|Publication number||US3840002 A|
|Publication date||Oct 8, 1974|
|Filing date||Aug 6, 1973|
|Priority date||May 15, 1972|
|Publication number||US 3840002 A, US 3840002A, US-A-3840002, US3840002 A, US3840002A|
|Inventors||Douglas C, Phillips J, Young W|
|Original Assignee||Douglas C, Phillips J, Young W|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (6), Referenced by (30), Classifications (9)|
|External Links: USPTO, USPTO Assignment, Espacenet|
States Patent [191 ouglas et al.
1 1 METHODS AND APPARATUS FOR SUBMIERGED COMBUSTION (WITH AIR POLLUTION CONTROL)  Inventors: Clarence J. Douglas; Walter L.
Young; Jack H. Phillips, all of Tulsa, Okla.
 Filed: Aug. 6, 1973  Appl. No.: 385,748
Related US. Application Data  Division of Ser. No. 253,541, May 15, 1972,
 US. Cl. 126/360 A, 159/16 A  Int. Cl. F23c 5/00  Field of Search 126/360 R, 360 A, 368; 159/16 A  References Cited UNITED STATES PATENTS 2,522,475 9/1950 Walker 159/16 A 2,890,166 6/1959 Heinze 159/16 A 2,981,250 4/1961 Stewart 126/360 A 3,005,288 10/1961 McGugin et al. 126/360 AX [451 Oct. 8, 1974 3,224,855 12/1965 Plumat 126/360 AX FOREIGN PATENTS OR APPLICATIONS 328,524 9/1919 Germany 126/360 R Primary ExaminerWilliam E. Wayner Assistant Examiner-William C. Anderson Attorney, Agent, or Firm-Thomas M. Scofield [57 ABSTRACT Improvements in submerged combustion evaporators and heaters particularly adapted to the heating and evaporation of various heat sensitive solutions, including both methods and apparatus therefor;
Improved apparatus and methods for the discharge of products of combustion from the combustion chamber of a submerged burner into and through the body of a heat-sensitive solution, said discharge handled in such manner as to reduce air pollution resulting from the practice of the submerged combustion process with respect to the given solution, as well as improve the effectiveness of the burner, per se, and the submerged combustion process,
10 Claims, 9 Drawing Figures PATEmwnm s 074 SHEET 10! 5 Ill PATENTED 8 74 SHEET 5 OF 5 I r/ r x METHODS AND APPARATUS FOR SUBMERGED COMBUSTION (WITH AIR POLLUTION CONTROL) This is a division of application Ser. No. 253,541, filed May 15, 1972.
THE PRIOR ART The following specifications are improvements relating to and over the submerged combustion apparatus and methods of the following patents:
1. Doennecke et al., 2,086,902 Method of Recovering Anhydrous Sodium Sulfate, issued July 13, 1937;
2. Doennecke et al., 2,159,759, issued May 23, 1939 for Apparatus For Recovering Anhydrous Sodium Sulfate And The Like;
3. Cecil et al., 2,418,162 Apparatus And Method For Producing Inert Gas, issued Apr. 1, 1947;
4. Stengl, et al., 2,456,032 Fuel Control Device For Submerged Burners, issued Dec. 14, 1948; and
5. Young, et al., 2,723,659 issued Nov. 15, 1955 for Submersible Burner.
Further see Young et al., 3,526,264, Sept. 1, 1970, for Method Stewart 2,981,250, issued Apr. 25, 1961 for Submerged Combustion Heating Apparatus Wolfersperger, 2,787,318, Apr. 2, 1957, for Burner.
Norman, 2,594,063, Apr. 22, 1952 for Heating System Smith, 2,556,984, June 12, 1951 for Immersion Heater Kemp, 2,536,608, Jan. 2, 1951 for Immersion Liquid Heating...
Ekstrom, 2,375,840, May 15, 1945, for Liquid Heating Apparatus Brosius, 2,358,302, Sept. 19, 1944 for Submerged Burner" Stewart, 2,025,695, Dec. 24, 1935, for Domestic Heating Process CONVENTIONAL SUBMERGED COMBUSTION BURNERS AND PROCESSES A typical conventional submerged combustion process involves burning a gaseous fuel in a specially designed chamber under the surface of a heat sensitive liquid. A typical such burner will librate between four to five million BTU/cubic foot/atmosphere/hour. Most submerged combustion process heat leaves the open mouth of the burner as sensible heat in the hot combustion gases passing directly into contact with the solution.
A conventional, open-mouth submerged combustion burner discharges hot combustion gases directly into the heat sensitive liquid, thereby involving both flame impingement on the liquid and liquid entering the combustion chamber. A first problem of the latter two effects involves the thermal decomposition of the heat sensitive liquid by direct contact with the hot discharge gases from the burner. A second disadvantage involves the heat sensitive solution entering the burner combustion chamber through the hot gas discharge opening or ports. It should further be noted that decomposed heat sensitive liquid will travel with the products of combustion through the solution, leaving the evaporater or heater through the stacks and discharging into the atmosphere. Such discharge comprises both an objectionable direct loss of product and an air pollution nuisance.
In the conventional submerged combustion burner, air and the fuel mixture enter the combustion chamber through the velocity tube. Complete combustion of the air-fuel mixture takes place in the combustion chamber. Typically, the conventional submerged burner is completely or largely submerged into the heat sensitive solution.
Some solutions are more heat sensitive than others. Ammonium nitrate and magnesium nitrate decompose when hot. Sodium chloride vaporizes and condenses in fine particles of the aerosol type.
With sodium sulfate, there are typically losses of less than one-half percent utilizing standard or conventional submerged burners. On the other hand, there is some entrainment of sodium sulfate (which entrained product drops out close to the plant, typically) and some aerosol effect which drops out miles away therefrom. On the other hand, in ammonium nitrate, with a conventional submerged combustion burner, 50 percent losses may be experienced, mostly through de-.
composition. In such case, ammonia and nitrous oxide are also given off. With respect to sodium nitrate, this compound does not typically decompose much, but some aerosol effect is encountered.
One does not want drawback of solution into the burners. For example, there is a problem of possible explosion in concentration of ammonium nitrate. In any case, if one gets solution into the conventional (or any other) burner, the water or liquid tends to evaporate and solids build up and cake in the burner.
In the art of submerged combustion liquid concentration, there has been much speculation as to what causes given materials to break down. Prior to the instant improvement, the theory was that the greater part of material breakdown or decomposition was because solution was actually entering the burner chamber and being partly incinerated. The instant improvement and invention has proved this theory.
OBJECTS OF THE INVENTION Therefore, an object is to provide a submerged combustion burner construction effectively operating to prevent heat sensitive solution from entering the combustion chamber of the burner or area of highest termperature gases therein, where same could decompose thermally.
Another object of the invention is to improve submerged combustion burner construction, thereby minimizing decomposition of heat sensitive liquids by preventing direct contact of hot discharge gases and flame therewith. This also prevents loss of valuable materials being concentrated and, additionally, minimizes air pollution produced by the use of the apparatus and practice of the process.
Yet another object of the invention is to provide a greatly improved submerged combustion burner design which, by virtue of considerably increasing the heat exchange surface in contact with the heat sensitive liquid, considerably lowers the temperature of the combustion gases from the burner before they discharge directly into the heat sensitive solution. This also further prevents thermal decomposition of the solution and further minimizes or prevents air pollution resulting from operation of the apparatus and practice of the process.
Another object is to provide improvements in submerged combustion burner construction and methods of operating same, wherein process operation is feasible with less burner submergence than that required of a normal or conventional burner. This, under certain circumstances, reduces the back pressure on the system, thereby resulting in a reduction of horsepower requirement to overcome the static head or submergence of the burner in the liquid being concentrated.
Other objects of the improved submerged combustion burner construction and methods of operating a submerged combustion process include: (1) greatly heightened feasibility of control of air pollution from practice of the process and use of the apparatus; (2) the provision of both multiple and indirect impingements of heat into the solution being concentrated with lower temperature gases being discharged ultimately into the heat sensitive solution than conventional; (3) minimal or no decomposition of notoriously decomposition-prone solutions and compounds; (4) effective and universal prevention of entrance of solution into the burner combustion chamber or area; (5) less actual loss of solution from practice of the process and use of the apparatus, whereby to provide a greater quantity of salable product.
Another object of the invention is to provide a submerged combustion burner of improved construction and operation wherein, where excess air is employed in the combustion process, the same amount of excess air will temper the heat more than in a standard burner.
Another object of the invention is to provide submerged combustion burner devices and methods of operating same which permit further and greater concentration of known compounds and solutions than ever before.
Another object of the invention is to provide burner devices and processes of use of same wherein solution concentration not only takes place with less decomposition losses, but, also, markedly less aerosol type losses, the latter type less usually causing difficult and offensive air pollution problems.
Another object of the invention is to particularly provide a new construction of submerged combustion burner which, by its very physical construction, results in a different heating and concentration process, particularly in that the device does not put all of the heat in all at one spot in the concentration vessel. In the instant improvement all of the heat produced goes into the solution, more uniformly, in two different ways. The first way involves indirect heat exchange between the burner body itself and the burner arms and extension parts therefrom. The second way involving direct heat input into the solution at spaced, dispersed, discreet outlets. As a result, compared to a conventional submerged combustion burner, there is markedly less local overheating than is present conventionally around the base of the burner, where all heat is concentrated coming out of the bottom openings.
Another object of the invention is to provide unique combinations and arrangements of the novel burner construction and solution tanks or vessels employed therewith, where a lower level of solution is feasible in the vessels, less violent agitation is employed, aeration of the burner containing tank is effected and circulation between at least a pair of tanks is created by the structure of the tanks and their inter-connections. In addition, a higher level may be employed for a given solution and, with respect to the relatively quiescent zone of the paired vessel, solids present are agitated.
Other and further objects of the invention will appear in the course of the following description thereof.
DESCRIPTION OF THE DRAWINGS In the drawings, embodiments of the invention are shown and, in the various views, like numerals are employed to indicate like parts.
Referring to the figures, FIG. 1 is a side, partly sec tional view of liquid concentrating apparatus involving a pair of interconnected tanks utilizable for the concentration of heat sensitive solutions with one form of the improved burner (utilizing secondary air) installed in the left hand tank in the view.
FIG. 2 is a top view of the left hand tank in the view of FIG. 1 taken along the lines 2-2 of FIG. 1 in the direction of the arrows,
FIG. 3 is an enlarged detail of the burner construction of FIGS. 1 and 2 (using secondary air).
FIG. 4 is a side, partly sectional detail of an improved submerged combustion burner construction (not using secondary air) installed in a tank analogous to the left hand tank in the view of FIG. 1.
FIG. 5 is a fragmentary top view of the submerged combustion burner of FIG. 4.
FIG. 6 is a side, partly sectional view of a third form of submerged combustion burner and tank construction (utilizing secondary air).
FIG. 7 is a top view of the construction of FIG. 6.
FIG. 8 is a side sectional view of a liquid concentrating tank employing a refractory lined burner.
FIG. 9 is a view along the lines 99 of FIG. 8 in the direction of the arrows.
DESCRIPTION OF THE INVENTION Submerged combustion burners may vary in capacity from 150,000 BTU/hour up to 30 million BTU/hour. With conventional burners the products of combustion may be discharged from the end of the burner at 2200 F. for 150,000 BTU/hour pilot plant burners and may be as high as 3200 F. for 30 million BTU/hour burners.
With respect to the burner construction improvements, per se, the burner may or may not employ secondary or excess air. In either case, heat exchanger tubes are installed at the normal or conventional burner hot gas discharge openings. The hot combustion gases from the burner must then pass through the heat exchange tubes before a discharge from the ends thereof. The heat exchange tubes are so configured and of a sufficient length and number whereby to cool (to some extent) the hot gases directly from the burner, thereby aiding in a preventing thermal decomposition of heat sensitive solutions. The passage of the combustion gases through these configured, multiple heat exchange tubes operates to indirectly cool the heat sensitive solution contacting the outside of the heat exchange tubes, thereby lowering the temperature of the hot combustion gases passing therethrough, as well as their exit temperature.
The tubes are typically spaced equally around the perimeter of the lower end of the combustion chamber of the burner. The presence and structure of the tubes also prevents heat sensitive solution from entering the conventional gas discharge openings and coming into contact with the flame in the combustion chamber. Yet further, the provision of heat exchange tubes (configured as shown) enables the products of combustion to be discharged at a plurality of spaced, positioned, discreet points within the solution away from the centrally positioned burner body. Thus, there is indirect heat exchange between the gases and the solution from the submerged burner body and the heat exchange tubes and multiple contact direct heat exchange between the combustion gases and the solution at the plurality of discharge points.
There is not change in the mechanics or mechanisms of flame combustion in the burner, per se.
If secondary air is added, there is typically a manifold and blower involved. Secondary air added typically functions as cooling air, it is not employed as an aid to complete combustion. No marked increase in efficiency with respect to fuel consumption is achieved because the gas going off from the concentrating vessels (and the solution leaving) depart at the same temperature as they would utilizing a standard or conventional burner. However, there are markedly less deleterious effects on the heat sensitive solutions being concentrated.
It should be understood that, in the use of a submerged combustion burner, level controls (solution level with respect to the burner in the concentrating vessel) are typically employed. Thus, typically, there are four level controls. First, there is a high level contact which monitors and limits the upper level of solution permitted in the vessel. Secondly there is a normal and preferred level below high level. The third level monitored and controlled is below the normal level, identified as the low level contacts. Therebelow is the fourth level monitored and controlled, comprising a shut-down and alarm level. These are conventional and will not be re-described with respect to the instant system, although the positioning of these four levels with respect to a given burner or burner and heat exchange arm configuration may vary for a given system.
FIGS. 13, INCLUSIVE Referring first to FIG. 1, therein is shown a pair of vessels generally designated and 11, here employed in an evaporator system. Tank 10 typically has a cylindrical side wall 10a with a frusto-conical lower section 10b and fiat circular bottom wall 100. The upper end of tank 10 is capped by flat circular top 10d received on circumferential ring flange 101:. An opening 14 is provided in cylindrical upper wall portion 10a to which connects larger diameter pipe or duct 15. Optimal and preferred liquid level in vessel 10 is seen at 16, just overflowing the lower boundary of pipe or duct 15.
A burner body 17 is shown substantially submerged in the liquid 18 being concentrated having feed tube or duct 17a extending upwardly therefrom and through an opening provided in top or cap 10d. This burner construction is conventional and the lower portion of the burner body is provided with conventional outlet openings designated in FIGS. 1 and 3 as 19 and 20. Attached to and running from each of said openings 19 and 20 are elongate heat exchange tubes 21 and 22 which connect into elongate, vertical tubes or ducts 23 and 24 (FIGS. 1 and 3) which serve to provide secondary air and are connected at their upper ends to manifold 25. v
A drain pipe 26 having valve fitting 27 and hand control lever 28 thereon are provided centrally of bottom wall 10c.
Vessel 11 has elongate cylindrical side wall Ila and top wall 11b with central opening therein. The lower portion of vessel 11 comprises elongate conical shell 11d having drain pipe 29 therefrom controlled by valve 30. Pipe 29 connects to and leads into discharge or product withdrawl pipe 31. The liquid level in tank 11 is seen at 32. Opening 33 is provided through the side of conical wall portion 11d connecting to the other end of duct or passage 13, whereby there is liquid flow intercommunication between the lower portions of the vessels l0 and 11. Circular opening 34 is provided in cylindrical wall portion 11a of vessel 11 to receive the end of duct 15 opposite that connecting to opening 14 in vessel 10 wall portion 10a.
Arrows are provided within ducts l3 and 15 and the lower portions of vessels 10 and 11 to show the direction of liquid flow under the action of the burner system in vessel 10.
At the upper end of vessel 11, gas discharge pipe 35 is provided having right angle take-off pipe 36 therefrom.
Referring to FIG. 2, this shows a plan view of vessel 10 of FIG. 1. The centrally located burner body 17 and the multiple heat exchange tubes 21a, 21b, 21c and 21d and 22a-d, inclusive, connecting to the secondary air tubes 23, 23a-c and 24, 24a-c may be clearly seen. The geometry of tubes 21-22 is for maximum inclusion thereof in the vessel. The mulitplicity of heat exchange tubes and secondary air input ducts for said tubes seen in FIG. 2 are not shown in FIGS. 1 and 3 for clarity. Additionally, in those views, the angling in plan view of the heat exchange tubes is also not illustrated for clarity. Such angling and geometry, as noted, serves the purpose of crowding more heat exchange tubes and secondary air input tubes into a relatively lesser diameter tank. There is also seen igniter tube 37 of conventional structure and purpose, connecting into the lower portion of burner body 17 in FIG. 2.
From FIG. 3, an enlarged detail of the structure seen in FIG. 1, it may be seen that the burner outlet openings l9 and 20 may be vertically displaced from one another for better spacing and fitting of multiple heat exchange tubes on the burner body radially, with respect to one another.
Turning now to the form of the invention seen in FIGS. 4 and 5, there is no substantial distinction between the bumer construction in the left-hand side of FIG. 1 and the view of FIGS. 2 and 3 as that shown in FIGS. 4 and 5, save for the fact that no secondary air is employed in or in conjunction with the burner. Accordingly, all of the parts of both the vessel and the burner which are identical or substantially identical to like parts in FIGS. l-3, inclusive, are numbered the same as the parts in those views, but primed. These parts will not be redescribed for brevity. Another slight distinction between the views is that the lower passage 13' is positioned slightly higher on the cylindrical portion 10a of the wall.
It may also be observed that, in the lower portion of the view of FIG. 4, two of the burner arms only are illustrated for clarity, taken off at the same level. However, reference to FIG. 5 will show, first, that burner arms are provided at two levels, for optimum distribution of the products of combustion and the pipes or channels themselves and, secondly, an even greater number is shown packed into the given volume of the vessel.
A plurality of U-shaped connecting members, inverted, are seen at 40 (for the right-hand side of the vessel in the view of FIG. 4) and 41 (the left-hand side of the vessel in the view) which make connection between the members 22' and 21' respectively and vertically downwardly extending pipe or duct members 42 and 43, respectively. The downward extension of the members 42 and 43, both with respect to the burner outlets 19 and 20' (at the two levels) and the passage 13' will be discussed with respect to description of the function of the device. (Referring to FIGS. 4 and 5, the solution level 16' is always maintained a few inches above the bottom of opening Opening 13' is always located below the bottom of the burner.)
FIGS. 6 and 7 show a third form of submerged combustion burner and tank construction, utilizing secondary air in the manner of FIGS. 1-3, inclusive. FIG. 6 is a side, partly sectional view of a vessel having the improved burner construction seen in the view of FIG. 6 at the right, with the blower and ducting for inputing secondary air seen in the left side of the view. In FIG. 7, there is seen a plan view of the apparatus of FIG. 6.
In this modification, it is contemplated that a relatively lesser volume of secondary air be mixed with the hot combustion gases from the burner, whereby the secondary air pipes are of lesser diameter and their connection into the or with the hot gas heat exchange tubes from the burner is different. Thus, in this modification, the volume of secondary air is such that the hot gases from the burner are entraining secondary air. In the modification of FIGS. 1-3, inclusive, the volume of secondary air input is such that the opposite is true, namely, the secondary air is entraining the hot gases from the burner.
Turning to the figures, at 50 there is generally disignated a liquid concentrating tank having an upper cylindrical portion 50a and a lower frusto-conical portion 50b with bottom 50c. An opening is provided centrally of bottom 50c with drain pipe 51 thereon controlled by valve 52. The upper portion of the vessel has an inlet pipe or feed pipe 53 controlled by a valve 54. Top circumferential flange 55 removably mounts lid or top 56 in sealing fashion. Gasketing may be provided and bolts controlling the engagement also.
Burner 57 has a lower larger diameter burner body 57a with combustion mixture feed tube or duct 57b leading into the top thereof. Suitable support forms or struts 58 connect the burner 57 to the cover or lid 56 and settler the burner within the tank 50. The input of the gaseous combustion mixture to feed tube 57b is centrally down upper pipe 59.
A plurality of openings 60 and 61 are provided, spaced and staggered in the lower portion of the burner body 57a from which lead hot gas heat exchange tubes 62 and 63. The configuration and geometry of these tubes is analogous to that seen best in FIGS. 2 and 5 and will not be redescribed. However, in the particular members just described and numbered, upper U-bends 64 and 65 connect to vertical, downwardly leading discharge portions 66 and 67 of the heat exchange tubes.
conventional igniter pipe 68 is provided with respect to said vessel, as well as gaseous output pipe 69 connected to the upper portion of cylindrical vessel wall 50a. The liquid level in the vessel is seen at 70.
A ring manifold 71 has connected to the lower end thereof and extending through the cap 56 a plurality of secondary air discharge pipes or tubes 72. The latter connect into the outer portions of the U-bends (65 and 64, for example) as at 73. Pipes 72 connect to each of the U-bend portions of the hot gas heat exchange tubes.
The secondary air is provided, typically, by a blower 74 of conventional type driven by motor 75 mounted on a suitable structural support as at 76. A filtersilencer 77 may be provided if desired over the blower inlet. Duct 78 leads from the outlet 74a of the blower through expansion joint 79, connecting with suitable piping of desired length, composition and diameter 80.
A pitot tube 81 connecting to manometer 82 may be provided. Flanges 83 on duct and inlet pipe 84 to manifold 71 preferably carries wafer valve 85. At 86 there is seen sensing means cooperating with means providing a high temperature cutoff. Wafer valve is a butterfly valve used to regulate the amount of secondary air.
Referring now to FIGS. 8 and 9, this drawing shows the improved burner construction in use with resepct to a refractory lined oil burner.
At 90 is generally designated a heater tank having the following parts. At the lower end thereof is a conical or frustoconical drain section 91 having a drain pipe 92 connected at the lower portion thereof, controlled by any suitable valve means of conventional type, not shown. Integrally connected to the upper end of conical portion 91 is a cylindrical liquid receiving heater tank portion 93 having a circumferential mounting flange 94 at the upper end thereof. Carried by the latter is a cylindrical refractory containing and carrying cylindrical pipe section 95. Section 95 has a lower flange 96 mating and engaging with flange 94 and an upper circumferential mounting flange 97. Continuous with or connected to lower flange 96 is a plate or sheet 98 serving as a floor for the refractory 99 and having a central opening 100 therewithin.
Above section 95 there is provided a second cylindrical section 101 having lower mounting flange 102 mating with and engaging with mounting flange 97 of section 95 and an upper partial ring cap 103 having a central opening 104 therein. Cap 103 overlies the central block or portion 105 of refractory and further serves as a mounting base for the upper cylindrical portion 106. The latter has lower support flange 107 and upper, inwardly extending ring cap 108 having central opening 109 therewithin. The upper portion or body 110 of refractory material is positioned within section 106. Refractory bodies 110, 105 and 99 have central openings 110a, 105a and 99a, respectively. The former two are cylindrical and of uniform diameter, while the latter, 99a, tapers downwardly in frusto-conical (inverted) shape as shown in the view.
A conventional oil burner 111 having an air input line 112 and a fuel input line 113 connected thereto (the latter controlled by valve 1130) is provided, mounted on flange 114 at the upper end of the tank, centered on flange 108 whereby to provide combustion therebelow as indicated schematically at 115.
Returning to cylindrical section 93, there is provided a pair of openings 93a (lower) and 93b (upper) connected to or having connected therewith relatively small duct or pipe 116 and relatively large pipe or duct 117, respectively. The liquid level 118 within tank portion 93 is carried just over the lower boundary of upper large pipe or duct 117.
Welded or otherwise fixedly attached to ring plate 98 and extending downwardly therefrom is frusto-conical duct or pipe portion 119. Fixed to or fastened to the lower end of the latter is cylindrical pipe or duct portion 120, commonly referred to as the dip pipe. A plurality of openings 121, 122 are provided spaced circumferentially around the lower portion of pipe 120 whereby to carry hot gas heat exchange tubes 123 and 124 thereon or connecting thereto. It should be understood that any configuration of openings 12] and 122 analogous to the openings 19, 20, 19 or 20' seen in the previous figures may be employed. Thus, the opposed arms 123 and 124 are just illustrating this latter for convenience, clarity and simplicity. Likewise, the plan configuration of the arms 123 and 124, as well as the attachments thereto, may be as in previous figures.
Connected at the upper ends of members 123 and 124 are U-bends 125 and 126 to which are connected vertically oriented, downwardly extending members 127 and 128.
Contrasting this form of burner and tank with respect to the previous air-gas forms, the following is noted. In the oil burner, air and fuel are introduced and mixed into the desired ratio, discharging into the combustion chamber. The combustionchamber is the area in which the combustion process takes place. This is defined by passages or openings 110a, 105a and 99a. This may be refractory lined as shown, or it may be of metal construction, depending upon the temperatures of the combustion gases, the amount of cooling to which the chamber is exposed, etc. The chief purpose of dip pipe 120 is to discharge the hot gases beneath the surface of the liquid.
SPECIFIC EXAMPLE In the use of the system and process improvements of the instant invention, utilizing the improved apparatus, as a specific example, the problem was to concentrate a 40 gpm effluent stream of 3 percent nitrogen solution (Wt. percent) to 20 percent. The goal was to recover only the concentrate. The nitrogen was in a water solution of ammonium nitrate with smaller amounts of sodium nitrate. The primary purpose in concentrating this solution was for waste disposal; in addition, the 20 percent nitrogen solution concentrate could be used as fertilizer.
Utilizing a conventional submerged combustion unit, there were discouraging results, with the most serious observation being that the ratio of sodium nitrate to ammonium nitrate was increased in the product compared to the feed. The obvious conclusion was that ammonium nitrate was being decomposed in the unit. The decomposition rate being in the range of 50 percent, it was evident that same was probably caused by high temperature gases, whereby it would be necessary to 7 gases leaving the burner. However, the burner gases at approximately 3000 F., even introducing excess air, proved to be supercritical in certain temperature ranges and, further, there were more stack gases leaving the evaporator. Thus, with the solution temperature at F., getting a concentration of l 1 percent nitrogen with only 5 percent decomposition of ammonium nitrate had to be contrasted with the decomposition rate going up to approximately 50 percent when the temperature of solution went up another 10 F. Utilizing air-gas ratios from the theoretical air-gas ratio to 33 percent excess air still resulted in ammonium nitrate being decomposed (from appearance of the stack gases brown fume) and analysis of the product still showed an increase in the sodium nitrate to ammonium nitrate ratio).
When the improved burner construction employing twelve distribution points into the solution tank (a dozen heat exchange tubes of the type shown in the drawings) was employed, the stack appearance was greatly improved. Thus, after ignition of the burner, after an hour-and-a-half, the solution temperature was up to about 200 F. The stack looked very good at this temperature and the steam disappeared after drifting about 500 to 600 feet. In 2 more hours, the normal operating temperature of 218 F. was reached. At this temperature there was a slight yellow hue to the steam as it left the stack and, after the steam disappeared, there was a slight gray hue left. Laboratory samples indicated the ammonium nitrate-sodium nitrate breakdown to nitrous oxide to be about 8 percent at 218 F., this comparing to about 50 percent at an even lower temperature, because this was the first time the system was ever operated at 218 F.
On a later 52 hour run, 41.9 gallons per minute of product was fed with 6.3 gallons per minute of product taken out at 19 percent concentration. The ratio of ammonium nitrate to sodium nitrate in the feed solution was 65 percent and the ratio in the product solution was 63 percent, with very little decomposition loss.
At a later date, the submerged combustion unit performed with a feed rate of 41.9 gallons per minute, product rate 6.3 gallons per minute, at a BTU/lb. water evaporated of 13.5. Some decomposition of ammonium nitrate occurred and the loss was estimated to be about 4 percent of that in the feed. The stack plume was much improved. The visual evidence of nitrous oxide in the gases was no longer seen but evidently there was some minor loss of material in the form of aerosols.
The improvement in the appearance of the stack gases and production of the ammonium nitrate loss from 8 to 4 percent was accomplished by blanking off a line from the vapor disengagement tank to the heater tank, causing a greater flow of solution through the line past the lower end of the burner.
At a feed rate of 41.9 gpm (8.92 lbs. per gallon) of 10.13 percent ammonium nitrate solution, the feed will contain 27.2 tons per day of ammonium nitrate. A 50 percent loss would be 13.6 tons per day; an 8 percent loss would be 2.18 tons per day and a 4 percent loss would be 1.09 tons per day. The submerged combustion unit was 24 million BTU/hour whereby, utilizing 12 heat exchanging pipes on the bumer, emitted the gases at 12 points equivalent to 2 million BTUs/hour from each pipe.
GENERAL STRUCTURAL AND FUNCTIONAL CONSIDERATIONS It should be noted that the system of FIG. 1 shows the burner tank coupled with a disengagement tank 11. Also, the burner tanks of FIGS. 4 and 8 are shown with duct or pipe connections for coupling with disengagement tanks if desired. The second or disengagement tank 11 helps in the entrainment problem.
The advantage or advantages of the coupled tanks lie in the following. First, one may operate with lower levels in the tanks and thus there is a lower static head that the burner must operate against. Secondly, there is a quiescent zone in the disengagement tank 11 where the vapor disengages and there is less entrainment.
In tank A (10) there is an aerated column from the burner gases which causes circulation according to the arrows.
With respect to quantity of solids in the double tank system illustrated utilizing the improved burner, if there are heavy solids present, one preferably does not employ the two tank system with the circulation illus trated in FIG. 1. It is preferred to use a cone bottom tank as in the B tank of FIG. 1 to remove solids. A sharper angled tank cone is employed when solids are coming off the bottom. This angle is preferably 45 to 60. Without the sharp angle, solids might build up on the side walls.
With respect to the function of the burners, generally speaking, the purpose of the lesser diameter (upper) velocity tube above the burner body is to prevent actual combustion within it, whereby to force combustion in the body of the burner therebelow.
With respect to the number of heat exchanging arms or pipes employed with respect to a given size burner body, if too few are employed, (less tube cross sectional area than the cross sectional area of the burner), there will be back pressure on the burner and blower powering same. It is better to have more tubes than the area of the burner and thus have lower pressure therewithin.
The devices may be operated with the solution level above the backbend of the heat exchange tubes if the operator will blow the device out before starting up. This gives the advantage of more area for indirect heat exchange, but, in some solutions, there might be a problem with explosions (ammonium nitrate). One does not want drawback of solution into the burner. Thus, if one gets solution into the burner, this will result in liquid evaporating and solids caking within the burner and arms.
The basic purpose of having the solution level up on the burner body is to keep the burner cool. One further considers the splash level on the burner and arms. The level is controlled by suitable conventional level controls on the tank (not described).
Providing the instant arm improvements (and more and longer of same) or adding an air manifold on the burner body operate to achieve the same effects. It is possible to combine the two, using the heat exchanging ducts of the instant invention, more and longer ones of same and adding an air manifold to the burner body. The provision of the return bends and their height corresponds to both the burner body height and the splash area.
Since the combustion gases and air are always hotter than the solution, one can add secondary air despite the number of additional heat exchanging ducts employed. Secondary air addition lowers the boiling point of the solution.
Having thus described my invention, I claim:
1. A method of concentrating heat sensitive liquids comprising the steps of:
a. establishing and maintaining a liquid body to be concentrated in two adjacent vessels having both an upper conduit communicating therebetween, same both considerably above and slightly below the common, maintained liquid level in said vessels, and a lower, large volume conduit interconnecting said vessels below the common liquid level therebetween;
b. burning a combustible mixture of fuel and air in a combustion chamber positioned substantially entirely below the surface of a first portion of the liquid body being concentrated in a first one of said vessels, the combustion chamber being in direct contact with said liquid body first portion;
. discharging the products of combustion from the lower portion of the combustion chamber at a plurality of locations in said liquid body first portion;
. then passing said products of combustion from said combustion chamber in indirect heat exchange with said liquid body first portion and below the surface thereof through and within a plurality of tubes which first rise in said body first portion substantially above said discharge locations at least substantially to the top of the combustion chamber and thereafter descend in said body first portion at least substantially to the level of said locations;
. passing said products of combustion into said liquid body first portion at a level substantially below the liquid body first portion surface and at a plurality of points in said liquid body first portion substantially spaced away from said conbustion chamber for direct contact with said liquid body first portion;
f. circulating liquid from said first vessel to the other via the upper conduit and from the second to the first vessel via the lower conduit, whereby to cool the combustion chamber and tubes discharging combustion gases therefrom by circulating liquid in contact therewith;
g. discharging gaseous products of combustion and vapors overhead from the second vessel, and
h. removing concentrated liquid from one of said two vessels below the liquid level maintained therein.
2. A method as in claim 1 wherein said second vessel has a conical bottom extending substantially below the second conduit and product is removed from said conical bottom.
3. A method as in claim 1 wherein said first vessel has a frusto-conical bottom into the wall of which the second conduit connects and discharges.
4. A method as in claim 1 wherein the second conduit discharges from the second vessel into the first vessel below the level of the combustion chamber and the discharge tubes connecting thereto.
5. A process as in claim 1 wherein secondary air is added into the combustion gases within said discharge tubes before said combustion gases are discharged into the liquid body first portion.
6. Means for treating and concentrating heat sensitive liquids with gaseous products of combustion comprising, in combination:
a. a first liquid containing vessel having a submerged combustion burner therein operative to flow gaseous products of combustion through the liquid in said first vessel within a multiplicity of independent passageways and thereafter into the liquid of said first vessel;
b. said burner having an elongate, hollow, vertical combustion chamber;
c. said chamber having at the distal end thereof a plurality of ports for discharge of combustion products from said chamber;
d. means connecting with the proximal end of said combustion chamber for continuously supplying thereto a gaseous combustible mixture;
e. pipe means connecting at one end thereof to each said chamber discharge port, extending substantially parallel with the combustion chamber axis but in the opposite direction with regard to gas flow in a portion of the length thereof and further having an open submerged end return bend of sufficient length, whereby, when the combustion chamber is substantially submerged in liquid to be heated, a portion of the return bend is above the liquid surface and the portion thereof furthest from the combustion chamber discharge port is submerged in said liquid;
f. a second liquid containing vessel positioned closely adjacent said first vessel;
g. a first liquid and gas carrying flow line interconnecting said two vessels at a level both considerably above and slightly below the maintained common liquid level in said vessels, whereby gas and liquid can readily flow therebetween from said first to said second vessel;
h. means for exhausting combustion gases and vapors from said second vessel overhead above the liquid level therewithin;
i. a second large volume liquid carrying line interconnecting said two vessels below the common liquid level therewithin, whereby liquid can flow therebetween, thereby to continuously circulate the liquid being concentrated in heat exchanging contact with the combustion chamber and pipe means connected therewith, and
j. a product withdrawal line on one of said vessels below the maintained liquid level therein.
7. Means as in claim 6 wherein the second vessel has a conical bottom extending substantially below the second liquid carrying line and product is removed therefrom.
8. Means as in claim 6 wherein said first vessel has a frusto-conical bottom and the second flow line connects thereinto to pass liquid therethrough.
9. Means as in claim 6 wherein said second flow line is positioned to recycle said concentrated liquid into said first vessel below the combustion chamber and discharge pipes connected thereto.
10. Means as in claim 6 including means for flowing secondary air into said burner pipes prior to their termination away from said combustion chamber.
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|U.S. Classification||126/360.2, 159/16.2|
|International Classification||B01D1/14, F23C3/00, B01D1/00|
|Cooperative Classification||F23C3/004, B01D1/14|
|European Classification||B01D1/14, F23C3/00C|