fig1 and 2 illustrate a bagging machine 10 as is typical of bagging machines used to fill a large flexible bag shown in phantom and indicated by reference number 12 . such bags 12 are mounted in folded condition ( accordion - type fold ) to the exterior of the tunnel 14 and is deployed incrementally as material is force - fed into the bag . as seen in fig1 , a backstop 16 is secured by cables 18 to cable drums 20 on machine 10 and the cables are resistively reeled out ( resisted by a brake mechanism ) to permit deployment of the bag . pressure to overcome the brake resistance is applied by the closed end 13 of the bag being forced outwardly as material is fed into the bag which will now be explained . a feed rotor 22 is shown in both fig1 and 2 , but the reader is particularly referred to the schematic side view illustration of fig2 . as illustrated in fig2 , a restricted inlet 24 is defined by the back - lower end of tunnel 14 and the tunnel floor 26 . the feed rotor 22 is positioned adjacent to the inlet and is rotated to grab and direct material being fed by conveyor 28 toward the feed rotor as indicated by directional arrows 30 , and from the feed rotor through the inlet 24 and into the tunnel 14 as indicated by arrows 30 ′. in operation , material to be bagged ( reference 32 ) is moved by e . g ., the conveyor 28 , which first engages beater bars 34 and is then directed into the teeth 36 . the teeth 36 rotate ( counter - clockwise as seen in fig2 ) to force - feed the material through the inlet 24 and into the tunnel 14 . the bag end 13 and backstop 16 is initially adjacent the end opening 38 and material 32 is fed into the tunnel and against the bag end 13 and backstop 16 . the bag end 13 is prevented from pushing away from the opening 38 by the cables 18 . the material fills the tunnel 14 to a compacted state and continued rotation of the rotor 22 generates a reverse force against the tunnel until sufficient pressure is applied to the backstop 16 to overcome the brake resistance of cable drums 20 ( see fig1 ). at that point the cable drum releases additional cable 18 and the machine 10 moves away from the backstop and such produces incremental deployment of bag 12 from the tunnel 14 . accordingly , material 22 in the tunnel 14 is incrementally moved through the end opening 38 and into the bag 12 . whereas the above procedure theoretically produces compaction of the material , first in the tunnel and then in the bag to fill the bag ( the bag being sized according to the tunnel size ) whereby the bag should closely confine the material and alleviate bag slack and the presence of air . experience has revealed , however , that the material settles and undesired bag slack does occur , particularly in the larger sizes of bags , e . g ., 10 to 16 feet in diameter . whereas the bag &# 39 ; s slack has been largely accepted as unavoidable for the larger sized bags , e . g ., of silage material , it has not been accepted as satisfactory . in the course of trying a variety of modifications , a change to the feed rotor unexpectedly has resulted in a desirable improvement to compaction which is now explained . as will be noted from fig1 , 5 and 6 ( and as explained in the above noted &# 39 ; 877 patent ), the feed rotor 22 is comprised of a center pipe 40 to which is affixed a pattern of radially extended teeth 42 . the teeth are provided as individual segments 44 as best seen in fig3 and 4 . each segment is a base ring 46 with teeth 42 intregal with and radially extended from the ring 46 . the inner diameter of the center opening 48 matches the outer diameter of the pipe 40 ( fig5 ) and thus the ring 46 can be slid onto the pipe from one end and positioned both axially and circumferentially as desired . many such segments 44 are mounted to the pipe and welded into place . it is desirable to offset adjacent segments circumferentially to form a pattern of teeth whereby the engagement with the material is essentially continuous while feeding incremental portions of the materials into and through the inlet 24 . as known to the industry and as illustrated in fig6 , fixed stripper bars 50 ( shown in dash line ) are positioned above the inlet 24 and fit between the teeth 42 to strip away material that is carried up and back over the rotor . from fig3 - 5 , it will be noted that each segment 44 carries three equally spaced teeth 42 . the leading edge of each tooth is provided with a wear strip 52 which can be replaced as needed . as seen in fig6 , the spacing between the segments 44 is about equal to the teeth width , e . g ., one inch . the rotor of the invention as provided with a three - teeth arrangement , even when slowed as compared to the prior two - teeth arrangement , produces a faster fill rate with less power . more importantly , the three - teeth arrangement provides better compaction of the material in the tunnel and thus in the bag . this result is not fully understood but is believed to be generated by the reduced size of the pocket that is formed between the segments . each tooth , in conjunction with the side walls of adjacent teeth , acts like a fast - moving bucket that engages and tears away a portion of the material . these are smaller buckets than previously , due to the closer spacing circumferentially , but there are more of them and material is fed into the tunnel as rapidly or even more rapidly but as smaller clumps . the smaller clumps compact in the tunnel with reduced interstices that otherwise form when compacting the larger clumps . thus , there is less settling and less bag slack and higher percentage of material per bag capacity . fig7 - 9 illustrate variations in the manner of securement of the teeth segments to the rotor pipe . in fig7 , the pipe 54 is square shaped and a square shaped opening 57 of teeth segment 56 allows the teeth segment to be fixed circumferentially relative to the rotor pipe without spot welding . the teeth may be separated by a spacer 58 . fig8 is a further variation with grooves 62 formed in a cylindrical pipe 60 and the teeth segment 63 and spacer 66 provided with tabs 64 and 65 respectively that fit the groove 66 which permit relative sliding and not rotative sliding of the segments on the pipe . fig8 illustrates a trapezoidal slot 68 formed in shaft 66 with segment 70 having tangs 21 that fit the slot . spacers 72 are similarly configured . in all these cases , the shafts 54 , 60 , 66 may be twisted ( or the grooves 62 , 68 twisted relative to the shaft ) to achieve the desired circumferential offset of adjacent teeth sets . alternatively , the teeth sets may be varied as to the circumferential location of the opening 57 , tab 64 or tang 71 relative to the teeth . a further embodiment is illustrated in fig1 wherein the pipe or shaft is provided with closely spaced grooves and the teeth segment 76 has widely spaced apart groove fitting teeth that permit adjustment of the segment 76 rotatively relative to each other . those in the art will conceive of modifications and variations as compared to the disclosed embodiment herein . the claims are not limited to the enclosed embodiment but include all such modifications and variations that are encompassed by a broad interpretation of the claims appended hereto .
a rotor for a bagging machine used to force feed material , e . g ., silage , for compaction in a tunnel of the machine prior to insertion of the material into a large storage bag . the rotor includes teeth sets closely spaced along the length of the rotor and each teeth set including at least three circumferentially spaced teeth . preferably the teeth of each teeth set are intregal with a support or base ring that slidably fits en elongate pipe or tube and position axially in circumferentially as desired and then weld tacked to the pipe .