US2624552A - Heat exchanger - Google Patents

Description

E. A. ROSE HEAT EXCHANGER Jan. 6, 1953 3 Sheets-Sheet 1 Filed April 27 1950 r i wwmm m 1F INVENTOR.

fi'jmsii flase BY W Mam M ATWE/YIKS Jan. 6, 1953 E. A. ROSE 2,624,552

' HEAT EXCHANGER Filed April 27. 1950 5 Sheets-Sheet 2 I N VEN TOR.

fiwsiji 080 E. A. ROSE HEAT EXCHANGER Jan. 6, 1953 5 Sheets-Sheet 3 Filed April 27 1950 @Ifi ' INVENTOR. fizms'ii 050 Patented Jan. 6, 1953 HEAT EXCHANGER Orleans, La., assignor to E. A. Rose, Inc., New Orleans, La., a corporation Ernest A. Rose, New

of Louisiana Application April 27, 1950, Serial No. 158,484

9 Claims.

The present invention relates in general to heat exchange apparatus, and more particularly to rapid heat transfer sugar crystallizers of the type employed in the manufacture of sugar and like materials.

Many varieties of apparatus have been devised to promote crystallization in massecuite and similar sugar crystallization solutions. In general, apparatus of this type depends upon rotary movement of heat conductive bodies or radial conduits through a mass of solution under-treatment with the exchange medium, usually a suitable fluid circulated through the conductive bodies or radial circuits, to simultaneously effect slight agitation and cooling of the solution to promote crystallization. In many instances, prior art machines have been subject to objection in that they employ a relatively large surface area for the heat conductive bodies in comparison to the total space in which the treatment is performed, which tends to precipitate rotation of the mass of solution under treatment. This is objectionable, as anything other than a very gentle agitation will have the effect of either breaking up or grinding crystals already formed by gradual reduction of the temperature of the solution. It should be remembered that the optimum goal to be achieved in sugar crystallizers is the rapid production of large crystals from the massecuite or mother liquor. Realization of this condition requires some means of insuring that crystals are produced by gradual growth rather than abrupt formation of batches of minute crystals. The larger the crystals which are obtained, the easier and more eflicient is the subsequent separation and consequently the better yield of sugar.

Attempts have been made to overcome, the, defects incident to large-.surfacerarea heat conductive conduits, arising from the high degree of agitation occurring on rotation of the conduits, by providing a series of spaced, relatively small cooling fluid conduits projecting from a central driven shaft, through which the cooling, fluid is circulated on rotation of the conduits to effect the desired heat exchan e action. These, however, have been found objectionable, has the immersion of these small conduits, with comparatively limited surface area, effects localized sudden chilling in the mother liquoror massecuite and promotes rapid formation of minute new crystals rather than gradual rowth of larger crystals from crystal nuclei. Continuous forced-circulation heat exchangers have likewise been employed as rapid sugar crystallizers, but the multitude of small diameter conduits and orifices and the network of valves required in such continuous forced-circulation systems, are in many instances conducive to becoming obstructed or otherwise inoperative, rendering parts of the heat exchanger inoperative, and destroying uniformity of the heat exchange action throughout the, solution.

An object of the presentv invention, therefore, is the provisionof .a novel heat. exchanger of simple design and durable construction, which is free of the above enumerated objections.

Another object of the present invention isthe provision of a novel heat exchange apparatus in which a mass to be treated may ,becooled or heated in a uniform manner throughout the mass.

Another object ofthe present invention is, the provision of a novel. heat exchange, apparatus of the rapid sugar crystallizer type, in which a mass is brought intoheat exchange relation with a cooling or heating fluid uniformly throughout the bulk of themass.

Another object of the present, invention is the provision ofa novel heat exchange apparatus for circulating a fluid in heatexchange relation, With a solution, wherein both the heat exchange fluid and the solution are gently agitated.

Another object of the. present invention is the provision of a novelheat exchange apparatus for circulating treating fluid in heat exchange relation with a solution, wherein circulation of the treating fluid is efiectedby gravitational forces.

Another object of the present invention is the provision of a novel heat exchange apparatus for circulating a treating fluid in heat xchange relation with a mass through fluid conducting elements, wherein acomplete change of the treating fluid in the fluid conducting elements is efiected for each cycle of operation.

Another object of the presentinvention is the provision ofa novel heat exchange apparatus for circulating a treating fluid in heat, exchange, relation with a solution, which is readily and conveniently adapted for complete exhaustion of fluid from the apparatus for cleaning the same.

Other objects, advantages and capabilities of the present invention will become apparent from the following detailed description taken in conjunction with the accompanying drawings,

wherein onlya preferred. embodiment is shown.

In the drawings:

Figure 1 is a vertical longitudinal sectionview of. a rapid sugar crystallizer embodying the present invention, showing .the agitator vanes in elevation:

Figure 2 is an orthagonal development of the central rotary fluid drum illustrating the relative disposition of the heat exchange fluid openings in' the periphery thereof Figure 3 is a vertical transverse sectional view of the instant sugar crystallizenitaken along the lines 3-} of Figure 1;

Figure 4 is a hor zontal, longitudinal section of oneof the agitating vanes, taken along the lines 4-4 of Figure 3;

Figure 5 is a vertical transverse section View of one pair of agitating vanes, illustrating the heat exchange fluid flow paths therein, taken along the lines 55 of Figure 1;

Figure 6 is an elevational view of the fluid supply distributing pipe disposed coaxially within the central drum in the instant crystallizer;

Figure 7 is a vertical transverse elevation of the fluid distributing pipe, taken along the lines l'-'l of Figure 6; and

Figures 8 to 11 inclusive, are side eleva'tional views of one pair of agitating vanes with parts of the side walls of the vanes broken away, illustrating the fluid content and fluid flow paths through the vanes at various positions of rotation, taken, for example, along the lines 8-4) of Figure 1.

Referring to the drawings, wherein like reference characters designate corresponding parts throughout the several figures, the instant sugar crystallizer comprises an upwardly opening tank or receptacle having opposed end walls 22, 22' and a side wall 24. The lower half of the tank 20 is preferably formed to define a half cylindrical surface similating a half drum, indicated at 24', while the upper portions of the side wall preferably extend substantially vertically. Suitable openings, generally indicated at 26, are disposed centrally in the end walls 22, 22', through which a hollow cylindrical drum 28 is extended. The drum 28 is intercoupled with the side walls 22, 22' of the tank 20 fo rotation by means of a bearing or journal bracket 30 fixed to the end walls 22, 22 of the tank and snugly fitting the surface of the drum 28. To prevent axial movement of the rotatably journalled drum 23, thrust collars 32 are keyed or otherwise fixed to the drum 28 immediately inwardly of the inner end of the bearing bracket 30, and suitable thrust washers 34 are disposed between the thrust collars 32 and walls of complementary recesses in the bearing brackets 38 at each end of the drum 28. Suitable packing glands 35 are likewise provided surrounding the drum 23 and positioned adjacent the outwardly disposed end of each bearing bracket 30 to provide a closure for packing recesses 38' formed in the outer surface of each bearing bracket 30.

External drive means are provided for the drum 28, comprising a worm wheel or gea 38 keyed or otherwise secured to one end of the drum 28 outwardly of the tank 20, intercoupled in driving engagement with a worm 40 driven from a suitable motor or other convenient prime mover (not shown).

Means are provided to supply water or other heat exchange fluid substantially uniformly throughout the elongated portion of the drum 28, comprising a centrally disposed, elongated fluid supply pipe 42 positioned concentric with the axis of the drum 28 for a substantial portion of the length thereof, and extending through a circular opening 42' of slightly greater diameter than the diameter of the pipe 42 in one end of the drum 28. The fluid supply pipe 42 terminates at one end in a flexible coupling 64 for rotation with the central drum 28, and is rigidly intercoupled with and positioned by flat spacer bars or rods 43 extending to the inner surface of the drum 28. discharge outlets 46, and an open inner end 48, as illustrated in Figures 6 and 7, for supplying the heat exchange fluid to the interior of the central drum 28 substantially uniformly along the entire length thereof. The main fluid supply line The pipe 42 is provided with spaced fluid 4 5!) is intercoupled between flexible coupling 44 and hot and cold water branch supply conduits 52 and 54 controlled by suitable valves to stop cocks 52', 54, respectively, disposed in the branch conduits, to permit manual control of the heat exchange fluid supply to the drum 28.

The fluid is brought into heat exchange relationship with a solution such as niassecuite in the tank 20 by mean-s of a series of agitating vanes, indicated at 60, formed of one quadrant hollow sectors disposed in diametrically opposed pairs in relatively ofiset relation along helical paths on the drum 28. These agitating vanes, more clearly illustrated in Figures 3 to 5 and 8 to 11, comprise a one quadrant hollow sector having spaced sides 62 and 52 suitably formed. of sheet metal or like material cut in the form of one quarter of a circle. The sides 62 and 02 are secured together along their radial edges forming leading edges 64 and trailing edges 66, and are secured to an arcuate strip 68 along their outer curved edge, to form a closed liquid receptacle. The inner portion of the sides 62, 62 are shaped, near the projected intersection of the radial edges 64 and 66, to define an arcuate recess adapted to snugly accommodate a portion of the surface of the drum 28 and be rigidly secured thereto.

An intermediate divider partition it is provided between the sides 62, 62' near and parallel to the leading edge 64 and extends, with the portion of the sides 62 and 62' lying between the partition 18 and the leading edge 64, for a short distance through complementary openings ?2 formed in the surface of the drum 28, forming in effect a substantially elliptical section of pipe extending into the interior of the drum 28 for a short distance beyond the inner periphery thereof, as indicated at 74. The divider partition 18 extends outwardly parallel with the leading edge 64 to a point near the arcuate strip 68 at the curved end of the sector 60, but spaced therefrom to provide an opening 16. The partition 7:! thereby defines a radial primary channel 78 along the leading edge of the sector and extending into the drum 28, and a heat exchange fluid reservoir 83 throughout the remaining portion of the sector E0.

The vanes '68 are disposed in oppositely radiating pairs along the length of the drum 28 lying within the tank 28, and are arranged on helical paths beginning at the outer portions of the drum 28 adjacent the thrust collars 32 and converging to an apex at the longitudinal center of the drum 28, as clearly indicated in Figure 2 by the orthogonal development of the surface of the drum 28, showing the relative disposition of the openings 12 for receiving the inner extensions 14 of the sector members forming the primary channel 18. This spiral or helical disposition of the vanes along the length of the drum 2!; reduces shock and wearing forces exerted on the agitating vanes '60 by their striking the massecuite solution in the tank on rotation of the vanes when the tank is not completely filled. It will be apparent from an inspection of Figures 1 and 2 that the agitating vanes 60 are spaced on the drum 28 in relatively staggered pairs and are inclined slightly relative to the medial longitudinal axis of the drum 28 so that the paths swept out by the vanes overlap and extend substantially continuously over the entire internal volume of the tank 20.

Means are provided at the end of the drum 28 through which the fluid supply pipe 42 extends,

to c'ollect and dispose of fluid overflowin from within the drum 28 through theaperture" 42'. This means comprises a; splash box '8 substantially surrounding the end or the drum '28 and provided with a.- discharge "conduit- 84" extending from the lower end thereofto carry'oif overflow liquid to a sewer, or to aspray pond forrecirculation, as desired. To lead the overflow liquid to the splash box 84, a suitable annular drip ring 86 extends around the surface of the drum 28 adjacent but spaced slightly'f-rom theend of the drum 28 to prevent liquid adhering to theundersurface of the drum and passing beyond the" edge of splash box 84. In additionra drain plug 88 is provided at the owei sur ace of the drum 28 within the area enclosedbytheisplash boi't'Mto efiect complete drainage of fluid 'f-rom the drum, as will be later described.

Operation of the instant rapid crystallizer will be more fully understood by specific reference to Figures 1 and 8 to 11. Water of desired temperature is admitted through-the conduit 50 to the discharge pipe 42 by'adjus'ting appropriate valves 52', 54 in the branch conduits' 52 and 54. The water flows through the central supplylpi pe 4'2 and spaced discharge outlets substantially uniformly throughout the length of the hollow drum 28. On continuous admission of water to the drum 28, the water level rises in the drum until it reaches the lower edge of the opening 42' through which the pipe 42 extends, after which the liquid level is maintained at this point by overflow of liquid through the opening' tz' into the splash boii 84. I

The instant device is operative to'effect a complete change of cooling liquid in the agitating vanes '50 for each cycle of rotation or the vanes in the following manner. Beginning'the description of the operatingcycle-of adi-ametrically opposed pair of vanes '50 and 60 with the primary channels 18 extending horizontally and to the left and right of drum 28, as viewed in Figure 8, the leading edge 64 of the Vans 60 is, at this point, disposed below the level-of the fluid in the hollow core 28 so that fluid'flows into thepr'i'mary channel 18 of the vane'fill. on progressive counterclockwise rotation of the vane 60 :from the vane '60 during this rotation through the third position illustrated in'Figure 8 to a position'of rotation with the axis of theprim'a-ry channel 18 disposed directly downwardly from the drum 28, increasing quantities of water from the hollow drum 28 are drawn, under influence of gravity, through the primary channel 18, opening 16, and into the reservoir '80 in the vane 60, the fluid capacity of the primary channel 18 and opening 76 being sufficient to maintain the'fluid level in the reservoir 80 in the vane 60 commensurate with the fluid level in the drum '28. Fluid flow in the vane 60 and liquid level-therein during this quadrant of rotation of the v'a'neBlI are. illustrated in Figure 9 of the accompanying-drawings.

During further rotation 'of'the vane 60 from a position with 'the axis of the primary channel 18 extending vertically downward-to aposition extending horizontally to the right of drum 28, as indicated by the vane '60 in Figure 8,-the primary channel 18 and reservoir 80 ofthe vane -'60 are maintained filled with the cool water as both of these chambers are below theliquid level established in the drum 28.

When the primarychannel 18 of the vane 60 passes through the horizontal axis, however, and thus progresses above theliquid levelestablished i8 is progressively discharged under the influence in the drum 28, the liquid in-the-primary channel:

quadrant'of its cycle, as the upper'end or the divider partition Win the vane 60" is sufficiently near the a'rcuate strip-68 to .prevent more than a very minute amount of liquid from spilling. through the opening 16 into the primer-Tenannel 18.

On fourth quadrant rotation of the vane 60 from a'po'sition with its primary channel18 and lead edge 64 disposed vertically to the initial position with the primary channel 18 disposed horizontally extending to the left as viewed in Figure '8, liquid in the reservoir '80, under the influence of gravity, collects along the divider partition 10' and spills through the opening 16 and primary channel .18 back into the hollow drum 23. Thus, during 'theiourth' quadrant rotation only is the-liquid which has been collected in the reservoir Bilof the' vane 60 exhausted from the vane and discharged :back :into the-hollow drum 2-8. The oppositevanetfl follows precisely the same cycles of fllling and discharging as-the vane 60, but lags 180 out'ofphase'with' the cyclic filling and discharging of the vanetfl.

It willbeseen,'therefore. that during each :cycle of rotating of the hollow drum 28, the vanes-6'0 and 60' are completely filled during one quadrant or of rotation, and continue in rotation for with-thereservoiriill of the vanes filled-with the cooling liquid. During the remaining 90 of rotation, the-liquid is completelydischa'rged from the vanes 60, 60 'and'the vanesreadicdiorxrefilling during theneiit'succeeding QO" of rotation.

It will be apparent, therefore, that this arrangement of agitating vanes will effect "very gentle agitation of the massecuite'solutionin the tank 20, and producegradual cooling of the solution by bringing a large surf-aceareaof cool-ing fluid in heat exchange relation with the solution throughout a substantial portion of one cycle of operation of any givenagitating' vane 60. -By distributing the cooling fluidnthr'oughout vanes of relatively large surface area, extending along the plane in which the vane-rotates, verylittle agitation is efiected in the solution, while the heat transfer to the solution ismaintainedsufflciently gradual to promote growth ot-crystals, rather than'shock ing a largebatch'oi minute crystals into existence. Likewisepthe complete charging and discharging of "the cooling fluid from each vane in one cycleof operation markedly increases the efficiency and spe'ed-of heat transfer in the device, as well asmaintaining'the heat transfer substantially uniform throughout the length of the tank- 20. Uniformity is-likewise improved by discharging the cooling-fluid from the supply pipe 42 tothe hollow drum 28 through the series of spaced liquid discharge outletsflfiextending along the pipe 42 substantially throughout'the lengthof the'hol-low drum 28. "Afterthe desired"temp'eratuiein the crystallizer has been attained, the mother liquor is still found to be supersaturated with sugar, in the usual case. Useful advantage of this fact can be made by passing steam or hot water from the branch conduit 52 through the hollow tube 28 and vanes 60 and 60' and thus heating the solution so as to make the separation of the mother liquor from the sugar crystals easier in the centrifugal separators. No sugar is dissolved during this heating as the mother liquor is still supersaturated.

At the end of the grinding season, it is the usual practice to drain all the fluid contained in the crystallizer, particularly if the crystallizer is located in a climate where hard freezes likely to fracture the vanes 60 may be expected. In order to facilitate this complete drainage of the crystallizer, the inner ends of the sector members defining the primary channels '18 are projected through the openings 12 in the hollow drum 28 and for a finite distance into the drum 28 beyond its inner surface, as indicated at M. The drain plug 88 is then removed from the hollow drum 28 and the liquid in the drum 28 allowed to drain into the splash box 84. By rotating the drum 28 and vanes 60 and 69' in a clockwise direction, as viewed in Figure 5, the liquid still trapped in the reservoirs 80 and primary channels 18 of the vanes is more quickly exhausted from the reservoirs into the primary channels and discharged into the hollow drum 2B. As the inner ends of the primary channels 18 project a finite distance into the core of the hollow drum 28, only minute quantities of liquid discharged from the primary channels 18 of the upwardly disposed vanes is permitted to run back into the inwardly projecting openings 14 of the primary channels in the downwardly disposed vanes, thus providing for relatively rapid exhaustion of all the liquid in the vanes from the crystallizer.

While but one particular embodiment of the invention has been shown and described, it is distinctly understood that the invention is not limited thereto, but that various modifications may be made in the invention without departing from the spirit and scope thereof, and it is desired, therefore, that only such limitations shall be placed thereon as are imposed by the prior art and as set forth in the appended claims.

What is claimed is:

1. Heat exchange apparatus comprising, a stationary receptacle, a hollow rotary drum journaled in said receptacle, means for continuously rotating said drum, fluid conduit means delivering a heat transfer fluid to the interior of said drum, means maintaining a preselected fluid level in said drum, and a plurality of hollow fluid circulating elements radially disposed on said drum for rotation therewith, said elements having feed duct means opening therein remotely from said drum for progressively admitting fluid thereto from said drum to fill said elements during the descending quarter cycle of rotation below said fluid level, said feed duct means including partition means in said elements retaining the fluid in said elements during the ascending half cycle of rotation of said elements, and said feed duct means discharging the fluid from said element during the descending quarter cycle of rotation of the leading edge thereof into alignment with the fluid level in said drum.

2. Heat exchange apparatus comprising, a stationary outer receptacle, a hollow rotary drum journaled in said receptacle, means for continuously rotating said drum, fluid conduit means for admitting fluid to the interior of said drum, means maintaining the fluid level in said drum substantially at its medial axis, means delivering a heat transfer fluid to said conduit means, and a plurality of hollow radial fluid circulating elements having leading and trailing edges mounted on said drum for rotation therewith, said fluid circulating elements having fluid chamber means and feed duct means opening remotely from said drum into said chamber for progressively admitting fluid thereto from said drum to substantially fill each of said elements during the descending quarter cycle of rotation of the leading edge thereof below sad fluid level, said feed duct means including partition means in said elements retaining the fluid in said elements during the ascending half cycle of rotation of the leading edge thereof, said feed duct means discharging the fluid from said elements during the descending quarter cycle of rotation of the leading edge thereof above the fluid level in said drum.

3. Heat exchange apparatus comprising, a stationary outer receptacle, a hollow rotary drum journaled in said receptacle, means for continuously rotating said drum, fluid conduit means for admitting fluid to the interior of said drum substantially uniformly along the length thereof, means maintaining the fluid level in said drum substantially at its medial axis, means delivering a heat transfer fluid to said conduit means, and a plurality of hollow radial fluid circulating elements having leading and trailing edges mounted on said drum for rotation therewith and disposed along said drum to sweep out overlapping paths traversing substantially the entire area of said receptacle, said fluid circulating elements having a fluid storage chamber and radial feed duct means intercoupled therewith remote from said drum for progressively admitting fluid thereto from said drum to substantially fill each of said elements during the descending quarter cycle of rotation of the leading edge thereof below said fluid level, said feed duct means including partition means in said element retaining the fluid in said elements during the ascending half cycle of rotation of the leading edge thereof, and said duct means discharging the fluid from said elements during the descending quarter cycle of rotation of the leading edge thereof above the fluid level in said drum.

4. Heat exchange apparatus comprising, a stationary outer receptacle, a hollow rotary drum journaled in said receptacle, means for continuously rotating said drum, fluid conduit means for admitting fluid to the interior of said drum, means maintaining the fluid level in said drum substantially at its medial axis, means delivering a heat transfer fluid to said conduit means, and a plurality of fluid circulating elements formed of hollow one quadrant sectors having leading and trailing edges radially disposed on said drum for rotation therewith, said sectors each having flow control means including a divider partition therein adjacent the leading edge thereof to define a primary channel coupled to the interior of said drum for coupling fluid therebetween and a fluid reservoir extending throughout the remainder of each sector coupled to said primary channels by an opening in said partition remote from said drum, whereby fluid is progressively admitted through the primary channel and remote partition opening from said drum to substantially fill the reservoir of each of said sectors during the descending quarter cycle of rotation of the primary channel thereof below said fluid level, the

fluid being maintained in said sector reservoirs by said divider partition during the ascending half cycle of rotation of the primary channels thereof and discharged through said remote opening and primary channel into said drum during the descending quarter cycle of rotation of the primary channels thereof into alignment with the fluid level in said drum.

5. Heat exchange apparatus comprising, a stationary outer receptacle, a hollow rotary drum horizontally journaled in said receptacle, means for continuously rotating said drum, fluid conduit means for admitting fluid to the interior of said drum including a plurality of spaced discharge openings extending along said conduit means to uniformly distribute fluid throughout the length of said drum, overflow means maintaining the fluid level in said drum substantially at its medial axis, means delivering heat transfer fluid to said conduit means, and a plurality of fluid circulating elements formed of hollow one quadrant sectors having leading and trailing edges radially disposed on said drum for rotation therewith and disposed along said drum to sweep out overlapping paths traversing substantially the entire area of said receptacle, said sectors each having flow control means including a divider partition disposed therein to define a primary channel adjacent the leading edge thereof coupled to the interior of said drum and a fluid reservoir extending throughout the remainder of each sector coupled to said primary channels by an opening in said partition remote from said drum, whereby fluid is progressively admitted through the primary channel and remote partition opening from said drum to substantially fill the reservoir of each of said sectors during the descending quarter cycle of rotation of the primary channel thereof below said fluid level, the

fluid being maintained in said sector reservoirs by said divider partitions during the ascending half cycle of rotation of the primary channels thereof and discharged through said partition opening and primary channel into said drum during the descending quarter cycle of rotation of the primary channels thereof into alignment with the fluid level in said drum.

6. Heat exchange apparatus comprising, a stationary outer receptacle, a hollow rotary drum journaled in said receptacle, means for continuously rotating said drum, fluid conduit means for admitting fluid to the interior of said drum, means maintaining the fluid level in said drum substantially at its medial axis, means delivering a heat transfer fluid to said conduit means, and a plurality of radial fluid circulating elements mounted on said drum for rotation therewith formed of radial sectors having means defining a radial primary channel aligned with a leading edge thereof and a fluid reservoir, the primary channel progressively admitting fluid under gravitational bias from said drum to the reservoir associated therewith to substantially fill the reservoir during the descending quarter cycle of rotation of the primary channel below said fluid level, said channel defining means retaining the fluid in said reservoir during the ascending half cycle of rotation of the leading edge, and said primary channel discharging the fluid under gravitational bias from the reservoir through the primary channel to said drum during the descending quarter cycle of rotation of the primary channel into alignment with the fluid level in said drum.

'7. Heat exchange apparatus comprising, a stationary outer receptacle, a hollow rotary drum journaled in said receptacle, means for continuously rotating said drum, fluid conduit means for admitting fluid to the interior of said drum, including a plurality of spaced discharge openings extending along said conduit means to uniformly distribute fluid throughout the length of said drum, overflow means maintaining the fluid level in said drum substantially at its medial axis, means delivering a heat transfer fluid to said conduit means, and a plurality of radial fluid circulating elements mounted on said drum for rotation therewith and disposed along said drum to sweep out overlapping paths traversing substantially the entire area of said receptacle, formed of radial sectors having partition means defining a radial primary channel aligned with a leading edge thereof and a fluid reservoir, the primary channel progressively admitting fluid under gravitational bias from said drum to the reservoir associated therewith to substantially fill the reservoir during the descending quarter cycle of rotation of the primary channel below said fluid level, said partition means retaining the fluid in said reservoir during the ascending half cycle of rotation of the leading edge, and said primary channel discharging the fluid under gravitational bias from the reservoir through the primary channel to said drum during the descending quarter cycle of rotation of the primary channel into alignment with the fluid level in said drum.

8. Heat exchange apparatus comprisng an outer receptacle, fluid coupling means disposed in said receptacle for rotation about a horizontal axis, means for continuously rotating said coupling means, means delivering a heat transfer fluid to said coupling means, means maintaining a reference fluid level proximate to the axis of rotation of said coupling means, a plurality of radial circulating elements coupled to said fluid coupling means for rotation therewith, and means for gravity charging and discharging fluid from said coupling means to said elements including feed duct means to progressively charge each element with fluid at a point remote from said fluid coupling means to substantially fill the same during the descending quarter cycle of rotation of each element below said reference fluid level, said feed duct means including partition means in said elements to retain the fluid in each element during the ascending half cycle of rotation thereof, said feed duct means discharging the fluid from each element during the descending quarter cycle of rotation of the leading edge thereof into alignment with said reference fluid level.

9. In heat exchange apparatus, the combination recited in claim 1, wherein said feed duct means includes a tubular conduit projecting through the wall of said drum and into the hollow core thereof providing a raised surrounding lip to prevent drainage of fluid into downwardly oriented elements when fluid is exhausted from said drum.

ERNEST A. ROSE.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,011,032 Blanchard Aug. 13, 1935 2,453,718 Mason et a1. Nov. 16, 19%

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