Patent Abstract:
A conveyor for moving hot material at temperatures on this order of 1000° F. or higher along a trough receiving the material has one or more cooling liquid flow vessels extending over but spaced from the outer surface of a trough inner wall to indirectly cause cooling of the inner wall. A heat transfer connection conductively interconnect the vessel and the inner trough wall such as interposed thin webs or plates, or alternatively a mass of conductive beads interposed to controllably transfer heat into the cooling liquid flow vessel. A series of wear plates are clamped to a pushing side of a helical tube of an auger type conveyor, which tube can also receive a flow of cooling liquid. The arrangement of a mass of conductive beads is used to provide a non rigid mechanical support of fluid carrying tubing, the support having a predetermined thermal conductivity.

Full Description:
CROSS REFERENCE TO RELATED APPLICATION 
       [0001]    This application is a divisional of U.S. Ser. No. 11/140,694 filed on May 31, 2005, which is a continuation-in-part of U.S. patent application Ser. No. 10/134,993 filed on Apr. 29, 2002 which claims the benefit of U.S. provisional application S.N. 60/586,685 filed on Jul. 9, 2004. 
     
    
     BACKGROUND OF THE INVENTION 
       [0002]    This invention concerns methods and arrangements for liquid cooling of structures contacting very hot materials which prevent the development of excessively high temperatures in the structure which can cause mechanical failures due to thermal stress. In conventional liquid cooling, liquid coolant typically flows through vessels in contact with the structures and a loss of cooling capacity may occur if the liquid coolant flowing in coolant vessels associated with the structures boils. This is a particular problem in conveyors such as auger or re-circulating chain flight conveyors used to convey very hot crushed or granular material exceeding 1000 EF through troughs such as in cement plants, lime kilns, power plants, etc. Conveyors for such very hot materials have in the past had short service lives and were prone to failure. This is because of the effect of the high temperatures reached by the conveyor components as a result of conduction of heat from the conveyed material into the structure and components. Such conveyors have sometimes incorporated liquid cooling jackets within the conveyor trough along which the hot material is conveyed as by an auger extending along the length of the trough. In the past, the trough and jacket have been constructed as a weldment, and since the liquid cooled liner is in direct contact with the hot material conveyed, the welds are severely stressed by gross thermal expansions and contractions. 
         [0003]    The resulting expansion and contraction of the trough and coolant jacket leads to cracking, buckling, weld failures and similar structural failures. If very hot material is conveyed (1000 EF or higher), cooling liquid in direct contact with the cooling jacket wall is heated to boiling, so that vapor is generated in the jacket, greatly reducing the rate of heat conduction into the cooling liquid. 
         [0004]    The high heat flux boiling that is encountered, usually has regions of unstable film boiling which causes a thermal shock in the structure surface, which in turn can cause plastic mechanical behavior. This can lead to premature failure and has been studied mathematically and experimentally. See Kappila, R. W., “A Boiler Tube Problem, Elastic-Plastic Behavior of a Thick-Walled Cylinder Caused By Sinusoidal Inside Surface Temperature, Internal Heat Generation, and External Heat Flux,” PhD Dissertation, University of Michigan, 1968. 
         [0005]    Since the trough cooling jacket is constructed as a weldment, it often is not designed or approved for use as a pressure vessel, allowing only very low coolant pressures and thus low flow rates imposing a substantial limitation on the rate of heat removal. 
         [0006]    Similarly, conveying augers have also often been constructed as a weldment, with a central tube having radial spokes welded to a central tube forming a triangular cavity. Liquid coolant has sometimes been circulated through such an auger, with direct contact of the coolant with the metal auger which in turn is in direct contact with the hot material conveyed, leading to the same problems described above in connection with the conveyor trough. 
         [0007]    Direct air cooling of the hot material requires dust collection equipment and baghouses and necessitates government permits, as pollutants may be mixed with the exhausted cooling air. 
         [0008]    Many other industrial applications and high technology projects experience such difficulties, such as, screw conveyors in hot quick lime production, power plant hot clinker removal, hot surfaces of space vehicles during re-entry into the earth=s atmosphere, cooling high temperature engines and jets, boilers, etc. 
         [0009]    It is an object of the present invention to provide arrangements and methods to control heat transfer into a liquid coolant within a flow vessel used to cool a hot material of the type described, in which direct contact of a liquid coolant with the structure holding the hot material is avoided. 
         [0010]    It is a further object to provide a conveyor for hot material which avoids the use of weldments to mount parts subjected to thermal stresses induced by a large temperature differential between connected parts of the conveyor. 
       SUMMARY OF THE INVENTION 
       [0011]    The above objects as well as other objects which will be understood upon a reading of the following specification and claims are achieved by a heat transfer arrangement including a connection between a coolant flow vessel and an inner wall structure to be cooled in which a desired controlled rate of heat transfer may be easily achieved to limit the rate of heat transfer to a predetermined level. This heat transfer arrangement connection may comprise a plurality of spaced apart stand off supports spacing the coolant vessel from the structure to be cooled. The stand off support crates a limited conductive heat transfer path between the structure to be cooled and the coolant vessel. 
         [0012]    The stand offs may be comprised of an array of thin webs in contact with the inner wall and extending to the coolant vessel and outer wall. 
         [0013]    As a preferred alternative, a mass of heat conductive beads of a predetermined size and configuration maybe confined in a space between the structure to be cooled and a coolant vessel as by an outer wall. 
         [0014]    In one application of the invention, a conveyor including a trough along which hot material is conveyed, has separate liquid flow vessels passing over but spaced from an outside surface of the trough wall. The flow vessels are supported on the outer surface of the inner trough wall by heat conducting standoff supports such as interposed thin metal strips, angled metal strips or curved thin metal standoffs. A mass of conductive beads or particles may alternatively be provided, filling the space between the outer surface of the inner trough wall and the inner surface of an outer confining wall located beyond the coolant flow vessels. 
         [0015]    Optionally, air flow can also be drawn in through openings in the outer wall and directed over the liquid flow vessels, and through the fins or beads to enhance cooling of the same. 
         [0016]    The coolant liquid flow vessels can be arranged in longitudinal or transverse loops or longitudinally extending straight sections, and may supplied with a cooling liquid from a manifold at one end of the conveyor trough. 
         [0017]    A helical auger tube mounted within the conveyor trough may have a side by side series of radially extending clamp-on wear plates of a durable material can be installed on the pushing side of the helical auger tube to prevent excessive wearing of the auger tube. The clamped attachment construction avoids thermally stressed welds. Optionally, a cooling fluid can also be circulated through the helical auger tube, or a second tube can be inserted in a larger outer helical tube with a series of metal strips or a mass of heat conductive beads, conducting the heat between the outer tube and the heat transfer liquid in the inner tube. 
         [0018]    The arrangement of a mass of heat conductive beads, i.e., particles, in the space between a hot structure and a cooling structure provide a solution to excessive thermal stress and coolant boiling problems with minimum mechanical stiffness. In particular, the use of heat conductive particles interposed between the hot and cool surfaces such as a tube containing cooling water inside of a larger tube exposed to the high temperatures allows a precisely controlled rate of heat transfer therebetween. If the particles are spherical in shape, the mechanical stiffness of the medium is minimal and thermally induced stresses are avoided, furthermore, the contact area between the particles is also small to restrict the amount of heat being conducted through the mass of particles. If smaller size particles are used, the void ratio or open space is reduced which increases the contact area and the thermal conductance of the medium. 
         [0019]    If the particle surfaces are flattened and made to fit adjoining particle surfaces, the contact area is farther increased and more heat is conducted. If the particles were shaped to be matched or complementary to each other perfectly with no void space, the medium is compact and approaches the heat transfer characteristic of a solid, except that the mechanical stiffness is still very small and the thermal stresses are minimized. 
         [0020]    Use a material of a higher or lower thermal conductivity to construct the beads also allows a variation in overall thermal conductivity. Thus the thermal conductivity can be closely controlled to achieve a precisely predetermined heat transfer rate to suite a particular application. 
     
    
     
       DESCRIPTION OF THE DRAWINGS 
         [0021]      FIG. 1  is a perspective view of an auger conveyor according to the present invention showing a portion of a helical tube auger included in the conveyor in broken lines.  FIG. 1 . 
           [0022]      FIG. 2  is an enlarged partially broken away end view of the conveyor shown in 
           [0023]      FIG. 3  is an end view of the conveyor of  FIG. 1 , with the trough outer wall partially broken away and showing further details of a coolant flow tubing installation for the trough. 
           [0024]      FIG. 4  is an end view of the conveyor with the outer wall broken away showing another form of coolant flow tubing installation for the trough. 
           [0025]      FIG. 5  is a perspective partially fragmentary view of another embodiment of the conveyor according to the present invention. 
           [0026]      FIG. 6  is an enlarged fragmentary perspective view of one end of the conveyor shown in  FIG. 5  with the outer wall of the trough partially broken away. 
           [0027]      FIG. 7  is an enlarged perspective view of the end of the conveyor shown in  FIG. 5  with both walls of the trough partially broken away to show the helical tube auger. 
           [0028]      FIG. 8  is a fragmentary perspective view of the helical tube auger shown in  FIG. 7  with a single wear plate shown in solid lines and a phantom line depiction of the entire series of wear plates. 
           [0029]      FIG. 9  is an enlarged transverse section taken across the helical tube auger and clamp on pusher blade of the type shown in  FIG. 7 . 
           [0030]      FIG. 10  is an enlarged transverse sectional view across a square section form of the helical tube auger. 
           [0031]      FIG. 11  is an enlarged transverse sectional view of a trough coolant tube of the type shown in  FIG. 7 . 
           [0032]      FIG. 12  is a sectional view of an inner round tube nested within a round outer tube using an interposed mass of beads as the heat transfer medium. 
           [0033]      FIG. 13  shows an outer square tube having an inner tube carrying a heat transfer fluid, and with a mass of heat conductive beads interposed. 
           [0034]      FIG. 14  shows a double walled conveyor trough having a mass of interposed beads as a heat transfer medium. 
           [0035]      FIG. 14A  is an enlarged view of the beads shown in  FIG. 14 , flattened to increase the contact area and thereby increase the thermal conductivity of the medium. 
           [0036]      FIG. 15  is a diagram showing the relationship between thermal conductivity and the void space defined within a mass of heat conductive beads. 
       
    
    
     DETAILED DESCRIPTION 
       [0037]    In the following detailed description, certain specific terminology will be employed for the sake of clarity and a particular embodiment described in accordance with the requirements of 35 USC 112, but it is to be understood that the same is not intended to be limiting and should not be so construed inasmuch as the invention is capable of taking many forms and variations within the scope of the appended claims. 
         [0038]    Referring to the drawings and particularly  FIG. 1 , a conveyor  10  is shown which includes an inclined trough  12  provided with optional covers  14  installed along the top thereof except at a loading opening  16 . 
         [0039]    The trough  12  is supported to be upwardly inclined by means of frame supports  18 , at either end. 
         [0040]    A discharge chute  22  is at the upper end. A helically wound auger tube  24  is disposed lengthwise in the trough  14  and rotated by a rotary drive  26 . A heat transfer liquid such as water used as a coolant is typically introduced at the discharge end through an axial inlet  32  and through a side inlet  34 , and exits outlets  28 ,  30  at the lower end of the conveyor  10 . 
         [0041]    A source  34 A,  32 A of as a liquid coolant is respectively connected with each inlet  34 ,  32  and a coolant recycler (such as cooling towers) may be connected with each outlet  28 ,  30 . 
         [0042]      FIG. 2  shows further details. U-shaped loops of fluid flow tubing  36  are located between an inner trough wall  38  and an outer wall  40 . The inner wall  38  typically would be made of heavy gauge metal to provide adequate structural support and durability as the conveyed material is in direct contact therewith and its weight supported thereby. The outer confining wall  40  can be of lighter gauge sheet metal or even a material having openings therein allowing air circulation through the intervening space such as the mesh material  40 A indicated in  FIG. 7 . 
         [0043]    The flow tube  36  is supported by interposed pieces here comprised of a series of side by side transverse thin metal fins or plates  42  contacting limited areas of the tubing  36  on edge, the outside surface of the inner wall  38  and the inner surface of the outer wall  40 . Thus, liquid coolant does not directly contact the hottest structure, i.e., the inner wall  38 , but rather there is only an indirect heat conducting path comprised of the interposed pieces, i.e. the fins or plates  42  contacting limited areas on the flow tubes  36 . 
         [0044]    The total area of contact and thus the conductivity of the pieces may be selected to allow conduction of heat into the liquid in the tubing  36  at a lower rate such as to  42  not result in boiling of the coolant liquid flowing within the tubing  36 . The fins or plates  42  may extend between the inner wall longitudinally so that an air flow can optionally be blown through the space and over the fins or plates  42 , from an air source  39 . 
         [0045]    Cooling liquid may also be circulated through the helical auger tube  24  introduced via a rotary fluid coupling  44  into a central support tube  46  rotated by the rotary drive  26  and supported by a rotary bearing  48  ( FIG. 1 ). 
         [0046]    Liquid is directed into the helical tube  24  via a radial support tube  50  mechanically attached to the support/drive tube  46 . The support tube  46  is blocked so as to avoid circulation through the support tube  46  which would be overheated if the conveyed material was at a sufficiently high temperature, i.e., on the order of 1000° F. or higher. Outlet flow is directed out into a support tube  46  at the lower end of the conveyor. 
         [0047]      FIG. 3  shows another view of the trough coolant flow tubing  36  showing the U-shaped loops of tubing  36  and outlet  30 , the loops extending transversely to the axis of rotation of the tube  24 , i.e., in circumferential directions, although occupying only a portion of the perimeter of the trough  12 . 
         [0048]      FIG. 4  shows a variation in which coolant flow tube loops  36 A are arranged longitudinally, and the fins or plates  42 A are oriented transversely to the longitudinal axis of the conveyor  10 . 
         [0049]      FIG. 5  shows another form of the conveyor  52  in which an inlet manifold  58  is connected to an inlet  60  at the upper end and an outlet manifold  54  is connected to an outlet  56 . A series of straight longitudinal flow tubes  62  (best seen in  FIG. 6 ) extend the length of the trough  64  in the space between an inner wall  66  and outer wall  68 . 
         [0050]    As shown in  FIG. 7 , the tubes  62  are supported on the inner wall  66  by interposed pieces composed of thin metal straight strips  70  and curved thin metal bar stand offs  72  ( FIG. 11 ). 
         [0051]    Thus, the fluid does not directly contact the hottest structure, i.e., the trough inner wall  66 , but rather has an interposed heat conductive connection thereto confined to a limited area of the tube  62  and wall  66 . This reduces the rate of heat transfer to prevent a loss of conductivity which would result from a heat transfer rate causing boiling of the cooling liquid. 
         [0052]    In order to reduce abrasion wear of the auger tube  74 , a series of wear plates  76  are clamped on the pushing side of the auger tube  74 , edge to edge along the length of the helical tube  74  ( FIG. 8 ). This clamp-on construction is used instead of a welded conventional attachment to reduce thermal stress and avoid structional failures. 
         [0053]    The hot granular material  80  being conveyed could otherwise rapidly wear the tube  74  depending on the material characteristics, temperature, as well as the volume conveyed. 
         [0054]      FIG. 9  shows details of the attachment clamps for the wear plates  76  which are preferably constructed of a material such as an Nichrome alloy which is wear resistant at elevated temperatures. 
         [0055]    A U-bolt  82  passes through a clamping piece  84  and is secured by nuts  86 . 
         [0056]    A pair of opposing legs  88 ,  90  on the wear plate  76  and clamping piece  84  have cut outs mating with the auger tube  74 . 
         [0057]      FIG. 10  shows a square section tube  74 A, such that a flat wear plate  76 A and clamping piece  84 A can be secured with the U-bolt  82 A and nuts  86 . 
         [0058]    Both forms of wear plates  76  and  76 A can have an angled portion  94  to assist in effectively pushing the material by rotation of the auger tube  74  or  74 A. The clamp-on design avoids the problem of weld failure resulting from the high temperatures reached by the tube  74  when very hot material (1000 EF or higher) is conveyed. 
         [0059]      FIGS. 12-15  illustrate the use of an interposed mass of beads as a conductive connection having minimal mechanical rigidity while providing a controlled conductivity heat transfer path to a liquid coolant tubing so as to avoid boiling of the liquid by a too high rate of transfer of heat into the tubing. In  FIG. 12 , a round tube  88  as (used for auger tube  24 ) receives a smaller diameter inner coolant circulating tube  90 . An intermediate space is filled with a mass of heat conducting beads or particles  92  to establish a heat transfer path which can be of a controlled conductivity by controlling the proportion of void space, in turn varying with the bead size. The type of bead material would be selected depending on the desired design parameters, but would typically be a durable thermally conductive material such as aluminum. The bead size would likewise be set to achieve the desired coefficient of thermal conductivity (see below). 
         [0060]    A series of centering webs  94  should be provided to maintain the tubes centered with respect to each other while the space therebetween being loaded with the beads. 
         [0061]      FIG. 13  allows a round inner tube  96  and square outer tube  98  and centering webs  100 . 
         [0062]      FIG. 14  shows a portion of a trough inner wall  102  and outer wall  104  with an intervening space filled with a mass of beads  106 . Spacer webs  108  are also provided. This is intended to produce a precisely controlled designed for thermal conductivity selected so as to not cause boiling of the coolant and to thereby avoid the resultant loss of heat transfer into the coolant due to the presence of water vapor and boundary layer effects. 
         [0063]      FIG. 14A  shows flattened particles or beads  106 A, which flattening reduces the void space and increases the contact area between the beads to increase the overall thermal conductivity of the medium. 
         [0064]      FIG. 15  shows the relationship between the proportion of void space and thermal conductivity. 
         [0065]    Large diameter, spherical beads will conduct the heat while still allowing relative movement as induced by differing coefficients of thermal expansion of the adjacent structures without causing excessive stresses. Beads or particles of other regular shapes or irregular shapes could be selected that serve the same basic purpose of controlling thermal conductivity. 
         [0066]    The proper selection of the spherically shaped particles involves diameter, material, and relative pipe sizes. If the space were filled with particles that would create a very large proportion of would void space, this approximate the conductivity of air, and the thermal conductivity would therefore be very low. However, if the space were filled with very small particles with minimal void space, this would approach the thermal conductivity of a solid and the heat transfer rate would therefore be high, approaching that of the material of the beads. Somewhere between these two extremes is a void ratio that would be in line with the desired heat transfer characteristics. By properly selecting the particle sizes and material, and the overall geometry of the thermal screw, a design may be achieved which reduces thermal stresses to a level where structural problems are avoided, and sufficient material cooling is accomplished. 
         [0067]    It should be noted that with proper design, forces due to dimensional changes from thermal effects, as well as thermal stresses cause by thermal gradients within structural members may be effectively controlled.

Technology Classification (CPC): 5