases directly from an external source. The hot gases supplied by the external source may include gases having a wide range of temperature and/or specific components and these hot gases may be selected by one skilled in the art to achieve any specific rate of evaporation. 
         [0044]      FIG. 6  illustrates a desalination system evaporator  510  which is similar to the desalination system evaporators of  FIGS. 1 ,  2  and  5 , in which like elements are labeled with reference numbers exactly 500 greater than those of  FIG. 1 . However, the desalination system evaporator  510  is connected to a condensing unit  600  thereby forming a desalination system. The condensing unit  600  includes a condensing vessel  610  having a cooling fluid input port  612  and a cooling fluid exit port  614 . Vapor travels from the desalination system evaporator  510  through the gas exit port  560  along a transfer tube  616  and into a condensing tube  618  that is partially disposed within the condensing vessel  610 . Within the condensing vessel  610 , the condensing tube  618  is partially submerged in a cooling fluid which has a surface  680 . The submerged portion of the condensing tube  618  allows heat transfer from the vapor within the condensing tube  618  to the cooling fluid, thus allowing the vapor the vapor to condense. Accordingly, the condensed liquid accumulates at the lowest points of the condensing tube where the condensed liquid may be removed via one or more removal valves  622 . 
         [0045]    The embodiment of a desalination system evaporator  710  shown in  FIG. 7  includes multiple gas tubes  722  and multiple weirs  740 . The evaporator vessel  730  may include more than one gas tube  722  and/or more than one weir  740  to increase desalinating capability without a significant increase in the size of the evaporator vessel  710 . 
         [0046]    In a desalination system, the evaporative fluid introduced into the evaporation vessel  510  is generally salt water or brine. Concentrated brine may be removed through the outlet port  532 . As hot gas is introduced through the supply tube  522  and mixed with the brine, water vapor is absorbed by the hot gas and carried out of the evaporation vessel through the gas exit port  560 . Through the positive (or negative) pressure imparted to the hot gas via the fan/blower, the vapor is forced (or drawn) through the transfer pipe  616  and into the condensing vessel  610 . This movement may be facilitated by one or more fans or pumps located in the gas exit  624 . Regardless, as the vapor traverses the condensing tube  618 , the vapor cools as a result of heat transfer through the condensing tube  618  walls to the cooling fluid. As a result of vapor cooling, the ability of the vapor to retain water will decrease to the point of saturation. Thereafter, water will precipitate out of the vapor and collect in the condensing tube  618 . The amount of precipitated water will depend on the amount of cooling performed in the evaporation vessel and the entry temperature of the vapor. The precipitated water may be removed from the condensing tube through the wafer removal valves  622 . 
         [0047]    The embodiment of a desalination system evaporator  710  shown in  FIG. 8  includes multiple gas tubes  722  and multiple weirs  740 . The evaporator vessel  730  may include more than one gas tube  722  and/or more than one weir  740  to increase cooling capability without a significant increase in the size of the desalination system evaporator  710 . 
         [0048]    The desalination system described above has many advantages over known desalination systems. For example, a desalination system as described above has virtually no moving parts and no heat transfer surfaces in the evaporation unit. Thus, maintenance and replacement are greatly reduced. The disclosed desalination system is scalable to accommodate virtually any required fresh water output. Additionally, readily available heat sources and brine sources may be used. For example, solar energy could be used to heat the input gas and seawater could be used for the brine. When operated on solar energy the energy requirement would be significantly less than that that for conventional systems. In addition, the seawater could be used as both the cooling fluid in the condensing vessel and as the evaporative liquid in the evaporator vessel. These and many other advantages may be realized with the desalination system described herein. 
         [0049]    Desalination systems according to the disclosure operate at higher percentages of suspended solids and/or the ability to use cooling fluids with higher concentrations of dissolved solids (due in part to the turbulent flow described above). Thus, desalination systems according to the disclosure can be used to desalinate brackish water that has very high concentrations of contaminants and also require less preventative maintenance (i.e., cleaning due to chemical residue buildup and/or precipitate coating of internal surfaces) than conventional desalination systems. 
         [0050]    It will be understood that, because the weir and gas dispersion configurations within desalination system evaporators illustrated in the embodiments of  FIGS. 1-8  provide for a high degree of mixing, induced turbulent flow and the resultant intimate contact between liquid and gas within the confined volumes  70 ,  170 ,  270 , etc., the desalination system evaporators of  FIGS. 1-8  create a large interfacial surface area for the interaction of the evaporative fluid and the gas provided via die gas inlet tube, leading to very efficient heat and mass transfer between gas and liquid phases. Furthermore, the use of the weir and, if desired, the baffle, to cause a predominantly horizontal flow pattern of the gas/liquid mixture at the surface of the evaporative fluid mixture mitigates or eliminates the entrainment of droplets of evaporative fluid within the exhaust gas. Still further, the high degree of turbulent flow within the evaporator vessel mitigates or reduces the formation of large crystals or agglomerates and maintains the mixture of solids and liquids within the evaporator vessel in a homogeneous state to prevent or reduce settling of precipitated solids. This factor, in turn, reduces or eliminates the need to frequently clean the evaporator vessel and allows the evaporation to proceed to a very high state of concentration by maintaining precipitates in suspension. In the event that such solids do form, however, they may be removed via the outlet port  32  ( FIG. 1 ) using a conventional valve arrangement. 
         [0051]    While several of different types of desalination system evaporators having different weir configurations are illustrated herein, it will be understood that the shapes and configurations of the components, including the weirs, baffles and gas entry ports, used in these devices could be varied or altered as desired. Thus, for example, while the gas inlet tubes are illustrated as being circular in cross section, these tubes could be of any desired cross sectional shape including, for example, square, rectangular, oval, etc. Additionally, while the weirs illustrated herein have been shown as flat plates or as tubular members having a circular cross-sectional shape, weirs of other shapes or configurations could be used as well, including weirs having a square, rectangular, oval, or other cross sectional shape disposed around a fire or other gas inlet tube, weirs being curved, arcuate, or multi-faceted in shape or having one or more walls disposed partially around a fire or gas inlet tube, etc. Also, the gas entry ports shown as rectangular may assume most any shape including trapezoidal, triangular, circular, oval, or triangular. 
         [0052]    While certain representative embodiments and details have been shown for purposes of illustrating the invention, it will be apparent to those skilled in the art that various changes in the methods and apparatus disclosed herein may be made without departing from the scope of the invention, which is defined in the appended claims.