Sorting conveyor

Abstract: A tray conveyor system (10) for receiving and dispensing products comprising: closed loop track means (41) for supporting and guiding the tray conveyor system; a closed loop tray conveyor assembly comprised of a plurality of individual tilt tray carrier means (20) each being coupled to the adjacent carrier means respectively located downstream and upstream of each carrier means whereby each carrier means comprises a "link" in a closed loop "chain"; each of said carrier means comprising roller means (25,27), said track means including guide means (41a-c,42a-c) receiving said roller means for guiding each of said carrier means along a closed loop track means; each of said carrier means including frame means (21) and a tilt tray (23) swingably mounted thereto; the bottom surface of each frame means being provided with a conductive metallic member (26a-b); linear electric motor means (LIM) mounted on said track means adjacent to said metallic member in such a manner as to provide a small air gap between said linear electric motor means and said metallic plate; said linear electric motor means being energizable to create an electromagnetic field for creating eddy currents in said metallic member to develop a thrust sufficient for moving all of said carrier means in a predetermined direction along said track means whereby substantially continuous propulsion of said tray conveyor is obtained as the metallic members of each of said carrier means passes said linear electric motor means.

Description: Field of the Invention The present invention relates to a tray conveyor system according to the preamble of claim 1. Background of the Invention Such a system is known from FR-A- 2044502. Tray conveyors have been utilized for conveying products from a delivery location to one of a plurality of output locations. It is also conventional to provide a closed loop conveyor comprised of a plurality of tiltable carriers, each being capable of receiving and supporting a product deposited thereon at a receiving location. As the tilt tray moves past an outfeed location, activating means cause the tray to tilt in the proper direction so as to dispense the product being carried thereon down upon a delivery chute. Present day systems employ massive complicated tilting mechanisms and further utilize drive mechanisms requiring a large number of moving parts which undergo significant wearing. It is thus highly desirable to provide a simple, highly reliable conveyor system. Brief Description of the Invention The system according to the present invention is characterized by the features of the caracterising portion of claim 1. A novel closed loop conveyor comprised of tilt tray carts coupled in tandem fashion in which the drive means has no moving parts and further in which the tilting mechanism provides reliable tilting and resetting thereof at speeds sufficient to assure dispensing of an object during the short dispensing "window" is provided, representing a distribution system comprised of a conveyor system of tiltable trays capable of delivering 175 bundles per minute at a modest speed of the order of only 99 meters per minute. The conveyor system is comprised of a plurality of tilt tray carriers connected in tandem fashion in a continuous loop, each tray carrier being constructed so that it serves as a "link" in a "chain" of tray carriers. Each tray carrier is provided with horizontal and vertical wheels which rollingly engage associated horizontal and vertical guides forming part of a track for precisely following the path of said track. The tray carriers are capable of navigating horizontal curves as small as 1,85 meters in radius, vertical curves of 3 meters radius and inclination angles of up to 30°. The drive system is unique in that it eliminates the use of any gear heads or sprockets and, in fact, there is no physical connection whatsoever between the drive and the tray conveyor. This is accomplished through the use of linear induction motors (LIMs), one component (stator) of the motor being secured to the conveyor support structure while the trays themselves serve as the cooperating movable component of the linear induction motor. A distributed drive system comprised of LIMs arranged at spaced intervals along the closed loop path of the track assures that there is never excessive force introduced on the conveyor at any point to provide smooth speed performance while allowing continued conveyor operation even in the event of the loss of any individual drive during use. Bundles are preferably loaded upon each tray by a novel overhead loader capable of delivering up to thirty bundles per minute to the conveyor. Empty trays are sensed as they approach the loading device and a bundle delivered to the loading device is dropped upon the desired tray by means of a high speed pusher driven by a servo-motor. The overhead loader accepts bundles from a source delivered to the overhead loader conveyor. A gate limits movement of the delivered bundle and thereby aligns the bundle in readiness for being dispensed. The overhead loader is tilted at an angle to compensate for the tilt in a bundle as it leaves the overhead loader conveyor to assure that each bundle drops squarely upon the desired tray. Bundles are discharged from a carrier by means of a tilt top which undergoes tilt motion as the tray approaches a discharge chute. The tilt mechanism includes a pair of cam follower wheels, at least one of which rollingly engages a cylinder (or solenoid) operated tilt cam causing a nesting cup of a swingable plate to be initially rotated away from a cooperating locking pin against the force of a torsion spring and thereafter causing the unlocked tray to tilt in the proper direction. Restoring cams respectively engage each of the tilt mechanism cam follower rollers to restore the tilt tray to the upright position and to prevent overshooting after delivery of a bundle. Each tray carrier is provided with only a single vertical wheel and two horizontal wheels arranged at the rearward end of each tray carrier for guiding the carrier along the track, the vertical and horizontal wheels of the upstream carrier serving to provide each carrier with guidance at both the forward and rearward ends. The bundles are tracked by an electronic tracking technique in which a tag is provided on a master cart which is sensed and which initiates a cart identification procedure. Thereafter, a proximity sensor identifies the passage of each successive cart thereby locating carts as to their position from the master cart. Optional bar code tracking can be utilized, if desired. Speed control for the system is comprised of a speed sensor utilizing multiple free-wheeling rollers which rollingly engage the bottom surfaces of the carts and are coupled to a sensor for generating pulses representative of conveyor speed. The use of plural interconnected sensor rollers assures that at least two rollers are in engagement with a cart at all times. The feedback information is utilized by a microprocessor based computer, for example, to maintain system speed to an accuracy of within plus or minus five percent ( ± 5 %) tolerance relative to the desired speed, to assure proper loading and unloading of bundles from the conveyor. Objects of the Invention It is, therefore, one object of the invention to provide a novel tilt tray conveyor system for product conveyors having a tilt tray mechanism which is initially moved to the unlatched position and thereafter moved to the tilted position responsive to engagement by a selectively operated reciprocating tilting cam. Still another object of the present invention is to provide a novel tilt tray conveyor system for product conveyors and the like in which the supporting wheels of an adjacent tilt tray carrier cooperating with the supporting wheels of the next succeeding tilt tray carrier to provide proper wheel support for each tray carrier, front and rear. Still another object of the present invention is to provide a novel tilt tray system for product conveyors and the like utilizing a novel drive system in which each tray carrier comprises an integral element of the motor drive. Still another object of the present invention is to provide a novel tilt tray for product conveyors and the like having a sturdy low profile tilt tray assembly. Still another object of the present invention is to provide a novel tilt tray system for product conveyors and the like utilizing linear induction motors in a unique manner for propulsion and hence movement of the conveyor. Still another object of the present invention is to provide novel feedback control means for rollingly engaging the undersurface of each tray assembly to provide a speed indicating signal, the rolling engagement means being designed to assure positive engagement with the bottom surface of at least two of said tray carriers at all times. Brief Description of the Figures The above, as well as other objects of the present invention will become apparent when reading the accompanying description and drawing in which: Fig. 1 shows a perspective view of a system employing the product conveyor of the present invention ; Fig. 2a and 2b show side and end views respectively of a tray assembly according to the present invention ; Fig. 2c shows the tray assembly of Fig. 2b in the titled position; Fig. 2d shows a detailed top view of the tilt assembly shown in Figs. 2a-2c; Figs. 3a-3d respectively show side elevation, front elevation, rear elevation and top plan views of the cart frame of Figs. 2a-2c; Figs. 4a-4c respectively show top, side elevation and front views respectively of the tip frame of Figs. 2a-2c ; Figs. 5a and 5b respectively show side elevation and top views of the latch block employed in the tilting assembly of Figs. 2a-2c ; Fig. 6 shows a plan view of the latch plate forming part of the tilting assembly of Figs. 2a-2c ; Figs. 7a and 7b respectively show side elevation and top plan views of the tip am assembly; Fig. 7c shows the manner in which the tip cam assembly of Figs. 7a and 7b performs a tilting operation upon a tilt tray assembly ; Figs. 8a and 8b respectively show side elevation and top plan views of a straightening cam ; Fig. 8c shows the manner in which two straightening cams are arranged to align a tilt tray assembly in the upright position ; Fig. 9 shows a block diagram of the speed control system employed in the present invention ; Figs. 9a and 9b respectively show top plan and end elevation views of the sensor assembly employed in Fig. 9, Fig. 9a being a sectional view of the assembly of Fig. 9b looking in a direction of arrows A-A ; Figs. 9c-9e are sectional views respectively looking in the direction of arrows B-B (Fig. 9a), C-C (Fig. 9a) and D-D (Fig. 9b) ; Fig. 9f shows a schematic view of the manner in which the encoder of Figs. 9-9e cooperates with the tilt tray assembly for monitoring the conveyor velocity ; Detailed Description of the Invention Fig. 1 shows an application in which the system 10 of the present invention may be used to great advantage. For example, the integrated arrangement may be comprised of conveyors 11 for delivering signatures from a press to a plurality of signature stackers 12 for stacking the incoming signatures into signature bundles 13 which may be of the compensated or uncompensated type. Each stacker 12 transfers a completed bundle 13 to an outfeed conveyor 14 for delivery to a tying station 15. Each tied bundle 13a is transfered from the tying station to a conveyor 16 for delivering each completed bundle to an overhead loader 17. Each of the overhead loaders, also referred to as top loaders, is controlled by a computer to precisely drop a completed bundle into the desired tray assembly 20 as it passes beneath the proper overhead loader. The loader conveyor may be used to bypass the overhead load and deliver a bundle to a bypass conveyor as an alternative delivery path to a truck, loading dock or other location. Each of the tray assemblies 20 is pivotally linked to the adjacent upstream and dowstream tray assembly to provide a closed loop product conveyor arrangement wherein each tray assembly serves as a "link" within an elongated, closed loop conveyor "chain" which is continuously recirculated about the loop by linear electric motors arranged at spaced intervals about the loop with the path of the loop being defined by a closed loop track 40 which is arranged to traverse a particular region and to substantially accomodate the contours and configuration of the region. For example, in the network 10 shown in Fig. 1, the application provided therein is to deliver predetermined bundles to a predetermined one of the delivery trucks 50 under control of a computer system. In order to provide a gravity feed arrangement, the track is provided with an inclined portion 40a to lift the trays and hence the bundles carried thereby to an elevation sufficient to feed a bundle to the desired truck by means of gravity. By computer control, a pneumatic ejector tilts the proper tray assembly, such as, for example, the tray assembly 20' causing the bundle 13b to the dispensed from tray assembly 20' and fall downwardly by gravity along an outfeed chute 60 and thereafter along an outfeed conveyor 62 for delivery directly to the desired truck 50 positioned at the loading dock in alignment with the outfeed conveyor 62. As will be more fully described, a pair of straightening cams are utilized to return the tilt tray to the upright position preparatory to being returned to the bundle receiving portion of the conveyor "chain" whereby the tray may be loaded with a bundle from any of the overhead loaders, all under control of the computer system for controlling the loading and unloading operations. Figs. 2a-2d show a typical tilt tray assembly 20 and the manner in which it is guided by the guide track 40. As shown best in Figs. 2b and 2c, the guide track is comprised of track portions 41 and 42 which are joined to suitable supporting elements (not shown for purposes of simplicity) so that the flanges 41a, 42a cooperate to provide a guide for the vertical roller 27 of the tilt tray assembly which cooperates with the guide flanges 41a and 42a to limit the lateral movement of the tray assembly as it moves along the track. Upper and lower portions 41b, 41c and 42b, 42c of track portions 41 and 42 form guides for the horizontal rollers 25, 25 of the tilt tray assembly to limit movement of the tilt tray assembly in a direction transverse to the horizontal. As can be appreciated from Fig. 1, the track may be comprised of a plurality of straight portions, curved portions, inclined and downwardly sloping portions of both the straight and curved type, the design of the tilt tray assemblies enabling the conveyor to navigate around horizontal curves as small as 1,85 meters in radius, vertical curves as small as 3 meters in radius, and inclination angles of up to 30°. The track sections are preferably formed of a suitable metallic material to provide a rugged and highly serviceable track. Each title tray assembly 20 is comprised of a one-piece frame 21 shown in detail in Figs. 3a-3d and comprised of a base portion 21c provided with forward and rearward uprights 21b, 21a having openings whose centerlines are horizontally aligned for supporting a shaft 22 for swingably mounting the tilt tray 23. Tilt tray 23 is comprised of a substantially flat base portion 23a having integral forward and rearward sides 23b, 23c which form an angle slightly greater than 90° with base portion 23a. Left and right-hand sides 23d, 23e form an angle of just slightly less than 180° with base portion 23a. Forward and reaward sides 23b, 23c serve to retain a bundle therebetween to a much greater degree than sides 23d and 23e which are designed to facilitate the dispensing of a bundle when the tilt tray is tilted from the upright position shown in Fig. 2b to the tilted position shown in Fig. 2c, to facilitate the delivery of a bundle at an outfeed chute location 60, shown for example, in Fig. 1. The forward end of frame 21 extends forwardly beyond upright 21b and is provided with a threaded opening 21d for receiving a ball and socket assembly comprised of threaded member 24 having a circular "socket" portion 24a for rotatably supporting the ball member 24b having an opening 24c adapted to receive a pin provided at the rearward end of the tilt tray assembly positioned immediately in front of tilt tray assembly 20 shown, for example, in Fig. a. This pin is shown, for example, as pin P arranged within the vertically aligned opening 21e provided in the portion of frame 21 extending rearwardly of rear upright 21a (see Fig. 5, 2b and 3a). The central portion of opening 21e in the frame is enlarged as shown at 21f to receive the ball and socket assembly of the titlt tray assembly arranged immediately behind tilt tray assembly 20 shown in Fig. 2a, for example. The rearward end of frame 21 is further provided with horizontally aligned threaded openings 21g, 21h which receive and threadedly engage the threaded portions of a pair of axle pins 25b, 25b which serve to rotatably mount the wheels 25,25 which rotate about the wheel bearings 25a, 25a. The bottom surface 21i of frame 21 is provided with a cold rolled steel plate 26a and an aluminum plate 26b respectively laminated to the bottom surface thereof and cooperating with the linear motor LIM (to be more fully described) to set up the proper eddy current paths for propelling the tilt tray assembly. As was mentioned hereinabove, vertical pin P, in addition to extending through the hollow opening 24c in ball member 24, further rollingly supports vertical wheel 27 having bearings 27a for rotation about the pin P. The tilt assembly TA is comprised of a threaded locking pin 28 threadedly engaging tapped opening 21j in frame 21. A tip frame 29 shown in Figs. 4a, 4b and 4c is a substantially rectangular-shaped frame having openings 29a, 29b for receiving and being swingably mounted upon shaft 22 which is rigidly secured to uprights 21b, 21c by fasteners F, F. Tip frame 29 is provided with tapped openings 29c for threadedly receiving suitable fasteners to secure tray 23 thereto. Frame 29 has a pair of projections 29d, 29e which extend rearwardly and are positioned on opposite sides of the frame upright 21a. A latch block 30 forming part of the tilt assembly and shown in detail in Figs. 5a and 5b is comprised of latch block lower and upper halves 30a, 30b secured to one another by means of fasteners F1 extending through openings 30b-1 in upper block 30b and threadedly engaging one of the tapped openings 30a-1 in lower block portion 30a. The blocks are machined or otherwise formed with semi-circular portions so that when they are joined together in the manner shown, for example, in Figs. 2a and 5a, they define openings O1 and O2. Opening O1 is coincident with the openings 29d-1, 29e-1 in rearward projections 29d and 29e of tip frame 29. The central axes of these openings serve as a pivot axis for the latch block 30 and latch plate 32. Larger opening O2 is substantially aligned with the elongated openings 29d-2, 29e-2 provided in rearward projections 29d and 29e of tip frame 29. Elongated shaft 31 extends through openings O2, 29d-2 and 29e-2 as shown best, for example, in Figs. 2a-2e. Cam follower rollers 31a, 31b are rotatably mounted at the opposite ends of shaft 31. The intermediate portion of shaft 31 extends through opening O2 and is tightly clamped between the latch block halves 30a and 30b. Resilient O-rings 31c prevent metal-to-metal contact between shaft 31 and the interior surfaces of the elongated openings 29d-2 and 29e-2. A latch plate 32 having a substantially semi-circular-shaped slot 32a for embracing locking pin 28, is provided with a pair of tapped openings 32b, 32c for threadedly engaging fasteners F2 for securing latch plate 32 to the lower half 30a of latch block 30. A shaft 34 extends through opening O1 in latch block 30 and openings 29d-1 and 29e-1 in tip frame 29. The latch block halves are clamped together to rigidity secure the latch block to shaft 34 which is free to rotate within the openings 29d-1, 29e-1 by suitable bearings 34a, 34b. At least one torsion spring 35 is wrapped about shaft 34 near roller 31b. If desired, a second torsion spring may be provided adjacent the roller 31a. The spring is preferably wrapped about two (2) to four (4) turns shaft 34. One end of torsion spring 35 rests against the lower rear edge of tray 23 and the other end rests against an adjacent portion of shaft 31, the torsion spring normally urging the tilt assembly in the counterclockwise direction about shaft 34 relatives to Fig. 2a so as to normally urge and position latch plate 32 against the rearward surface of upright 21c in the manner shown in Fig. 2a in order to embrace locking pin 28. The torsion spring 35 also further serves to normally orient the tip frame 29 and tray 23 in the upright position, especially when two such springs are provided. When one of the rollers, such as for example, the right-hand cam follower roller 31a is urged upwardly from the position shown in Fig. 2b toward the position shown in Fig. 2c by an opening cam surface C shown in dotted fashion in Fig. 2c, the initial upward movement of the cam follower roller 31a causes latch block 32 to rotate clockwise (relative to Fig. 2a) about pivot pin 34, moving latch plate 32 away from latch pin 28. As soon as the latch plate cup 32a clears latch pin 28, the tip frame and tray are free to tilt about mounting shaft 30, moving the tip frame 29, tilting assembly 27 and tray 23 counterclockwise about shaft 30 (relative to Fig. 2b) to move the tip frame and tray from the position shown in Fig. 2b to the position shown in Fig. 2c is sufficient to cause a bundle riding therein, such as a signature bundle, to be dispensed therefrom. The angle of the tray, together with the rapid movement of the tip frame and tray from the position shown in Fig. 2b to the position shown in Fig. 2c, cooperate to drop the signature bundle carried thereon to an outfeed chute, such as, for example, any of the chutes 60 shown in Figs. 1. As an alternative arrangement, there may be a reversal of parts whereby latch plate 32 may be provided with a pin, and upright frame 21a may be provided with an opening for receiving the pin, said reversal of parts providing substantially the same operation as the arrangement shown, for example, in Figs. 2a. As will be described more fully hereinbelow, a pair of restoring or straightening cams, arranged on opposite sides of the centerlines of movement of the tilt tray assemblies engageable by the cam follower rollers 31a, 31b, cause the tilt tray to be moved to and retained in the upright position. The use of a pair of restoring cams, in addition to restoring the tilt tray to its upright position, prevents overshooting of the tilt tray from the tilted position to a position beyond the upright position. Upon return to the upright position, the latch plate cup 32a moves into aligment with latch pin 28 causing the cup to embrace the latch pin under the force of torsion spring 35 and causing the latch plate to be urged against the rear surface of upright 21c to return the tipping assembly to the latched position. The tray assembly will remain in the upright position indefinitely and until tipped therefrom by a tipping cam. As shown in Fig. 2a, a linear electric motor having a length and width which is substantially equal to the length and width of the bottom surface of frame 21, is secured to the guide track frame, in the region between flanges 41f and 42f as shown best in Fig. 2b and is spaced a very small distance away from the bottom surface of the laminated plates arranged upon the bottom surface of frame 21. The linear electric motor, which may be of the single-sided type produced by Northern Magnetics, Inc. of Van Nuys, California, is preferably a three-phase linear motor spaced from the bottom surface of plate 27 to provide an air gap of the order of 2,30 centimeters. The three phase linear motor sets up electromagnetic fields which create eddy currents in the laminated plates secured to the bottom of frame 21 developing a thrust which causes the tray assembly to move in the forward direction as shown by arrow A in Fig. 2a. The thrust of the motor is sufficient to propel the tray assemblies by providing LIMs at regularly spaced intervals about the closed loop path. For example, employing the LIMs of the type described hereinabove, a plurality of such LIMs spaced a distance of the order of 17 meters intervals have been found to be more than adequate to provide the desired operating speed, which in one preferred embodiment is of the order of 6 kilometers per hour having the capability of delivering a 175 bundles per minute at the aforementioned operating speed. The actual spacing, however, is a function of the inclines, curves and other path shapes as well as the bundle weight and may vary dependant upon these factors. The linear motor is further provided with blower means B for maintaining the linear motor at a desired operating temperature, as is conventional. The tray assemblies are conveyed about the closed loop track without any direct mechanical connection whatsoever between the drive motors (LIMs) and the tray assemblies. Fig. 9 shows a simplified view of the manner in which the operating speed is controlled, as will be more fully described. The Figs. 7a-7c show the tip am assembly referred to hereinabove, for tilting the tiltable tray assembly. The tip cam assembly 70 is comprised of an L bracket 71 for mounting the tip cam assembly to one of the guide tracks and, as shown in Fig. 7c, specifically guide track 41. Fasteners F3 secure the vertical arm of bracket 71 to one vertical side of track 41 while the horizontal arm of L bracket 71 is secured to the horizontal surface 41b of track member 41 by fasteners F4. The tip cam assembly is further comprised of a ramp member 72 secured to the horizontal arm or bracket 71 by fasteners F5 and having an inclined cam surface 72c. The pivot ramp is further provided with a pair of bifurcated arms 72a, 72b each provided with an opening for receiving a mounting pin 73 extending through an opening in elongated tip cam 73 whose opening is provided in a downwardly depending forward portion 73b. Tip cam 73 is coupled to a pair of links 74, 74 by means of pin 75. The opposite ends of the links 74, 74 are coupled to pin 76 which extends through a pair of slider yokes 77, 77. A pair of slider blocks 78, 78 are slidably arranged within the elongated slots 77a, 77a of the associated slider yokes 77, 77. The tip cylinder 79 is secured to a mounting block 80 by means of pin 81 which is coupled to the clevis 79a provided at the right-hand end of cylinder 79. Mounting block 80 is secured to the horizontal portion of mounting bracket 71 by fasteners F7. The cylinder piston 79b extends outwardly from the cylinder and to the left and is provided with a mounting eyelet 79c having an opening for receiving pin 76. Cylinder 79 is a pneumatic cylinder provided with control ports 79d, 79e. Assuming the tip cam assembly to be in the off condition with tip cam 73 in the solid line position, and assuming that the next tilt tray assembly is to be tilted, pneumatic pressure is applied to port 79e driving piston 79b to the left. This movement is imparted to the links 74, 74 which lift tip cam 73 from the solid line position to the phantom line position 73'. Phantom circles 31a, 31a', 31a'' show the progress of the tip cam follower roller 31a. The ramp surface 72c provided along ramp member 72 assures gradual movement of a roller onto the cam surface of the tip cam in the event that there is any misalignment of the cam follower rollers to prevent the cam follower rollers and hence the tip cam assembly from experiencing any sudden jolt or impact as a cam follower roller moves, approaches and engages the tip cam assembly. The tip cam assembly may be rapidly reset by applying pneumatic pressure to port 79d to thereby abruptly move the tip cam from the phantom line position 73' to the solid line position 73 in order to prevent the tilting of a tilt tray assembly which is not intended to be unloaded at the output chute location. Tip cam assemblies of the type shown as assembly 70 in Figs. 7a-7c are provided at a location slightly upstream relative to each output chute 60 in order to selectively tilt the desired tilt tray assembly. It should be noted that each tilt tray assembly is capable of being tilted either in the clockwise direction or in the counterclockwise direction (relative to Fig. 7c, for example) and further that the output chutes may be placed on either side of the closed loop track enabling unloading of a signature bundle to an outfeed location on either side of the closed loop track. Thus, by placing a tip cam assembly on the opposite side of the track assembly, i. e. by mounting a tip cam assembly to the track portion 42 shown in Fig. 7c, the tilt tray may be tilted in the clockwise direction relative to Fig. 7c, the side upon which the dispensing of bundles is to take place being dependant only upon the needs of the user. Figs. 8a-8c show the tray straightener cam assembies 90, 90, there being a tray straightener cam assembly mounted to each track half 41, 42 as shown in Fig. 8c. Since the tray straightener cam assemblies are substantially identical and are actually symmetrical to one another, these assemblies have been identified by like numerals. Each assembly is comprised of an L-shaped mounting bracket 91 whose vertical arm is secured to an associated one of the track portions by fasteners F1 while the horizontal arm is coupled to one of the track sections by fasteners F2. A straightener cam 92 is provided with a ramp portion 92a which slopes upwardly in the direction of movement of the tip cam follower roller 31a and, after reaching a peak at 92b, has a downward sloping portion 92c. A cam mount 93 cooperates with cam 92 for positioning a slidable cam 94. Cam mount 93 has a tapered portion 93a which can be seen to be coplanar with an upper portion of the sloping portion 92a of cam 92. At a peak 93b which is in aligment with the peak 92b of cam 92, cam mount 93 has a downwardly sloping portion 93c which is coplanar with the downwardly sloping portion 92c of cam 92. Adjustable cam member 94 is provided with a pair of elongated slots 94a, 94b through which the fasteners F2 and F3 extend, fasteners F2 and F3 being threaded at their free ends to threadedly engage tapped apertures 92d, 92e in cam member 92. Adjustable cam 94 has an upwardly sloping surface portion 94c and a downwardly sloping portion 94d, these portions being substantially coplanar with the upwardly sloping portions 92a, 93a, and the downwardly sloping portions 92c, 93c. Adjustable cam 94 is slidable either downwardly and to the left or upwardly and to the right to extend the upward sloping portion in order to adjust the tray straightener assemblies to compensate for any deviations from the normal spacings between the cam follower rollers and the cam straightener assemblies. Noting Fig. 8c, a pair of cam straightener assemblies are provided for cooperation with each cam follower roller 31a, 31b regardless of the direction in which the tray is tilted for the reason that the provision of two cam straighteners each cooperating with the associated cam follower rollers prevents the tilting assembly from overshooting the desired uprigh position, regardless of the direction in which the tray has been tilted. The tray straightener cam assemblies are mounted just downstream from each output chute in order to straighten each tilt tray assembly as it passes the tray straightener cam assembly. As was mentioned hereinabove, the linear motors are controlled to accurately regulate the speed of the tilt tray assemblies in order to accurately dispense bundles from each of the outlet chute locations, as well as being capable of operating the loader which loads bundles onto the tilt tray assemblies, the operation of the loaders also being dependent upon accurate control of the speed of the tilt tray assemblies. The manner in which the desired control is obtained is by way of a feedback arrangement shown in Fig. 9 comprised of a controller 100 for controlling the current to each of the LIMs. A speed setting input 100a receives the desired speed. For example, a touch screen may be employed for imputting the desired speed and for displaying the desired speed which has been inputted. Controller 100 is coupled to encoder 104 which provides a feedback signal of the conveyor speed which is continuously compared against the set speed for regulating the amplitude of the three-phase current applied to each of the linear motors 102. Encoder 104 is comprised of an encoder assembly shown best in Figs. 9a-9f and includes a substantially U-shaped encoder support 106 coupled to the downwardly depending flange portions of the track sections 42 and 41 shown best in Fig. 9b. A pair of plates 108, 110 are secured together in spaced parallel fashion by means of spacers 109 arranged between the plates and set within shallow circular recesses provided in the plates as shown in the vicinity of the uppermost spacer 109' shown in Fig. 9a. The spacers are secured to plates 108 and 110 by fasteners F1. Three tires 111, which are substantially identical to one another, are mounted to rotate upon shafts 112 journaled within bearings arranged within the plates 108 and 110. Each tire 111 has an integral gear member 111a while the uppermost tires 111' are further provided with left-hand integral gear members 111b. An encoder 113 is fixedly secured to left-hand plate 108 by fasteners F2. Encoder 113 is provided with a similar gear or sprocket 113a extending to the right of the encoder housing. The shaft upon which the sprocket is mounted extends through a clearance opening 108a provided in plate 108. Encoder 113 is designed to provide an electrical signal representative of the rotational speed developed by the encoder shaft 113b which is coupled to the right-hand gears 111a by means of a common timing belt 114 shown in dotted fashion. The tire assemblies 111' also have their left-hand gears coupled in common by a single timing belt 115. Three shafts 116a, 116b, 116c shown in dotted fashion in Fig. 9a and shown in solid line fashion in Figs. 9b through 9e, extend through cooperating openings, such as, for example, the openings 108b, 110b provided in plates 108 and 110. Clamp collars 117 orient plates 108 and 110 relative to the shafts 116a, 116c, each clamp collar further including a threaded fastener 117a as shown in Fig. 9d for rigidly securing each clamp collar to its associated shaft and for further clamping plates 108 and 110 between each associated pair of clamp collars. Each of the shafts 116a-116c have their left and right-hand ends extending through elongated slots 106a, 106b provided in the vertical sides of support 106. Clamp collars 117' fixedly secure the shafts against movement in the direction of their longitudinal axis while at the same time permitting each of the shafts to move vertically up or down within the elongated slots. Note, for example, slot 106b shown in Fig. 9e. A plurality of mounting pin assemblies 118 are secured to the right-hand vertical side of support 106 and each of said assemblies, at their free ends support the upper end 119a of a helical spring 119 whose lower end 119b embraces an associated one of said shafts 116a-116c. A plurality of somewhat similar pin assemblies 120 are fixedly secured to the left-hand vertical side of support 106 and, in a similar fashion, each supports the upper end 121a of a helical spring 121 whose lower end 121b is wrapped about the left-hand end of an associated one of the shafts 116a-116c. Each of the shafts is preferably provided with an annular groove for receiving and retaining the lower ends 119b, 121b of the helical springs 119, 121 respectively. The resiliently mounted tire assembly is adjusted so that the surfaces of the tires 111 and 111' engage the bottom surfaces of the tilt tray assemblies as they pass over the sensor assembly 104 with the resiliency of the springs being adjusted so that the wheels are urged against the bottom surfaces of the frames with a force of the order 900 to 1800 grammes. The spring supporting pins 118 and 120 are mounted within elongated slots in the vertical sidewalls of support 106, such as, for example, elongated slot 106c provided in the right-hand vertical side of the support 106 and are adjustable to adjust the spring force. Figs 9f shows the manner of operation of the encoder assembly. As was mentioned hereinabove, all three tires are tied together with at least one timing belt and in operation, the tires 111 and 111' are positioned in such a manner that two of the three tires are always in rolling engagement with one of the tilt tray assemblies. The tires are further always maintained in rotation since even a tire moving into the gap G between adjacent tilt tray assemblies 20 will not be free wheeling due to the fact that it is rotated by the timing belt of the remaining two tires which make rolling engagement with the passing tilt tray assemblies 20. Thus, the encoder assembly provides an accurate indication of the operating speed enabling the controller to dynamically adjust for any changes in operating speed by altering the driving signal applied to the linear motors 102. All of the linear motors are coupled in electrical parallel and the nature of the system is such that even the failure of one or two of the linear motors will not require shutdown of the system. A latitude of modification, change and substitution is intended in the foregoing disclosure, and in some instances, some features of the invention will be employed without a corresponding use of other features. Accordingly, it is appropriate that the appended claims be construed broadly and in a manner consistent with the spirit and scope of the invention herein described.

Claims: A tray conveyor system (10) for receiving and dispensing products comprising closed loop track means (41) supporting and guiding the tray conveyor assembly, a closed loop tray conveyor assembly comprised of a plurality of individual tilt tray carrier means (20) each being coupled to the adjacent carrier means respectively located downstream and upstream of each carrier means whereby each carrier means comprises a "link" in a closed loop "chain"; each of said carrier means comprising roller means (25, 27), said track means including guide means (41b, 41c, 42b, 42c, 41a, 42a) receiving said roller means for guiding each of said carrier means along the closed loop track means (Fig. 1), each of said carrier means including frame means (21) and a tray (23) moveably mounted thereto ; the bottom surface (21c) of each carrier means being provided with a conductive metallic member (26a, 26b) ; linear electric motor means (LIM) mounted on said track means adjacent to said metallic member in such a manner as to provide a small air gap between said linear electric motor means and said metallic plate ; said linear electric motor means being energizable to create an electromagnetic field for creating eddy currents in said metallic member to develop a thrust sufficient for moving all of said carrier means in a predetermined direction along said track means whereby substantially continuous propulsion of said tray conveyor is obtained as the metallic members of each of said carrier means passes said linear electric motor means characterised in that the tray (23) is swingably and tiltably mounted to the frame means (21) and in that the conductive metallic member (26a, 26b) is attached to the bottom surface (21c) of the frame. A tray conveyor system according to Claim 1, wherein said tilt tray carrier means further comprising : tilting means (27) coupled to said tilt tray ; locking pin means (28) ; said tilting means being tiltable about first and second mutually perpendicular axes ; bias means (35) normally urging said tilting means in a first direction about said first axis for engaging said locking pin means ; said tilting means further comprising a tilt bar (31) having a cam follower roller means (31a, 31b) mounted thereon ; tip cam means (70) arranged along said track means and having a tip cam member (73) swingable between a first position displaced from said cam follower roller means and a second inclined position (73') which is adapted to cause said cam follower roller means to move along the inclined surface of said tip cam member for tilting said tray means. The apparatus of Claim 1 wherein said metallic member is comprised of a pair of laminated metallic plates (26a, 26b) : each plate having a substantially rectangular configuration of a predetermined length and width ; said linear electric motor means (LIM) being of substantially the same shape and size as said plate ; said track means further comprising first and second elongated track portions (41, 42) arranged a spaced distance apart to thereby provide a predetermined gap therebetween ; said linear electric motor means being arranged within said gap and being secured to said track portions ; said roller means (25, 27) aligning said plates with said gap ; and said linear electric motor means being positioned immediately beneath said plate and at a distance from said plate means to provide a predetermined substantially uniform air gap between said plate and said linear electric motor means. The apparatus of Claim 3 wherein said laminated plates comprise a first steel plate (26a) secured to the undersurface of said frame means and an aluminium plate (26b) secured to said steel plate. The apparatus of Claim 4 wherein the thisknesses of said plates are of the order of 0,305 to 0,33 cm. The apparatus of Claim 1 wherein said linear electric motor means comprises a plurality of linear electric motors (102) arranged at spaced intervals along said tracks means ; power means for energizing said linear electric motors ; and said linear electric motors being connected in electrical parallel to said power means. The apparatus of Claim 6 wherein said power means comprises a three-phase alternating current power source. The apparatus of Claim 1 further comprising control means (100) for adjusting power to said linear electric motors for controlling the speed of said conveyor system. The apparatus of Claim 8 further comprising adjustable speed control setting means (100a), said control means being responsive to said speed control setting means for adjusting the signal applied to said linear electric motors responsive to the setting of said speed control setting means. The apparatus of Claim 9 further comprising feedback means (104) for monitoring the speed of said tray conveyor system for generating an electrical feedback signal representing conveyor speed ; said controller means (100) comparing said feedback signal with said speed setting signal for controlling the linear electric motors to maintain the speed determined by said speed setting means ; said feedback means comprising speed monitoring means (104) rollingly engaging said carrier means ; and conveyor means coupled to said speed monitoring means for converting the rotation of said speed monitoring means into an electrical signal representative of conveyor speed. The apparatus of Claim 10 wherein speed monitoring means comprises a plurality of rollers (111, 111', 111'') and coupling means (114) for coupling all of said rollers to said converter means (113) ; said plurality of rollers being arranged in tandem fashion so as to be lie along an imaginary line which is substantially parallel to a path of movement of said carrier means (20) ; said rollers being spaced sufficiently far apart so that at least two of said plurality of rollers are always in engagement with at least one of said tilt tray carrier means. The apparatus of Claim 11 wherein three rollers are provided. The apparatus of Claim 12 further comprising a support (106) for mounting said feedback means on said track means ; resilient mounting means (116a, 119, 121) coupled to said support for resiliently mounting said rollers ; and said resilient mounting means being coupled to said rollers for causing said rollers to exert a substantially constant force of the order fo 8,9 to 17,8 N upon said carrier means. The apparatus of Claim 2 further comprising straightening cam means (92) arranged adjacent said track means downstream relative to said tip cam means (70) for engaging said roller means to move said tilting means (27) to its upright position. The apparatus of Claim 2 further comprising : first and second straightening cam means (92) arranged along opposite sides of said track means (41, 42) a spaced distance downstream relative to said tip cam means (70) and each being engageable with an associated one of said cam roller means for realigning said tilting mechanism and said tilt tray to the upright position ; and each of said cam straightening means comprising an inclined cam surface (92b) whereby at least one of the cam follower rollers (31a, 31b) engages the associated inclined cam surface to move said tilting mechanism to the upright position and wherein the remaining one of said inclined cam surfaces engages the remaining cam follower roller to prevent overshoot of the tilt mechanism as it is returning to the upright position. The apparatus of Claim 2 further comprising : a slide block (77); a link (74) pivotally connecting the free end of said tip cam (73) to said side block ; cylinder means (79) for reciprocating said side block whereby movement of said side block in a first direction causes a free end of the tip cam member to be lifted to an inclined position for tilting said tilting mechanism and to be moved to a horizontal position (73) displaced from said tilting mechanism when moved in the opposite direction. The apparatus of Claim 16 wherein said tip cam means (70) further comprises an inclined ramp (72) arranged upstream relative to said tip cam member (73) for guiding a cam follower roller along an inclined surface preparatory to engagement with the tip cam member when in the second position. The apparatus of Claim 15 wherein each of said first and second cam straightening means is further comprised of adjustable means (94) for extending the height of said inclined cam surface (92b). The apparatus of Claim 10 wherein said speed monitoring means (104) comprises a plurality of roller means (111, 111', 111''); elongated mounting means (108, 110) for rotatably mounting each of said roller means thereto whereby the axes of rotation of said roller means lie at spaced intervals along and perpendicular to an imaginary straight line ; housing means (106) coupled to said track means for supporting said speed monitoring means (104) ; spring means (119, 121) coupled between said housing means (106) and said mounting means (108, 110) for resiliently supporting said mounting means ; coupling means (114) for coupling rotation of all said roller means to said converter means (113) ; said housing means (106) being positioned relative to said track means to place the roller means in a position for rollingly engaging the bottom surfaces of said carrier means (20) ; the spacing between said roller means (111, 111', 111'') being sufficient to assure that at least two of said roller means are always in engagement with one or more of said carrier means. The apparatus of Claim 19 wherein said speed monitoring means includes three roller means (111, 111', 111'') ; each of said roller means and said converter means (113) being provided with integral gear means (113a, 111a) ; and means (114) entrained about all of said gear means for maintaining all of said roller means and said converter means rotating at substantially the same angular speed. The tray conveyor system according to Claim 1 wherein each carrier means further comprises : a body (21) having a longitudinal tilt axis ; said roller means comprising rotatable wheel means (25, 27) arranged near a rear end of said body for rollingly supporting said body ; a support tray (23) swingably mounted upon said body and being swingable along a longitudinal axis substantially coincident with the longitudinal tilt axis ; a coupling (24) releasably secured to the forward end of said body ; said body having a coupling receiving pin (P) near said rear end for receiving the coupling (24) of a similar apparatus ; a locking means (28) on said body ; tilt means (27) coupled to said tray and swingable therewith ; said tilt means including (am) follower rollers (31a, 31b) mounted upon a tilt bar and extending beyond opposite sides of said body ; said tilt means including a swingable locking plate (32) swingable about an axis transverse to said longitudinal axis ; and cooperating having means (32a) cooperating with said locking means when in a first position ; bias means (35) normally urging said locking plate toward said locking means ; said locking plate being swingable away from said locking means to a second position displaced from said locking means when said tilt means is tilted through a first predetermined angle away from the upright position and said tilting assembly and said tilt tray being tilted in the same direction as said tilting apparatus as said tilting assembly moves through a second predetermined angle. The apparatus of Claim 21 wherein one of said locking means and cooperating means comprises a pin (28) and the other of said locking means and said cooperating means comprises an opening (32a) for receiving said pin. The apparatus of Claim 21 wherein said support (23) comprises a base portion (23a) and sides (23b, 23e) integral with substantially surrounding said base portion and cooperating with said base portion for embracing a product deposited upon said base portion, said base portion being substantially rectangular and having integral longitudinal sides (23b, 23c) and two integral lateral sides (23d, 23e) ; said longitudinal sides each substantially forming a right angle with said base portion ; and said lateral sides forming a small acute angle with said base portion. The apparatus of Claim 21 wherein said cam follower rollers (31a, 31b) are adapted to rolling (14) engage a tilt initiating device (70) ; said bias means comprising a torsion spring (35) mounted about the pivot axis of said latching plate (32) and having a first arm engaging said tray and a second arm engaging said tilt bar, said torsion spring normally urging said tilt bar in said first direction. The apparatus of Claim 21 wherein : each of said tilt tray carrier means (20) is further comprised of vertical wheel means (27) free-wheelingly mounted upon the coupling receiving pin, receiving said coupling means (24) ; and said tilt bar (31) further comprising resilient means (31c) arranged at spaced intervals about said tilt bar so as to be positioned within elongated openings (29c-1, 29c-2) within a tip frame (29) to prevent contact of said tilt bar (34) with said tip frame (29). The apparatus of Claim 25 wherein said tip frame has a substantially rectangular frame shaped configuration comprised of four integral sides (Fig. 4a) surrounding an open central area and a pair of integral arms (29d, 29e) projecting from one end of said frame, said arms being provided with openings (29d-1, 29d-2) for receiving a pivot pin (34) and said elongated openings (29e-1, 29e-2) for receiving said tilt bar (31). The apparatus of Claim 21 wherein said rotatable wheel means comprises a first pair of wheels (25) extending beyond opposite sides of said body (21) and a single wheel (27) having a rotating axis which is perpendicular with the rotating axis which is perpendicular with the rotating axis of said first pair of wheels the axis of rotation of said single wheel being equidistant from the axis of rotation of said first pair of wheels. A method for operating a conveyor system according to one of the Claims 1 to 20 for dispensing a bundle upon a moving carrier means (20) moving along a path having a substantially linear path portion as the carrier means moves past a bundle dispensing station (17), said conveyor system including bundle, dispensing apparatus comprising a conveyor belt (151a) aligned transverse to said linear path portion ; a pusher plate (150) and a gate member (160) positioned adjacent said conveyor movable along substantially parallel paths which are parallel to said linear path, said method comprising the steps of : moving the bundle onto said conveyor means ; positioning said gate means (160) across said conveyor means to block movement of a bundle beyond said gate means ; moving said conveyor means in a direction to advance said bundle means toward said gate means ; halting said conveyor means when said bundle engages said gate means ; and rapidly moving said pusher means in the same direction of movement as said carrier means whereby the bundle engaged by said pusher means is pushed off of said conveyor means at a velocity to cause said bundly to move completely off of said conveyor means and experience a free-fall drop under the influence of gravity and the force imparted to the bundle by said pusher means to fall flat upon said carrier means, without turning or trumbling. The method of Claim 28 wherein said conveyor means (151) is inclined at an angle to the horizontal sufficient to compensate for tipping of said bundle as it leaves said conveyor, further comprising the step of moving the pusher means (150) at an angle which is substantially the same as the angle of inclination of said conveyor means ; and aligning the surface receiving the bundle being substantially horizontal (14). The method od Claim 28 further comprising the steps of rapidly returning the pusher means to the start position preparatory ot receiving the next bundle. The method of Claim 28 further comprising the step of retracting the gate member (160) and moving the bundle on the conveyor means to a bypass location.

Inventors: HOUSEMAN J D, PAETS HENRI T, SJOGREN CHRISTER A, HOUSEMAN, J.D., PAETS, HENRI T., SJOGREN, CHRISTER A.
Applicants: QUIPP SYSTEMS INC, QUIPP SYSTEMS, INC.
Application year: 1990
Main classification: B65G47
IPC codes: B65G23, B65G47