Abstract:
A centrifugal dryer ( 10 ) has a plurality of conveyors ( 12 ) that are arranged inside a pair of trunnion rings ( 36 ) such that the conveyors ( 12 ) are shingled to form a polygon shaped cylinder ( 14 ) that rotates about the central axis (A—A) of the trunnion rings to create centrifugal forces on produce, or other material conveyed on the conveyors. Each conveyor ( 12 ) has an elongated endless porous belt ( 18 ) driven in one direction by a one-way bearing to convey material from the inlet end to the outlet end of the conveyor. A crank arm ( 56 ) extends from each one-way bearing and rides in a gimbal ring ( 50 ) which causes reciprocating motion of the crank arm ( 56 ) to intermittenly advance the conveyors ( 12 ) as they rotate. The gimbal ring ( 50 ) can be positionally adjusted to vary the amount each conveyor ( 12 ) advances per revolution, or it can be set in a neutral position where no movement is imparted to the crank arms ( 56 ), thereby allowing the dryer to process in a batch mode. A conical inlet ( 58 ) and outlet ( 61 ) are designed to minimized damage to the produce upon entry into and exit from the dryer.

Description:
BACKGROUND OF THE INVENTION 
     1 . Field of the Invention 
     The present invention relates, generally, to an apparatus for drying materials, and is particularly suited for drying of vegetables 
     2. Background Information 
     Produce, such as vegetables, is typically treated with a chlorine solution prior to packing and shipping for the end market. For leafy vegetables that are often packaged in bags, the vegetables are processed in a slurry form. The bulk of the water can be drained by gravity. However, all excess moisture must be completely removed from the surface of the produce as mold and rot will ensue. Additionally, the produce cannot be damaged during the drying process, as damaged produce either cannot be sold or brings a reduced price. Commercial produce packaging plants, therefore, further “dewater” produce in a commercial dryer. 
     There are many known commercial dryers using centrifugal force to remove moisture from produce. U.S. Pat. Nos. 4,493,156 to Siegmann and 5,027,5302 Volmer et al. disclose a vertical and horizontal drying apparatus respectively. However, the drying processes of prior art dryers are particularly damaging to produce and much is ruined, with the end result of unacceptable levels of waste. Additionally, existing dryers typically process produce in either a continuous or intermittent (batch) sequence. They do not provide the options for continuous and batch mode of operation in a single dryer. Further, the capacities of these dryers are not sufficient to meet today&#39;s demand for high-speed automation, such as processing leafy type vegetables in the range of 2000-7000 pounds per hour. 
     Applicant&#39;s invention provides an improved dryer which overcomes the limitations and shortcomings of the prior art. 
     BRIEF SUMMARY OF THE INVENTION 
     The present invention provides a cetrifugal drying apparatus for dewatering produce or removing liquid from other materials. The dryer comprises a plurality of conveyors that are arranged inside a pair of trunion rings such that the conveyors are shingled to form a polygon shaped cylinder that rotates about the central axis of the trunion rings to create centrifugal forces on produce, or other material conveyed on the conveyors. The shingled orientation of the conveyors reduces product spillage and increases yield. A conical inlet and outlet are designed to minimize damage to the produce upon entry into and exit from the dryer. Each conveyor has an elongated endless porous belt driven in one direction by a conveyor drive mechanism to convey material from the inlet end to the outlet end of the conveyor. A control mechanism is connected to the conveyor drive mechanisms to advance conveyors an amount with each revolution of the trunion rings. A drive mechanism is connected to at least one of the trunion rings to rotate the trunion rings and thereby rotate the conveyors about the central axis. 
     Each conveyor drive mechanism includes a one-way bearing which is actuated in one embodiment by a lever arm extending radially therefrom. The lever arms are received in a portion of a gimbal ring which causes the lever arms to reciprocatingly move an amount with each revolution of the trunion rings. The gimbal ring is positionable about a transverse axis to vary the amount of reciprocating movement, thereby varying the amount the conveyors advance with each revolution. The gimbal ring can also be set in a neutral position where no movement is imparted to the crank arms, thereby allowing the dryer to process in a batch mode. 
     In another embodiment of pair of slidable concentric rings are substituted for the gimbal ring to achieve the same effect on the lever arms. 
     In still another embodiment a friction roller is connected to the one-way bearing rather than a lever arm and a friction ring is rotated independently of the conveyors and trunion rings to control the amount the friction rollers turn with each revolution of the the trunion rings. In a variation of this embodiment the friction ring has individual segments which can be selectively actuated to engage or disengage the friction rollers. 
     In still another embodiment, the friction rollers are cone-shaped and the control mechanism includes a stationary friction drive ring segment positioned adjacent the friction cones to intermittently contact the friction cones as the conveyors and trunion rings rotate. The friction cones are axially adjustable to provide variable circumferential contact with the friction drive ring, thereby controlling the amount each conveyor advances each time its cone contacts the drive ring segment. 
     The features, benefits and objects of this invention will become clear to those skilled in the art by reference to the following description, claims and drawings. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a perspective view of the dryer drum of the present invention consisting of a plurality of individual endless belt conveyors spaced to form a side-by-side shingled cylindrically-shaped polygonal conveyor assembly and showing an outlet discharge belt. 
     FIG. 2 is a side view of the conveyor assembly of FIG.  1  and disclosing a conical feed inlet. 
     FIG. 3 is an end view of the conveyor assembly and better showing the individual shingled conveyors, a stationary frame supporting the drum, and a trunion drive system to drive the drum relative to the frame. 
     FIG. 4 is an end view of the cylindrically shaped polygon conveyor better showing the structure supporting the conveyors. 
     FIG. 5 is a cross sectional view of a conveyor belt and its supporting structure taken along line  5 — 5  in FIG.  2 . 
     FIG. 6 is a cross-sectional view like FIG. 5 of an alternate embodiment of a conveyor belt and its supporting structure. 
     FIG. 7 is a schematic end view of the dryer drum and a gimbal ring used to drive the conveyors in a step-wise manner. 
     FIG. 8 is a schematic side view of the gimbal ring rotated off vertical to cause a one way bearing crank arm of each conveyor (two arms shown) to move back and forth. 
     FIG. 9 is an enlarged view of a crank arm on a conveyor capable of moving both back and forth via the gimbal ring but its corresponding conveyor will only move in one direction. 
     FIG. 10 is a perspective view of the exit portion of the dryer illustrating a conical shaped exit ring and a collection conveyor below it. 
     FIG. 11 is a side view of the dryer drum of FIG. 1 shown mounted within a schroud and with a drip pan beneath the drum. 
     FIG. 12 is an end view of FIG.  1 . 
     FIG. 13 is a schematic end view of an alternate embodiment of the conveyor assembly disclosing a friction drive ring, mating with individual friction drive wheels, for driving the individual conveyors. 
     FIG. 14 is a schematic end view of an alternate embodiment of intermittent drive system employing individually actuated ring segments. 
     FIG. 15 is another alternate embodiment of intermittent drive system employing a spring loaded ring segment that drives an adjustable cone beveled gear assembly, which in turn drives a corresponding conveyor. 
     FIG. 16 is a schematic end view of an alternate embodiment of the drive mechanism that drives the individual conveyors through a pair of sliding concentric rings. 
     FIGS. 17A-B are schematic side views of corresponding conveyors with their corresponding one way bearing crank arms moving in rocking motion by action of the slide rings of FIG.  16 . 
     FIG. 17C is a schematic detail illustrating the slide ring mounting and shifting system; 
    
    
     DETAILED DESCRIPTION 
     Referring to FIGS. 1-3, an example of the preferred embodiment of the present invention is illustrated and generally indicated by the reference numeral  10 . The dryer is described below first in terms of its major structural elements and then in terms of its secondary structural and/or functional elements which cooperate to perform the drying function. 
     The present invention is directed to a centrifugal dryer for passive large scale drying or dewatering (the removal of additional water from a product). Although the dryer is most suitable for produce, and particularly for vegetables, the features of the present invention, as further discussed below, make it ideally situated for other products, beyond produce, or as a means for separating different solids from liquids. 
     Referring to FIGS. 1-3, the present invention is directed to a dryer having a drum  10  which consists primarily of a plurality of shingled individual conveyors  12  forming an essentially cylindrically-shaped polygon conveyor assembly  14  where all the conveyors rotate about an axis A—A, which is the centerline of rotation. In operation, the individual conveyors  12 , while rotating about axis A—A, convey product such as produce (not shown) from the inlet end of drum  10  to the outlet end of drum  10 , at which point that the dewatered product is discharged from drum  10 . Liquids (e.g. water) are separated from the produce (vegetables, etc.) by centrifugal force during operation. 
     Referring particularly to FIG. 4, each conveyor  12  is positioned relative to adjacent conveyors to create a shingling effect such that when the conveyor assembly  14  is rotated in the direction of the arrow, materials on the conveyors  12  can tumble from one conveyor to another without material becoming lodged between conveyors. For example, material on conveyor  12   a  could fall onto conveyor  12   b , and that on  12   b  could fall onto  12   c , etc. This shingling feature significantly reduces gaps between the individual conveyors and allows the rotating product to maintain constant contact with the conveyors during rotation, thereby reducing damage to the product (especially fragile produce). 
     The shingling effect is accomplished by having the plane representing the inner belt surface of one conveyor ( 12   a ) intersect the surface of the subsequent adjacent conveyor ( 12   b ). In the preferred embodiment, this is accomplished with belts of uniform circumference being mounted non-tangentially relative to the rotational drive member. Conveyor support members  13  are attached to round channels  36  such that conveyor support members  13  extend radially inward from channels  36  and are uniformly spaced around them. Conveyor mounting plates  15  attach to each end of a conveyor support frame  26  that supports a conveyor  12 . The conveyor mounting plates  15  attach between two adjacent conveyor support members  13  such that an angle θ is formed between the conveyor surface and a secant line  16  extending between conveyor support members  13  at round channel  36 . For an assembly of six belts as shown, the preferred angle θ is approximately five degrees. 
     An alternate way of accomplishing the shingling effect would be to use slightly tapered belts that could be mounted tangentially with respect to round channels  36 . However, because of the availability of conventional belts having a uniform circumference the above described method of accomplishing the shingling effect is preferred. 
     Referring also to FIG. 5, each conveyor  12  includes an endlessly conveyed porous or perforated belt  18 . The belt  18  of each conveyor is preferably made of a polymer compound that is food grade approved. The belt  18  is driven by a shaft  20  (FIG.  3 ), which is driven by a gimbal drive ring that will be discussed in detail below. The belt moves in one direction, which is shown by the arrow  22  (FIGS.  1  and  9 ). The belt is conveyed in the direction of arrow  22  and returns once the belt has rotated about its end drive wheel  24 . 
     Belt  18  preferably includes a plurality of tabs  28  on its bottom surface near each outer edge and spaced across the belt which cooperate with guide rails  30  attached to conveyor support frame  26  to track the belt during use and to resist centrifugal force pulling the return portion  100  of belt  18  away from the conveyor support frame  26 . The guide rails  30  may have a surface made of UHMW plastic where they interface with belt  18 . The use of UHMW plastic eliminates the need for lubrication and is ideal for wet environments. 
     Alternatively belt  18  may not have tabs  28  to constrain the belt during operation. In that case, support frame  126  may have side elements  132  to constrain the belt laterally along with guide rails  130  to support the belt against centrifugal force. To support return portion  100  of belt  18 , support frame  126  has outer portion  134  disposed outside of return portion  100  with guide rails  130  extending inwardly therefrom. Outer portion  134  has side elements  136  to laterally constrain the return portion  100 . Guide rails  130  may have a friction reducing surface or insert  128  to reduce friction or to act as a wear surface. Insert  128  may be made of any suitable material such as UHMW plastic or TEFLON®. 
     Referring again to FIGS. 1-4, the polygonal conveyor assembly  14  is driven by a drive system that rotates the conveyor assembly about axis A—A. In a preferred embodiment, a friction trunion roller drive system  34  engages a frame including round channels  36  that contains the polygonal conveyor assembly  14 . Round channels  36  are made by known techniques such as rolling straight channels to a round shape, or machining rolled, forged or cast material. Preferably, the frame includes a pair of round channels of a size and shape to engage a pair of trunion wheels  38 , which are mounted on a trunion shaft  42 . The trunion shaft and trunion wheels are mounted on a stationary frame  44 . An electric motor and gearbox  46  may be used to actuate a chain and sprocket drive  48 , which in turn drives the trunion wheels  38 , which in turn drives the round channels  36  for rotating the conveyor assembly  14  about the drive axis A—A. Alternatively, a chain may positively drive the conveyor assembly or the conveyor assembly may be driven by a combination of both positive engagement and friction elements. 
     Referring now to FIGS. 7-9, the present invention provides an external gimbal ring  50  mounted for pivotal tilting movement about the axis  51 — 51  at the pivotal mounting  52  on the gimbal ring frame  53 . The gimbal ring may be tilted about the axis  51 — 51  by a ram  54  (FIG. 2) but is otherwise stationary relative to the rotating conveyor assembly. The ram  54  may be pneumatic, hydraulic, or screw actuated or any suitable alternative equivalent. The gimbal ring, in combination with a one way bearing crank arm  56  located on the end of each conveyor drive shaft provides for step-wise movement of each conveyor belt  18 . The gimbal ring  50  rotates off vertical, as shown in angle β in FIG. 8, to cause the one way bearing crank arm  56  to rock back and forth, as indicated in FIG. 9, as the conveyor frame rotates relative to the gimbal ring  50 . When the arm  56  is rocked back and forth, a ratcheting effect advances the belt  18  in one direction indicated by arrow  22  in FIG. 9. A one way bearing  57  driven by crank arm  56  functions as a clutch so that the conveyor drive shaft  20  will rotate when the crank arm  56  is moved to the left by the gimbal ring  50  as shown in FIG.  9 . When the crank arm is moved to the right toward the vertical and therebeyond, however, the drive shaft  20  will not be rotated. The crank arm  56  is integral to a housing containing the one way bearing  57 . One way bearings are well known and may be a shell type roller such as the series HF, HFZ sold by INA Devcon Company. Conveyor shafts  20  are supported by antifriction bearings, preferably made of UHMW plastic. Each driven conveyor shaft  20  is engaged to rotate the end drive wheel  24  of the conveyor  12 . The speed of rotation of the drum  10  and tilt position of the gimbal ring determine conveyor speeds. Tilting the gimbal ring changes the length of the processing cycle (i.e. it alters the duration of dwells in the step-wise motion). 
     One aspect of the invention is the ability to also process the product in an intermittent, or batch method. This is accomplished by positioning the gimbal ring to have a neutral effect, such as by aligning it with the vertical line  55  in FIG.  8 . The endless conveyor assembly will rotate but will not be driven to convey any product. 
     Referring again to FIGS. 1 and 2, the present invention includes an inlet feed and an outlet discharge that is designed to minimize damage to any produce/product. The inlet feed is a conical member  58 , seen best in FIG. 2, having a larger opening  60  adjacent the conveyor assembly  14  and a smaller inlet opening  62  at the infeed end. Transfer of product to the inlet opening  62  in the conical member  58  may be accomplished through a conveyor carrying the produce/product with surface moisture, or by a flume, or by being pumped using water as a means of conveyance. If the produce/product is transferred by water, the conical member  58  may include perforations or mesh to allow the water to pass through the mesh and/or perforations and the product to accelerate outwardly onto the conveyor assembly  14 . The conical shape of the conical member  58  serves to rotationally accelerate the product/produce before it is transferred to the conveyor assembly  14 . The surface speed of the inlet opening  62  is proportionally smaller than the larger opening  60 , thereby rotationally accelerating product/produce moving from inlet opening  62  to larger opening  60 . Since the rotational speed of the conveyor assembly  14  is approximately that of the product/produce as it leaves larger opening  60  of conical member  58 , damage to the product/produce due to its transfer onto the conveyor assembly is greatly reduced. 
     Referring to FIGS. 1 and 10, two embodiments for the outlet discharge are illustrated. In FIG. 1 the produce/product is transferred from the conveyor assembly  14  to an endless discharge conveyor belt  64 . The discharge conveyor belt  64  need only cover approximately 180 degrees of conveyor assembly  14  because the conveyors  12  are only advancing, and thereby discharging product/produce, during approximately half of their rotation due to the operation of the gimbal ring described above. The discharge conveyor belt  64  is edge-driven by a drive ring  66 . The discharge conveyor belt may be supported similar to the belt guide rails described above and shown in FIG. 5 or by idling rollers  68 , as shown in FIG.  1 . Support for the rollers (or rails—not shown) may be attached and cantilevered to frame  44 . The discharge conveyor belt is oriented to allow for static change in the direction of the product/produce. Accumulation of the product/produce is generally accomplished downstream of the dryer in the production cycle to maintain the velocity of the drying processes and to maintain integrity of the product/produce. 
     The embodiment for the outlet discharge shown in FIG. 10 uses a conical shaped ring  61  supported by rollers  67   a, b  and  c . The ring  61  has a smaller diameter end  63  adjacent discharge ends of conveyors  12 , and a larger diameter end  65 . At least one of the rollers  67  is used to drive the ring  61 . In this embodiment rollers  67   a  and  67   b  are connected to the same shaft that has trunion wheels  38  used to drive trunion ring  36 . Rollers  67   a  and  67   b  are smaller diameter then trunion wheels  38 , thereby rotating ring  61  slower than the conveyor assembly  14  rotates. The speed of ring  61  relative to the conveyor assembly  14  is determined by the diameter ratio between rollers  67   a  and  b  and trunion wheels  38 . Alternatively, rather than driving ring  61  with rollers connected to the trunion wheels  38 , an independent drive source can be used to rotate the ring. For example, roller  67   a  may be connected to a variable speed motor to allow the rotational speed of the ring  61  to be controlled independently of the rotational speed of the conveyor assembly  14 . 
     As product/produce is conveyed from conveyors  12  onto ring  61 , the slower rotation of ring  61  and its outward and downward sloping shape direct the product/produce onto a collection conveyor  69  which is disposed below ring  61 . Conveyor  69  then conveys the product/produce away for further processing. To further facilitate product/produce being removed from ring  61  and onto conveyor  69 , a removal device  70 , such as an air knife, may be used to adjacent to ring  61 . 
     Referring to FIG. 2, the conveyor assembly  14  may be cleaned through the addition of a spray bar  71  on either an intermittent or continuous basis. The spray bar&#39;s location is shown illustratively, but may be positioned in various locations relative to the conveyor assembly depending on the application. Hygiene may be enhanced and product contamination can be reduced by the introduction of spray systems (or an individual spray bar such as discussed herein) on the infeed end of the conveyor assembly. 
     Referring to FIGS. 11 and 12, the dryer drum  10  is mounted within a shroud  72 . Preferably, the shroud is self-supporting and is anchored to the floor. A drip pan  74  may be attached to the frame, beneath the conveyor assembly. The drip pan  74  collects the excess water during the drying process. Sloping sidewalls  76  of the drip pan funnel any collected water into a well  78  which may include an opening (not shown) for ease in draining the contents of the drip pan. Preferably, the shroud and drum components (less the belt) are made of Nema 4-X stainless steel, required in the food processing industry. 
     Referring to FIG. 13, a method is schematically illustrated for conveying the product on the conveyor assembly either in a continuous drive with variable speed, or which may be operated to simulate a batch drive system. According to this feature, a friction drive ring  80  is caused to rotate at a speed slightly less than that of conveyor assembly  14 . The friction drive ring is rotated by a pair of friction drive ring trunion rollers  82  which rotate in the direction shown by arrows  84 . The friction drive ring trunion rollers may be controlled locally or remotely as desired. The friction ring  80 , in turn, slowly rotates in a direction shown by arrow  85  in driving contact with a plurality of conveyor drive wheels  86  (one wheel per conveyor  12 ). Each drive wheel  86  includes a pillow block gear assembly  88 , as shown, having a bevel gear  90 . Each bevel gear  90  mates with a corresponding bevel gear  92  located on each conveyor  12 . Turning the friction drive wheels  86  thus conveys the product (produce and the like) on the conveyors  12 . This method creates either a continuous drive with variable speed or may simulate a batch system, depending on the chosen rotational speed of the friction drive ring  80 . 
     FIG. 14 schematically illustrates another conveyor drive system suitable for the present invention to provide intermittent drive to the conveyors  12  . The drive ring  101 , similar to drive ring  80  in FIG. 13, may include individually actuated ring segments  102  that are actuated by small pneumatic cylinders or the like. Thus, the conveyors will move intermittently from the individually driven ring segments, as opposed to continuous drive motion from the rotation of a single drive ring. 
     Another means for accomplishing intermittent processing is shown in FIG. 15, which includes a spring loaded drive ring segment  104  that drives adjustable cones  106  that are part of the pillow block gear assembly  88 , discussed above. Here, though, there are no drive wheels. The spring loaded ring segment actuates the adjustable cone  106 , which in turn, provides intermittent drive to the bevel gear  90  on the pillow block gear assembly as the drum rotates. The gear  90  in turn, drives its corresponding bevel gear  92  located on each conveyor  12 . The ring segment is supported by means (not shown) such that, when different diameters of the drive cones engage it, it can give way and adjust to the diameter. The position of the cones may be manually adjusted along their mounting shafts to obtain different dwell times. This is done while the machine is not operating. The cones may also be mounted to slide on a spline shaft configuration and engage on a slide ring mechanism that would change their radial position, thus changing the diameter of engagement on the drive ring segment  104 . 
     Referring to FIGS.  16  and  17 A-C, a pair of of slide concentric rings  94  which remain stationary relative to the rotating drum  10  may be used as an alternate embodiment to the gimbal ring illustrated in FIGS. 7-8, for controlling the movement of conveyors  12 . With the gimbal ring configuration crank arms  56  extend approximately radially outward from the conveyor assembly  14 . With the concentric rings  94 , crank arm&#39;s  56  extend approximately axially from the conveyor assembly  14 . As the drum  10  rotates, the rocking/swinging motion of the crank arms  56  caused by contact with the slide rings  94  as depicted in FIGS. 17A and 17B, replicates the movement caused by the gimbal ring  50  of FIGS. 7-8 as previously described. As illustrated in FIG. 17C, the rings  94  may be mounted on a frame  93  carried by the shroud frame  72 . The brackets  95  serve to connect the inner and outer rings  94  together and to the frame  93 . The brackets  95  protrude out of the plane of the page to clear the crank arms  56  which ride between the rings as shown in FIGS. 17A and 17B. The rings to  94  may be coated with UHMW plastic or an equivalent substance as a bearing or anti-friction wear surface. The frame  93  may be mounted in suitable channels  97  constructed from UHMW plastic or equivalent low fricton material and is shifted in the direction shown by the arrows in FIG. 15C by means of a suitable linear actuator  99 . The actuator  99  may be a pneumatic, hydraulic, or electrical motor, mechanical screw or any equivalent thereof. The position of the slide rings  94 , of course, determine the duration of dwells in the step-wise conveyor movement. One advantage of the shiftable rings  94  is the reduced size and simplified structures. Also, the amplified movement of the conveyor crank arms due to the shingled angle of the rotating conveyors provides better control of the drive means. 
     The benefits of the present invention are numerous. The uncomplicated system of the present invention provides a high degree of reliability and is hygienic as well. The passive conveyance reduces product defect. The return belt path of the conveyors is designed to be a large diameter to create a higher centrifugal force that will help continuously clean the belt. The shingled orientation of the conveyors reduces product spillage and increases yield. The present invention is designed to handle capacity ranging from 2000-7000 pounds of leafy vegetables an hour. It will also be understood that the rollers or alternate drives may be controlled locally through traditional electro-mechanical controls or through remote programmable logic controllers. 
     Changing various criteria of the dryer can control the drying process. For example, a dwell time of 87 seconds and produce drying capacity of 3344 lbs./hr can be attained with the following specifications. 
     
       
         
               
               
               
               
             
               
               
               
             
           
               
                   
               
             
             
               
                 Centrifugal force calculation: 
                 Weight/area = 
                 4.8 
                 lbs./ 
               
               
                 calculate force on product 
                   
                   
                 sq ft 
               
               
                 over a One Square foot area 
                 Force Centrifugal/area = 
                 5 
                 lbs 
               
               
                 using the bulk density, 
                 Force Aerodynamic = 
                 1.06 
                 lbs. 
               
               
                 product depth and conveyor 
                 per each conveyor 
               
               
                 RPM. 
                 assembly 
               
               
                   
               
             
          
           
               
                   
                 Value 
                 Units 
               
               
                   
               
               
                 Spin Dryer Calculations 
               
               
                 Parameters to be entered: 
               
               
                 Product bulk density (wet) 
                 19 
                 lbs./cubic ft 
               
               
                 Product depth 
                 3 
                 in 
               
               
                 Conveyor Assy. Spin Dryer RPM 
                 35 
                 rev/min 
               
               
                 Conveyor Drive Sprocket Dia. 
                 8 
                 in 
               
               
                 Conveyor Belt Length 
                 8 
                 ft 
               
               
                 Conveyor Assy. Dia. 
                 60 
                 in 
               
               
                 Conveyor Belt Width 
                 24 
                 in 
               
               
                 Conveyor Quantity 
                 8 
                   
               
               
                 Gimbal Ring angle 
                 3 
                 Deg 
               
               
                 Drive motor RPM 60 Hz 
                 1750 
                 rpm 
               
               
                 Trunion offset distance 
                 8 
                 in 
               
               
                 Gimbal Ring clearance 
                 2 
                 in 
               
               
                 Trunion drive wheel diameter 
                 18 
                 in 
               
               
                 Trunion drive wheel angle off center 
                 30 
                 Deg. 
               
               
                 Conveyor belt weight per square ft. 
                 3 
                 lbs 
               
               
                 Conveyor rail friction factor 
                 0.18 
                 Uf 
               
               
                 Bearing rolling friction 
                 0.01 
                 Uf 
               
               
                 Coefficient of Drag 
                 2 
                 Cd 
               
               
                 Air Density 
                 0.0764 
                 lbm/cubic ft 
               
               
                 Estimated conveyor assy weight 
                 130 
                 lbs 
               
               
                 Calculated Values: 
               
               
                 Conveyor Assembly Rotational Surface Speed 
                 550 
                 ft/Min 
               
               
                 Conveyor Assembly Rotational Surface Speed 
                 6.25 
                 mph 
               
               
                 Conveyor Drive sprocket rpm 
                 2.6 
                 rpm 
               
               
                 Crank arm length relative to sprocket 
                 9 
                 in 
               
               
                 diameter + 5 in 
               
               
                 Crank arm angle 
                 13.45 
                 Deg 
               
               
                 Gimbal Ring Diameter 
                 80 
                 in 
               
               
                 Conveyor Linear Belt Speed 
                 5.5 
                 ft/Min 
               
               
                 Conveyor Belt Surface Area 
                 128 
                 sq. ft. 
               
               
                 Product Weight (Total) in Spin Dryer 
                 614 
                 lbs 
               
               
                 Product Dwell Time 
                 87 
                 sec. 
               
               
                 Capacity 
                 3344 
                 lbs./hr 
               
               
                 Calculate  values for Gear Box ratios and HP&#39;s 
               
               
                 Trunion diameter for calculating trunion drive 
                 76 
                 in 
               
               
                 wheel speed 
               
               
                 Trunion drive wheel rpm 
                 148 
                 rpm 
               
               
                 Gearbox ratio (Drive) 
                 0.08:1 
                 ratio 
               
               
                 Weight of conveyor assemblies, 
                 2038 
                 lbs. 
               
               
                 belt and product 
               
               
                 Horsepower req&#39;d to convey product 
                 0.25 
                 HP 
               
               
                 Horsepower req&#39;d to rotate conveyor 
                 0.5 
                 HP 
               
               
                 assemblies (friction) 
               
               
                 Horsepower req&#39;d to rotate conveyor 
                 0.14 
                 HP 
               
               
                 assemblies (air resist) 
               
               
                 Total Horsepower with 80% efficiency 
                 1.07 
                 HP 
               
               
                   
               
             
          
         
       
     
     The descriptions above and the accompanying drawings should be interpreted in the illustrative and not the limited sense. While the invention has been disclosed in connection with the preferred embodiment or embodiments thereof, it should be understood that there may be other embodiments which fall within the scope of the invention as defined by the following claims.