HEATED RAILROAD TANK CAR

Abstract: A heated railroad tank car (10) having a heat exchanger apparatus within the tank car spaced above the bottom of the tank car to form a dead space or compartment. A pair of heat exchanger units (28, 30) which extend inwardly and downwardly from the ends of the car in an end-to-end relationship. Each of the heat exchanger units has top (32) and bottom (34) plates spaced apart and being sealed at their periphery (40) with a plurality of spaced apart plates (36) secured thereto and extending therebetween to create a baffle system between the top and bottom plates of longitudinal passages. Each of the heat exchanger units has an inlet (42) formed at its inner end to enable steam or hot water to be introduced into the heat exchanger unit. The heated water or steam is passed through the heat exchanger unit by the baffles and is subsequently discharged from the heat exchanger unit by an outlet (44) in communication therewith. The upwardly steam conducting flow channels are preferably smaller in area cross-section than the downwardly conducting channels to reduce back pressure. Drainage tubes (46, 48) in the lowermost portion of the apparatus communicate between the flow channels and drain outlet to provide total drainage of condensate by purging and by gravity flow.

Description: HEATED RAILROAD TANK CAR This invention relates to a heated railway tank car and more particularly to a heated tank car having the heat exchanger assembly provided therein. Railway tank cars are commonly used to transport liquid commodities that must be heated to enable the material to flow and unload through the bottom or top mounted discharge valve. At the present time, the material is heated by steam which passes through coils positioned on the exterior surface of the car or by coils which are positioned in the interior of the car. Typical of the prior art devices may be found in United States Patent Nos. 2,145,614; 2,558,648; 2,772,784; 3,143,108; 3,176,764; 3,228,466; 3,595,307; and 3,685,458. It is apparent from the above-identified patents that there are large areas of the cars that are not subject to the heated steam and that the tank saddles and underframes attached to the bottom ' end of the tank act as large heat sinks which radiate heat out to the air rather than inwardly to the product. A problem also associated with the external and internal coils is that they are sub¬ stantially horizontally disposed which makes them difficult to drain after the steam has been disconnected thereby causing freezing and corro¬ sion and subsequent failure to the coils. Still another problem associated with the prior art is that the material at the upper end of the tank is heated faster than the material at the bottom of the tank. The material at the upper portion of the tank is heated for longer than is desirable since the material will not begin to flow from the tank until the material around the discharge valve has been sufficiently heated to enable it to flow from the tank. Still another problem associated with the prior art devices is that a "boot" of material is formed in the bottom end of the car. The "boot" forms due to some commodity precipita ts going to the bottom of the car due to heating and to lack of agitation. The "boot" also forms due to the heat sink effect of the steel attached to the tank at this particular location. The "boot" is the product remaining in the car after the car has been unloaded " and the "boot" keeps building or accumulating, thereby reducing the effective capacity of the car. At some time, the "boot" must be removed by chipping or other manual removal process. Also, the prior art rail tank car using heated coils is not too suitable for the unloading of congealable, heat sensitive materials. Because of this, many problems have been incurred. First, the quality of the many commodities has been affected due to over heating. On certain materials, overheating has caused the complete rejection of the commodity by the customer. Second, heating by present methods has proven ineffective due to the problem of film buildup on the surfaces. This is caused by the settling of solids to the bottom of the car during the heating process. If not removed, the baking of the product to the surface will greatly reduce heating efficiency. The boot upon heating can also cause corrosion of the bottom of the tank. The third, and often overlooked problem, is contamination of new high quality material by burnt commodity or heel. Fourth is the hazard which is presented to a person who must enter this enclosed environment to remove settled or burnt material. The concept being proposed is the use of a heat system to be installed in the bottom of a tank car with sufficient slope to permit total drainage of the commodity. Such a system would concentrate the heat in the bottom of the car to obtain maximum transfer of heat at the bottom of the commodity (lading) . The heated portion of the lading, as it rises through the lading, causes the unheated por¬ tions of the lading to descend to the bottom to effectively cause mixing or rolling of the lading. Such thorough and uniform heating of the lading prepares the lading for faster unloading and pre- vents the lading being subjected to excessive heat which burns or caramelizing the lading. Also, the application of the heat at the bottom of the lading causes faster melting of the lading in and around the outlet valve. Heating efficiency is greater with the new system during unloading because the entire heating surface remains in contact with the lading during the unloading until the tank is almost empty. Coil cars lose heating efficiency through exposure of coils as the lading level drops in the car. Initial tests indicate that the use of a heated exchanger in contact with the bottom of the lading improves heating efficiency. Data taken, using a series of probes located in tank cars, with readings taken every five minutes, proved that the improved heat system gave uniform heating of the contents. It was noted during the tests that a rolling action occurred during the heating process, and the lading turned, allowing mixing of the hot and cold portions. In the tests, an external coil tank car and a plate (novel heat exchanger) tank car of equal capacity were used. Temperature probes were installed 6", 24", and 42" above the bottom of each tank car at the center. The boiler pressure was maintained at 76 to 80 PSI and the condensate was monitored for volume and temperature. In the coil tank car, the condensate flow was 3 gallons per minute with temperatures of the condensate reading 70 F. or less for the first 1-1/2 hours, and then rising to a final temperature of 90° F. In the plate tank car, the same procedure was followed as for the coil tank car, but the condensate temperature rose rapidly to 135° F. and held at a steady pace, requiring less than half of the previous time. The temperatures in the coil tank car rose rapidly in the top portions of the lading when com¬ pared with the temperatures at the bottom portion of the lading. This heat layering was noted and monitored after 2 hours of heating, at which time, rolling or mixing action was noted. To determine this rolling action, dye was periodically added to both cars. The plate tank car showed rapid movement of the lading due to the concentration of the heat at the bottom of the car, while the coil tank car showed very slow mixing. The lading in both of the tank cars consisted of water. Another test was run on the plate tank car only. The test was conducted using an animal fat (congealed) . The heat exchanger heated the at rapidly, then, as the rolling action started, the temperature dropped off and paralleled the tempera- ture rise of the lading. It was noted that the valve outlet area temperature rose rapidly. This is important, for the faster the valve temperature rises, liquifying the lading in this area, the quicker the unloading can begin. In another test, a plate tank car was filled with blackstrap molasses which weighs 11.5 pounds per gallon. In 5 minutes, the heat system was raised to a temperature of 80 F. The temperature of the molasses rose evenly throughout and there were no layers of heat in the molasses, as usually happens in present coil tank cars, wherein there is a hot layer of lading at the top and a cold layer of the lading at the bottom. The plate car was then ready to be unloaded in 15 minutes after application of the heat. After the pumping was completed, there was no molasses left in the tank car, and the lading that was removed was tested. None of this lading was burned (caramelized) , which is common in high sugar products in present coil tank cars. Thus, it can be seen that the invention accomplishes at least all of the stated objectives which are more specifically reiterated hereinbelow. Since units of the heat exchanger are sloped. substantially all of the condensate is drained out and the heat exchanger is not subject to any freezing. Since the lading is substantially resting on top of the heat exchanger which applies heat over a large area of the lading, no air pockets or hot spots occur as they do in an external coil prior art tank car. A tank car using the inventive heat ex- changer, as opposed to the prior art external coil tank car, unloads much faster than the coil tank car in winter. No cooking of the lading occurs because the heat exchanger applies uniform heat over a large area of the lading. Approximately 4/5 to 5/6 of the subject tank car is empty before any portion of the heat system (heat exchange units) is exposed to the atmosphere in the tank, as opposed to the prior art internal pipe coils and external coils which are completely exposed when the tank car is 7/8 empty. Therefore, the inventive heat system con¬ tinues to be in contact with the lading and heat the lading, keeping it fluid until the tank car is empty. The pitch of each heat exchanger unit of almost 1:12 (8% grade) assures a complete unload¬ ing and prevents material buildup. All of the heat is at the bottom of the tank car, and as the heat rises, the tank car will unload much faster, saving BTU (British Thermal Units) costs. The side coils on an external coil car do not do much good because the heat goes about 8" into the lading and goes through commodity OM to the top of the tank car. Also, coils at sides of the car are closer to the top of the car and overheats the top of the car. By positioning the heating system off the floor of the tank car, heat sinks caused by the tank cradles, body bolsters, and trucks are non¬ existent or eliminated. External coils on a coil car are positioned or spaced from one another a minimum of 6" between the welded positions which cause a lot of dead spots between the coils and such coils are spaced even farther apart on the bottom of the car in order to miss the stub sills and body webbing, as opposed to the inventive heat system which provides a solid (i.e. , substantially continuous) heating surface at the bottom of the tank car. In view of the flow arrangement in the heat exchanger, there is no need to steam jacket the outlet valve. Because of the slope possessed by each unit of the heat exchanger and the rolling action of lading caused by the heating action and the slope of the heat exchanger, there is no corrosion or product buildup, as opposed to the formation of a boot in an external coil tank car, which boot cuts down on the efficiency of heat transfer on the bottom coils of the tank car and which acts as an undesirable heat insulator. The application of heat at the bottom of the lading creates internal circulation commencing at the bottom, then upwardly through the lading, lading to move downwardly towards the bottom, thereby creating a rolling or mixing action, re¬ sulting in a faster and uniform heating of the lading. Since the present heating system uniformly heats the lading, the temperatures of the heating medium need not be excessive, thereby avoiding damage to plastic linings used within the tank cars, as would occur in a coil tank car. Further, in a modified form of the inven¬ tion, heat exchanger is provided with appropriate ports for the immediate purging of any condensate forming in the heat exchanger. The foregoing avoids a buildup of the condensate which opposes the introduction of the pressurized heating medium. Also, such condensate buildup saps the incoming heat so that it is revaporized. In cold weather, the buildup of condensate forms a liquid plug which has to be bodily moved forward by the incoming heat¬ ing medium, thereby requiring an increase in the pressure of the incoming heating medium. Therefore, it is a principal object of the invention to provide an improved heated tank car. A further object of the invention is to provide a heated tank car having a heat exchanger provided in the interior thereof with the heat exchanger being insulatingly spaced above the bottom of the tank to achieve a more ef icient and uniform heating of the material. A still further object of the invention is to provide a heated tank car which eliminates the heat sink problems normally associated with con- ventional heated tank cars. Still another object of the invention is to provide a heat exchanger for a tank car which is sloped towards the middle of the car so that con¬ densate will drain from the heat exchanger, thereby reducing corrosion of the heat exchanger. Still another object of the invention is to provide a heated tank car which prevents the forma¬ tion of a "boot" at the bottom of the car. A further object of the invention is to provide drainage means in the heat exchanger for purging any heating medium condensate that may form within the heat exchanger. Still another object of the invention is to provide a heated tank car employing an inclined heat exchanger therein to assist the flow of material to the discharge valve of the car. These and other objects will be apparent to those skilled in the art. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a plan longitudinal sectional view of the tank car and heat exchanger therein; FIG. 2 is a partial side longitudinal sectional view of the car and heat exchanger; FIG. 3 is an enlarged sectional view taken on lines 3-3 of Fig. 1; FIG. 4 is an enlarged sectional view taken on lines 4-4 of Fig. 1; FIG. 5 is an enlarged sectional view taken on lines 5-5 of Fig. 4; FIG. 6 is an enlarged sectional view taken on lines 6-6 of Fig. 1; FIG. 7 is a plan longitudinal partial sectional view of a tank car equipped with a modi- fied heat exchanger therein; FIG. 8 is an enlarged sectional view taken on lines 8-8 of Fig. 7; OlvϊH FIG. 9 is an enlarged sectional view of a further embodiment of the heat exchanger; FIG. 10 is an enlarged partial sectional view of a still further embodiment of the heat exchanger; FIG. 11 is another embodiment of the heat exchanger utilizing two heating units, one above and one below; FIG. 12 is an embodiment similar to that shown in Fig. 11 except that the upper heating unit is disposed exteriorly of the tank; FIG. 13 is an embodiment using a pair of heating units for heating a tank car provided with additional dead air spaces; and FIG. 14 is a further embodiment of a heat exchanger wherein a heating unit is secured directly to the inside of the tank car, without using brackets. SUMMARY OF THE INVENTION A heated tank car is disclosed which has a heat exchanger means positioned therein above the bottom of the tank. The heat exchanger means comprises a pair of heat exchanger units which are secured to and supported by the ends and side walls of the tank and which extend downwardly from the ends of the tank towards the center of the tank. Each of the heat exchanger uni-s comprises spaced- apart top and bottom walls or plates which have a plurality of spaced-apart baffle plates secured thereto and extending therebetween to define a plurality of baffles or passageways within the heat exchanger. An inlet valve or pipe is in communication with the inner end of each of the heat exchanger units with the baffle plates being arranged so that heated water or steam is directed back and forth through the heat exchanger for subsequent discharge through the heat exchanger for subsequent discharge through a discharge pipe or valve extending down¬ wardly from the heat exchanger unit through the tank car. The peripheries of the heat exchanger units are supported by and secured to the side walls and end of the tank so that a sealed com¬ partment or dead air space is created below the heat exchanger thereby reducing the heat sink effect of the tank saddles and under frames attached to the tank. To further accelerate the heating of the lading, additional heating units may be disposed adjacent the top of the tank so that the lading is sandwiched between opposed heating units. The heat exchanger means may be provided with drainage parts communicating between the passageways and the discharge pipe for purging heating medium condensate that may form during the heating of the tank car. DESCRIPTION OF THE PREFERRED EMBODIMENT The numeral 10 refers to a conventional railway tank car comprising a wheeled support means 12 of conventional design. Storage container or tank 14 is mounted on the frame means 12 by conven¬ tional means such as by tank saddles 16. Tank 14 generally has a cylindrical configuration although the bottom 18 of the tank 14 slopes inwardly from the ends of tank heads 20 and 22 towards a discharge valve assembly 26. It is to this conventional tank car structure that the heat exchanger of this invention 01181 is mounted and which will be referred to generally by the reference numeral 28. Heat exchanger 28 comprises heat exchanger units 30 and 30' which are identical except for being mirror images of each other. Inasmuch as units 30 and 30' are identical, only unit 30 will be described in detail with " * " being indicated on unit 30' to indicate identical structure. Heat exchanger unit 30 comprises arcuate top and bottom plates 32 and 34 having a plurality of baffle plates 36 secured thereto and extending therebetween as best illustrated in Fig. 1 to create a plurality of passageways 38 therebetween. The peripheries of plates 32 and 34 are secured together and sealed by means of a wall member 40 extending therearound and define therewith a heat exchanger medium containing chamber 43. As seen in Fig. 1, the inner end of wall 40 is curved at 41 so as to conform to the configuration of the upper end of the discharge valve 26. The numeral 42 refers to an inlet extending upwardly through the bottom of the tank 14 and in communication with the interior of the heat exchanger as best seen in Figs. 2 and 3. Outlet 44 also extends upwardly through the bottom of the tank 14 and is in communication with the interior of the heat exchanger as illustrated in Fig. 2. • More specifically, the heat exchanger unit 30 is defined as follows. The heat exchanger outer wall 40 has a curved outer end portion 40a, a flat inner end portion 40b with a curved tank outlet surrounding portion 40c, and longitudinally extending flat side portions 40e and 40f that diverge inwardly toward one another. The baffle plates or means 36 includes U-shaped outer baffle plate member 33 surrounded by wall 40 and having outer longitudinally extend¬ ing legs 33a, 33 b that diverge outwardly from one another', the outer ends 33c of legs 33a, 33b being speced away from curved end portion 40a; and laterally extending inner end portion 33d that has a central curved portion 33e going around part of the tank drain 26 and having U-shaped outwardly directed bight portion 33f surrounding the inlet 42. The baffle means further includes longi¬ tudinally elongated fins or plates 35, 35 adjacent wall portion 40b and connecting with the curved portion 40a and extending short off the inner end portion 33d; a hairpin shaped longitudinally extending central baffle plate 37 having outwardly diverging leg portions 37a, 37a ending short of the outer curved portion 40a and inner curved end portion 37b curved around part of heat exchanger outlet 44; and a shortened central plate 39 that extends in slightly between leg portions 37a, 37a. The heat exchanger 32 has the same baffle construction and need not be described further. The numerals 46 and 48 refer to tubing provided at the upper surface of the bottom plate 34 to assist in draining the condensate in the heat exchanger unit toward the outlet or discharge 44. The baffles 36 are provided with openings 49 at the tubes 46 and 48 to enable the condensate in the passageways to flow through the baffle plates so that the condensate is discharged closely adjacent the outlet 44. Bars 50 and 52 are welded to the interior $Q ~ £A ~ 01..PI surface of the sides of the tank as seen in Fig. 3. Bars or brackets 54 and 56 are secured to the sides of the heat exchanger unit 30 and are welded to the bars 50 and 52 respectively. Bar or bracket 54 or 58 is also secured to the outer ends of the heat exchanger unit 30 and is welded to the bar 50 or 52 on the interior surface of the tank head end 20 or 22. The conventional tank car 10 may be converted to the heated tank car of this invention by first removing a portion of all of the ends or heads 20 and 22. Preferably, the bars 50 and 52 would then be welded to the interior surfaces of the side walls of the tank. The heat exchanger units 30 and 30' are then inserted into the interior of the tank so that the brackets 54 and 56 rest upon the bars 50 and 52 respectively and so that the inner end of the units are positioned adjacent the discharge valve 26. The tank m bottom 18 would have been pre- viously cut away to provide the inlets and outlets of the heat exchanger to extend downwardly through the bottom 18 of the car. The heads 20 and 22 are then replaced in conventional fashion with brackets 54 and 56 then being welded in a continuous fashion to the interior surfaces of tank heads. The new brackets 54 and 56 are also welded to the bars 50 and 52. Preferably, the inner ends of the heat exchanger units would also be welded together so that a sealed compartment or dead air space 60 is created below the heat exchanger and the bottom 18. In use, assuming that the car contained a liquid commodity, steam or hot water would be connected to the inlets 42 and 42'. The incoming steam passes around the discharge valve 26 and then O PI travels in the paths defined by the arrows in Fig. 1 for subsequent discharge through the outlets 44 and 44*. Heating of the material (lading) by the heat exchanger would initially cause the material in contact with the heat exchanger to flow towards the discharge valve 26 assisted by the weight of the material on top. This method of heating the lading eliminates part of the material being overheated awaiting for the material on top. This method of heating the lading eliminates part of the material- being overheated awaiting for the material.to start flowing downwardly through the discharge valve. The provision of the space 60 between the heat exchanger and the bottom of the tank prevents the undercarriage and saddles of the car from acting as heat sinks so that a much more efficient heating of the lading is obtained. The fact that the heat exchanger slopes towards the discharge valve assists the flow of material to the discharge valve 26. Thus, it can be seen that a novel heated tank car has- been provided which provides a more efficient heating of the lading and which eliminates the forma¬ tion of a "boot" of material at the bottom of the car. It can also be seen that the sloping of the heat exchanger unit and the elements 46 and 48 aid in the prevention of condensate accumulating in the heat exchanger, thereby eliminating the serious problem of corrosion normally associated with prior art devices. A further feature of the invention lies in the elimination of the heating medium condensate which forms inside the heat exchanger during the process of heating the lading in the tank car. The foregoing feature is illustrated with the following OMPI embodiment of the heat exchanger illustrated in Figs. 7 and 8. Within a tank 114, there is mounted a heat exchanger means 128 comprising a pair of heat exchange units 130, 130. Since both units are identical in construction, only the left portion of the tank 114 is shown supporting one of the heat exchange units 130, 130. Since the heat exchanger 128 is supported by the same means as the heat exchanger unit 28 described in reference to Figs. 1-6, there is no necessity for describing the support structure. The heat exchanger unit 130 comprises arcuate top and bottom plates 132 and 134 supporting there¬ between a plurality of channels 135 and 137 as defined by baffle means in the form of a corrugated member 139 interposed between the top and bottom arcuate plates 132 and 134. It will be noted, as viewed in Fig. 8, that the channels do not possess equal cross-sectional areas. For example, the channel 135 is smaller than the channel 137 , the smaller channels 135 functioning to direct a heating medium (steam) upwardly from an inlet 142 toward a tank head 120 and the larger channel 137 directing the heating medium (steam) downwardly toward inlet 142. Referring particularly to Fig. 7, the heating medium such as steam entering the heat exchanger means 128 through the inlet 142 progresses upwardly through the narrow channel 135 until it reaches heater exchanger curved end portion 140a, at which time, the steam subdivides into two portions which flow along a pair of wide channels 137, 137 until the steam portions reach a minor manifold 141 which directs the steam into narrow channels i35a, 135a. The steam upon reaching the curved end portion 140a is redirected thereby into wide channels 137 , 137a, the steam continuing on its way until it meets an inner wall 143. Thereafter, the steam, after it leaves the channels 135b, ' impinges on the curved end portion 140a which redirects the steam along the wide channels 137b, the steam finally completing its passage in a main manifold 145 communicating with the atmosphere through an outlet 144. In the alternative, the exiting steam may re-enter a reheating chamber in the steam apparatus (not shown) generating the steam. As was previously described in reference to the first embodiment shown in Figs. 1-6, application of heat at the bottom of the lading will develop a rolling or a circulating flow in the lading as heat continues to be imparted to the lading. That is, the heated portion of the lading, as it rises through the lading causes the unheated portions of the lading to descend to the bottom to effectively cause mixing or rolling of the lading. Such thorough and uniform heating of the lading prepares the lading for faster unloading and prevents the lading being subjected to excessive heat which burns or carmelizes the lading. Similar circulation of lading occurs in the embodi- ment shown in Figs. 7 and 8. To increase the heating and the flow movements of the lading, the heat exchanger means 128 is provided with feeder lines 147, 149 and 151. The flaring out of the passages lines as they proceed out to ends of the tank also enhances flow movements of the steam and condensate and increases faster heating of the lading. These feeder lines communicate between the narrow channel 135 and the wide channels 137b, thereby permitting a portion of the steam entering 0____-ι the channel 135 to be directed outwardly into the outermost channels 137b to provide steam quickly for quick heating of the extremities of the heat exchanger with steam to assist in purging the heat exchanger with steam and more quickly warm up the lading. To further increase the heating and the flow movements of the lading, the heat exchanger means 128 may be provided with additional feeder lines 147a and 147b, as shown particularly in Fig. 7. Referring still to Fig. 7, any condensate that forms in channels 137a and 135b will flow down¬ wardly toward the inner wall 143 and pass through an internal drainage port 153 into the minor manifold 141 to join with additional condensate which is formed in channels 137 and 135a, which additional condensate also flows towards the inner wall 143, and then finally exits- through an external drainage port 155 which communicates with the outlet 144. As is apparent, the drainage means provide removal of the condensate during application of the steam and adequate gravity drainage of the exchanger means after the tank car has been emptied. Any condensate formed in central channel 135 flows downward below the steam moving upstream and out drainage port 142 and through port 155 to outlet 144. The corrugated member 139, as shown in Fig. 8, is secured to the top arcuate plate 132 and the bottom arcuate plate 134 by appropriate means, such as welding. This ensures that there is no transverse heating medium flow between adjoining channels 135 and 137. The feeder lines 147, 149, 151, 147a and 147b may be arranged to pass through the walls form¬ ing the various channels. However, in the preferred arrangement, the various feeder lines do not pass through the walls of the channels, but are disposed exteriorly of the channels. Referring to Fig. 8, the feeder lines, for example, feeder lines 147a, are secured exteriorly of the heat exchanger means 128 by being secured underneath the bottom arcuate plate 134. The particular feeder lines 147a extend between and communicate with the channels 135 and 135b. From the arrangement shown in Figs. 7 and 8, it is seen that the steam coming into the inlet and going up the central passage and then along the side passages, the heat exchanger permits any condensate water that is formed to roll down well below the steam and by this technique the steam can quickly get to the steam exiting at the bottom of the tank without having to push any water or condensate out through the passageways and therefore permit a fast purging of the heat exchanging system. Although the embodiment disclosed in Fig. 8 uses a corrugated member 139 to define a plurality of different size channels, it is apparent that other means may be employed for creating the channels. For example, as shown in Fig. 9, a heat exchanger means 228 comprises baffle means having a plurality of spaced narrow channels 235 which are defined by a series of longitudinal half-oval members 235a secured to a top arcuate plate 232 and a bottom arcuate plate 234 and a plurality of wide channels 237 defined by the spaces between adjoining half-oval members 235a. Since the half-oval members 235a do not provide sufficient rigidity to the heat exchanger 228, a pair of longitudinal bars 259 are secured between the top and bottom arcuate plates 232 and 234, respectively. The longitudinal bars 259, in con¬ junction with adjacent half-oval members 235a, define a pair of channels 235b adjacent each of said longitudinal bars 159. The arrangement of the spacing of the narrow channels 235 conducting the steam in an upward direction, and the wide channels 237 directing the steam on its return path in a downwardly direction is the same as was described in reference to the embodiment shown in Figs. 7 and 8. For example, as shown in Fig. 9, the narrow channels 235 formed by the half-oval members 235a, are separated by the wide channels 237 established between the top arcuate plate 232 and the bottom arcuate arcuate plate 234 and the adjoining half- oval members 235a, or by the wide channels 235b established between the top arcuate plate 232 and the bottom arcuate plate 234 and the longitudinal bars 159. From the foregoing example, it is obvious that other means may be employed for defining the channels between the top and bottom arcuate plates 232 and 234, respectively. The remaining structural details of the embodiment shown in Fig. 9 are the same as those in connection with the embodiment described in Figs. 7 and 8. In other words, the arrangement of the inlet, outlet and drainage ports would be the same. Fig. 10 shows a modified structure of a heat exchanger means 328 having a plurality of channels or passageways 338 defined by longitudinal arcuate members 335 adjoining each other and secured toan arcuate plate 332. Fig. 11 shows another modified structure of a heat exchanger means wherein heat exchanger means 428 comprises a pair of heat exchanger units 430a OTv'.PI and 430b, oppositely disposed with respect to each other to apply heat to the lading between said heat exchanger units. As described in reference to the preceding embodiments, the heat exchanger units are insulated from the wall of the tank 414 by means of dead air spaces 460a and 460b. Some of the channels are interconnected by feeder lines 447, as previously described in reference to the embodiment shown in Fig. 7. Fig. 12 shows a still further modification of a heat exchanger means 528 having a pair of heat exchanger units 530a and 530b adapted to impart heat to a lading inside the tank 514. The heat exchanger unit 530a is similar to the heat exchanger units previously described. The heat exchanger unit 530b comprises a series of tubes arranged in serpentine fashion on top of the tank 514. The arrangement of the two heat exchanger units 530a and 530b imparts heat to the lading disposed between these heat exchanger units. Some of the channels in the heat exchanger units 530a, 530b are interconnected by feeder lines 557. The heat exchanger unit 530b can be permanently mounted on top of the tank 514 for heating lading, such as sulfur, requiring a large input of heat for liquification purposes. Alterna¬ tively, the heat exchanger unit 530b may be a portable unit which can be placed atop the tank 514, as the occasion demands. The embodiment illustrated in Fig. 13 is secured within a tank 614 which has been provided with additional dead air spaces 660c as defined by upstanding walls 661. These additional dead air spaces 660c cooperate with dead air spaces 660a, 660b to increase heat transfer from heating units 630a, 630b to the lading in the tank 614. As in the preceding embodiments, feeder lines such as feeder lines 647 interconnect some of the channels in the heating units. Fig. 13 shows another way of securing a heat exchanger unit 730a to a tank 714. Instead of using intermediate members for securing the heat exchanger unit to the tank, the intermediate members comprising brackets 54, 56 and bars 50, 52, as shown in Fig. 3, these intermediate members can be eliminated by securing the heat exchanger units 730a directly to the tank 714 by appropriate means such as a con¬ tinuous welding bead 430c which secures the outer periphery of the heating unit to the tank 714. OMPI _

Claims: C L A I M S 1. A heated tank system comprising: a horizontally disposed lading container having opposite ends, and top and bottom portions, a heat exchanger means mounted within said container spaced above the bottom portion of said contain and having an interior compartment for receiving a heated medium therein for heating the lading in said container above said heat exchanger means, said heat exchanger means having at least one inlet and at least one outlet in fluid communication ther with, said lading container having at least an inlet and an outlet. 2. The heated tank system according to claim 1, wherein the compartment of said heat exchanger means comprises spaced-apart top and bottom plates or ovals defining a chamber for receiving and circulating said heated medium. 3. The heated tank system according to claim 1 or 2, wherein a plurality of spaced-apart baffle plates are secured with ' said top and bottom plates and extend therebetween to define fluid passageways therebetween. 4. The heated tank system according to any of the claims 1-3, wherein said heat exchanger means has a longitudinal sectional V-shaped configuration. 5. The heated tank system according to any of the claims 1-4, wherein said heat exchanger means has a transverse sectional semi-circular configuration. 6. The heated tank system according to any of claims 1-5, wherein said container has opposite side walls extending between its ends, and wherein heat exchanger mea is supported on and secured to said side walls and said ends of said container whereby the fluid lading c rried by said container is maintained above said heat exchanger means. 24 7. The heated tank system according to claim 1, wherein said heat exchanger means comprises first and second heat exchanger units positioned in said container in an end-to-end relationship. 8. The heated tank system according to claim 7, wherein the outlet of said container is positioned between the adjacent ends of said first and second heat exchanger units. 9. The heated tank system according to Claim 7 or 8, wherein the inlet and outlet of each of said heat exchanger units are positioned at the inner ends thereof outwardly of the container outlet. 10. The heated tank system according to any of the claims 7-9, wherein the heated medium leaving each of said units passes closely adjacent the outlet of said container prior to exiting from said unit outlet. 11. The heated tank system according to any of claims 1-10, wherein said system includes a wheeled suppor means for transporting the container. 12. The heated tank system according to any of the claims 1-11, wherein the heated medium leaving said heat exchanger means passes closely adjacent the outlet of said container prior to exiting from said unit outlet. 13. The heated tank system according to any of the claims 1-12, wherein said heat exchanger means include support means attached to the lower portion of the contain for supporting said heat exchanger means above the bottom of the container to define a dead air space between said heat exchanger means and said bottom of said container; whereby said dead air space acts as a heat insulating mean to prevent transmission of heat from the heat exchanger means to an undercarriage of said container. 14. The heated tank system according to any of the claims 1-13, wherein the plurality of spaced-apart baffle plates are interconnected by drainage tubing slanti toward the outlet of said heat exchanger means; whereby said drainage tubing facilitates the draining of con¬ densate into the plurality of passages defined between said baffle plates. 15. The invention according to any of the clai 1-14, wherein said lading container is provided with heat exchanger mounting means adapted to releasably receive said heat exchanger means and extending about the periphe of said heat exchanger means and is provided with the hea exchanger means a sealed thermal insulating space between the heat exchanger means and the bottom of the tank. 16. The heated tank system according to claim 13, wherein said support means comprises a bar element secured to the lower portion of said container, and said heat exchanger means includes a peripheral bracket means adapted to sit upon said bar element, whereby the securem of said bracket means to said bar element, such as by wel ing, defines a dead air space between said heat exchanger means and said bottom of said container. 17. The heated tank system according to claim 15, wherein said heat exchanger positioning means compris a continuous weld bead securing the periphery of said hea exchanger means to said container. 18. A heated tank system according to any of t claims 1-17, including an additional heat exchanger means, and further means for positioning said additional heat exchanger means inside said lading container in the upper portion thereof, and defining a dead air space between th top of said container and said additional heat exchanger means. 19. The heated tank system according to any of the claims 1-18, including an additional heat exchanger means, and means for positioning said additional heat ex¬ changer means on top of said lading container. 20. The method of converting a tank into a heated tank to facilitate dispensing a congeliable stored medium, comprising the steps of: removing at least a portion of said tank to expose the interior of said tank, inserting a heat exchanger into said tank, positioning said heat exchanger in said tank car so that said heat exchanger extends continuously on inside walls of said tank above the bottom of said tank, providing an inlet and an outlet in said heat exchanger, securing peripheral edges of the heat exchanger to the interior walls of said tank whereby said heat ex¬ changer creates a compartment portion-therebelow which is above said heat exchanger, and replacing said removed portion of the tank. 21. The invention according to claim 20, wherei an inlet and an outlet are provided in the tank for the inlet and the outlet in said heat exchanger to permit a heated medium to be passed through said heat exchanger to heat the lading in said tank. 22. The invention according to claim 20 or 21, wherein the compartment portion is sealed from the interio of the tank. 23. For use in a fluid lading carrying tank structure, a heat exchanger for heating a congeliable lading in a storage tank, said heat exchanger comprising a structure havin a plurality of longitudinally extending flow passages adapted to receive and conduct a heated medium, said structure being configured along longitudin and transverse axes to develop gravity drainage, said heat exchanger having an inlet and an outle at a low point for gravity drainage.

Inventors: LOEVINGER RICHARD P, LOEVINGER, RICHARD, P.
Applicants: LOEVINGER RICHARD P, LOEVINGER, RICHARD, P.
Application year: 1983
Main classification: B61D27
IPC codes: B61D5, B65D88