Waste recycling device

The present invention relates to unique waste recycling machines possessing improved efficacy in recycling bulky waste materials to a recycled waste product. The feed for the machine is equipped with a floating stripper plate which scrapes adhering waste materials from a continuous metal apron feed. The device also includes a releasable cradle assembly which supports a striking bar and a screen positioned about a rotating drum equipped with impacting teeth or blades. When a damaging obstacle enters an impacting or fragmenting zone of the machine, a shear pin which maintains the cradle assembly in a fragmenting position will shear causing the cradle assembly to become dislodged to an inoperable or non-damaging position. The machine also includes impacting teeth which are dynamically balanced and positioned upon a rotating impacting drum so as to effectuate especially effective fragmentation of waste materials to a desired particle size.

FIELD OF THE INVENTION 
The present invention relates to recycling machines and methods for 
recycling bulky materials and more particularly to machines and methods 
for processing of waste materials to a desired particle size and bulk 
density. 
BACKGROUND OF THE INVENTION 
The current economy generates vast tonnages of wastes for disposal. Such 
wastes contain a multitude of diverse chemical components. Most 
unprocessed wastes exist as bulky materials which, in the unprocessed 
form, are usually unusable and occupy tremendous space. Landfill disposal 
no longer affords a satisfactory disposal solution to modern day wastes. 
Plastics, cellulosic materials (e.g. vegetative wood, paper, cardboard, 
etc.), glassware, waste foods and feeds, metals, agricultural, 
construction and industrial wastes, etc. generally comprise the bulk of 
such wastes. Certain waste collection sites and municipalities require a 
separation of wastes into different classes of waste materials such as a 
separation of paper, wood, metal cans, plastics, waste foods, etc. These 
separated wastes are desirably converted to less bulky materials and 
recyclable products such as recycled metals, recycled wood, (e.g. 
landscaping mulch and livestock bedding, pressed wood products), 
cellulosic products such as recycled paper, cardboard, cellulosic 
insulation, newsprint, livestock bedding, and other similar useful and 
saleable products. Processed wastes are also utilized as an energy source 
for powering commercial and industrial equipment such as in generating 
electricity and drying kilns. 
Costly, heavy-duty equipment powered by energy-consuming motors operated at 
relatively high r.p.m. and momentum are generally needed to process such 
wastes. The recycling machines are designed to convert the wastes into a 
form suitable for resale or reuse. The waste recycling generally entails 
grinding the bulky waste material to a useful bulk density or particle 
size. 
The problems associated with industrial waste disposal may be typified by 
the accumulation of wooden pallets at a heavy industrial manufacturing 
sites. Raw materials and components used by the manufacturer are 
customarily shipped upon wooden pallets which affords a convenient means 
for transporting the components about the manufacturing facility with 
forklift trucks. It is usually too costly to return, reship or reuse these 
wooden pallets. As a result, stockpiles of wooden pallets typically 
accumulate at the manufacturing site. Disposal of these bulky and 
space-consuming wood pallets becomes a troublesome and costly problem. 
Waste materials are often prone to be contaminated with latent materials 
capable of causing considerable damage to the waste processing equipment. 
It is often economically unfeasible or undesirable to purify or refine 
waste materials so as to insure removal of machine damaging contaminants. 
This is typified by the processing of common wastes such as wood and 
garbage products which may often contain a machine damaging substance such 
as a large metal rod or rail, a rigid pry bar, etc. Conventional waste 
processing devices are poorly equipped with safety mechanisms capable of 
safely interrupting the mechanical operation or working of machine before 
extensive damage is caused to the device. This can result in extensive 
downtime for costly repairs and service. In the meantime, unprocessed 
wastes continue to accumulate at an unsafe and unhealthy rate. Another 
problem associated with conventional waste recycling devices is the 
propensity of the wastes to clog or foul the machinery. The need to 
frequently clean, maintain and repair untidy equipment leads to costly and 
prolonged downtime during which the wastes continually stockpile. 
There exists a need for a high-capacity, waste recycling device capable of 
effectively handling a broad spectrum of waste materials to produce an end 
product of a desired uniformity and quality. A productive recycling 
machine capable of recycling stockpiled waste of conventional garbage and 
cellulosic materials (e.g. paper, wood, etc.) for prolonged operational 
periods without fouling or clogging would fulfill a long existing need 
within the waste disposal industry. A waste recycling machine equipped to 
productively handle large waste volumes at a relatively low rate of power 
or energy consumption would fulfill another existing need. Another 
prerequisitial need centers upon the need for a waste recycling machine 
equipped with different screen types which may be expeditiously removed 
and replaced by another screen so as to permit effective processing of 
different waste materials into end products of a desired uniformity. 
Another current need centers upon a desire for a high-capacity waste 
recycling device equipped so as to spontaneously interrupt its mechanical 
operation when subjected to potentially damaging hazards so as to avoid 
otherwise extensive damage and costly repairs to the processing equipment 
and injury to persons. Another desire is a need to provide a high volume 
and durable waste disposal device which can be effectively operated for 
prolonged mechanical working periods without requiring extensive downtime 
for maintenance and repair. These needs and other objectives are generally 
achieved by the unique waste recycling device of this invention and its 
use. 
SUMMARY OF THE INVENTION 
The present invention provides a waste recycling device or machine capable 
of processing a wide range of waste products to a desired end product. The 
recycling machine is designed to effectively handle large waste volumes. 
The recycling device of this invention may be continuously operated for 
prolonged operational periods without costly interruptions. Maintenance, 
repairs and downtime are substantially alleviated by unique features 
afforded by the present recycling machine. The recycling machine affords 
significant efficiencies in energy and power requirements so as to require 
a lesser horsepower than conventional devices for any given capacity. 
The unique recycling machine includes a continuous metal apron comprised of 
metal apron sections hinged together so as to allow the metal apron to be 
continuously driven about spacer and drive sprockets. This provides for 
continuously feeding wastes for processing by the device. An adjustable 
floating stripper plate strategically positioned at a discharging apron 
end tangentially contacts the metal apron so as to cleanly strip waste 
materials from the apron. The apron is thus thoroughly cleaned of debris 
as it revolves about a discharge end sprocket (i.e. at juncture of 
changing its planar direction) and commences its return to a feed trough 
at the replenishing feed inlet. The adjustable floating stripper plate is 
pivotally or axially mounted at one end and biasingly leveraged against 
the apron through use of a tensioned adjusting bolt or bolts positioned at 
a biasing site. This allows the stripper plate to float freely upwardly 
and downwardly upon the metal apron. Springed adjusting bolts permit for 
an operational adjustment to the appropriate applied tension level by the 
stripper plate tip against the apron. The stripper plate serves to 
effectively remove and cleanly strip waste residue from the apron. Thus, 
any build up of adherent and potentially fouling substances upon the apron 
is thereby avoided. The freshly cleaned apron is then driven about a 
feed-end sprocket to a feed site wherein freshly replenished waste 
materials are again fed onto the apron for its return trip to the stripper 
plate. 
The floating stripper plate is positioned in a juxtapositional feeding 
relationship to a striking bar so that material stripped from the feed 
apron freely flows onto a striking bar. Initial fragmentation of the waste 
feed is accomplished within a dynamically fragmenting zone comprised of a 
unique striking bar and a cylindrical rotor equipped with a balanced 
arrangement of breaker teeth. The striking bar serves as a supportive 
anvil for shearing waste material fed to the fragmenting zone. Upon 
impacting against waste supported by the striker bar, the shearing teeth 
pull and shred the supported waste in a downwardly and radially outwardly 
direction away from a cutting edge of the striking bar. The teeth, which 
exert a downwardly and radially outwardly pulling and shearing action upon 
waste material resting upon the anvil, are positioned (in relationship to 
a vertical line intersecting the axial shaft of the rotating cylinder 
assigned a value of 0 degrees) so as to make initial contact upon the 
waste at a radial arc ranging from about 26.degree. to about 36.degree. 
angle. The counterclockwise rotating cylinder equipped with tangential 
disposed removable breaker teeth is preferably positioned from about a 
64.degree. angle to about a 76.degree. angle in relation to the striker 
bar. The net effect of this arrangement results in a highly effective 
shearing or fragmentation of the waste materials at the striking bar site. 
The striking bar incorporates a unique releasing mechanism which allows the 
striking bar to become safely disengaged from the fragmenting zone when 
exposed to a damaging force exceeding the safety tolerance of the device. 
This is accomplished by means of a unique break-away cradle assembly which 
serves as a supportive structure for the striking bar and a removable 
screen. The striking bar may be structurally integrated into the 
supportive frame structure for the cradle assembly. Associated with the 
cradle assembly is a shearing means which, upon exposure of an excessive 
torquing force (e.g. a lodged damaging obstacle), will shear so as to 
cause the entire cradle assembly including the striking plate and screen 
to become disengagedly dislodged or removed to a disengaged unoperational 
position. The striker bar, which forms the leading edge of the cradle 
intake side, will thus, as in the case of the screen, be released to a 
non-damaging position upon exposure to a damaging obstacle which exceeds 
the shearing tolerance of a shear pin or shear bolt mechanism. The unique 
break-away feature afforded by the cradle assembly provides excellent 
mechanical protection against structural damage. 
The screen is also cradled within a supportive cradle structure positioned 
about an arcuate section of the rotating cylinder. The screen also 
embodies several unique features which contributes a higher efficacy in 
the processing of waste materials. As mentioned, the screen and striking 
bar incorporate a unique break-away shearing mechanism. Further 
fragmentation of waste materials occurs as the fragmented waste is 
propelled by the toothed rotary cylinder across the grated surface of a 
replaceable screen. The screen serves to further fragment and grate the 
waste until the waste is reduced to appropriate sized particles for 
screening and recycling collection. 
The cradle assembly advantageously includes an adjustable clearance means 
for adjusting the cradle so as to provide the appropriate clearance or 
distance between the rotating teeth, the striking bar and the screen. The 
unique cradle assembly of this invention permits a simultaneous adjustment 
of both the screen and striker bar to an operational clearance which, in 
turn, optimizes the waste fragmentation and screening efficiency for the 
particular waste being processed by the machine. 
The shearing mechanism is operationally associated with the cradle assembly 
which uniquely breaks away from a processing or fragmenting zone when 
subjected to a damaging obstacle. The cradle assembly, which supports the 
screen and striking bar, is operationally connected to cammed shearing 
means. The supportive cradle is preferably pivotally or axially mounted at 
one end (distal or discharge side) and equipped at an opposing screen 
cradle end with a cammed shearing means operationally connected to the 
adjustable clearance means for adjusting the clearance between the 
striking bar, the screen and the rotor. The cammed shearing means, upon 
exposure to a force exceeding the desired shear limitations for the 
device, will shear the shear pin or shear bolt which in turn allows the 
cam to spontaneously pivotally rotate and immediately drop the supportive 
cradle along with its attached striking bar and supported screen to a safe 
and undamaging distance from the rotating teeth. 
The cradled screen design also permits the screen to be conveniently 
removed and replaced with another simply by unsecuring the adjusting means 
and removing the screen from cradle. A boom mountable to a boom mount 
enables a single operator to readily remove and replace a cradled screen 
with another screen. 
A unique feature provided by a cradle assembly in operative association 
with shear releasing means resides in a machinery capability to 
instantaneously break away from the rotating teeth when subjected to a 
potentially damaging obstacle creating a shearing force which exceeds the 
shearability threshold of the shear pin or shear bolt becomes lodged 
within the processing zone. The shear bolt or shear pin and supportive 
cradle assembly embodiments allow the device to be safely operated at a 
high revolutionary speed and momentum without undue concern over the 
latent presence of damaging obstacles in the waste. When a damaging 
obstacle is encountered, the shear pin or bolt will simply instantaneously 
shear causing the cam to rotate about its axial support and drop the 
cradled screen and striking bar to a safe and non-damaging clearance from 
the rotating teeth. In operation the cradled screen and striking bar may 
be further disengaged by untightening clearance adjusting means so as to 
provide a greater clearance for effective removal of lodged obstacles from 
the processing zone or for screen removal and replacement. After removing 
the damaging obstacle, a new shear bolt may be inserted into the screen 
and striking bar reset to an appropriate operative clearance for effective 
operation. 
The unique waste processing machine provides an effective machine for the 
processing of conventional garbage and cellulosic objects such as paper 
and wood. These waste tend to form compacted materials which can readily 
lead to clogging or stalling of the device. The present device alleviates 
these problems and permits the unit to be utilized at a highly efficient 
processing capacity while substantially curtailing the energy requirements 
needed to process the wastes.

DETAILED DESCRIPTION OF THE INVENTION 
With reference to the figures, the basic mechanical operations of the 
depicted recycling machine (referenced in general as 1) include, in 
general, feeding means (defining a feeding zone generally enumerated as 3) 
for feeding wastes W to fragmenting means (generally depicted by 4) for 
fragmenting the waste to a desired particle size and bulk density and 
discharging means (defining a discharging zone and generally designated as 
5) for discharging of processed or fragmented waste materials D from 
machine 1. 
As depicted FIGS. 1-13, the present invention provides a unique releasable 
cradle assembly (generally designated by a 30 series enumeration) for use 
in a waste processing machine 1 comprised of an impacting rotor 40 
equipped with impacting teeth 41 rotationally carried about a cylindrical 
drum 42 and a screen 43 for screening particulated wastes D therethrough, 
said cradle assembly 30 comprising: 
a) a supportive cradle frame 31 for supportively securing screen 43 
thereto; 
b) a striking bar 33 carried by the frame 31 at a waste fragmenting 
position (shown as F); 
c) releasing means (generally designated as 35) for disengaging the cradle 
assembly 30 from the fragmenting position F upon subjecting the cradle 
frame to an excessive shearing force; and 
d) adjustable clearance means (generally designated as 37) for adjusting 
the cradle assembly 30 to the waste fragmenting position F. 
As further depicted by FIGS. 1-3 and 5-6, the waste recycling machine 1 is 
suitably equipped with a waste feed cleaning assembly 13 for cleaning 
waste residues W from the assembly 13, said waste cleaning assembly 13 
comprising a conveying apron 9 continuously driven about laterally 
disposed pulleys 9D and 9E, an adjustable floating stripper plate 15 
equipped with a scraper blade 15A tangentially contacting apron 9 so as to 
scrape the waste residues W from apron 9 and an adjustable biasing means 
17 for adjusting a scraping force as applied by said scraper blade 15A 
against said conveyor 9. Waste residue W uniformly and cleanly scraped 
from the apron 9 by scraper 15 is then discharged to the fragmenting zone 
F for fragmentation to the desired particle sized waste D. 
FIG. 1 depicts an external side view of the waste recycling machine 1 of 
this invention. The depicted machine 1 includes a sturdy frame 16 (shown 
more particularly in the cross-sectional views) of welded steel beams 
supportive of mechanical workings of machine 1. Since machine 1 is used to 
splinter and fragment wastes under great impacting forces, machine 1 is 
protectively covered with a sturdy plate metal shell 18. Appropriate 
powering means structurally anchored to frame 16 of machine 1 provides 
means for powering machine 1 as may also be observed in FIG. 1. Although 
machine 1 may be powered by a variety of appropriate power sources (e.g. 
internal combustion engines, diesel engines, hydraulic motors, industrial 
and tractor driven power take-offs, etc.), the depicted machine 1 is shown 
as being powered by several electrical motors generally prefixed by M. 
FIG. 1 depicts four electric motors equipped with suitable drive means for 
powering the various working components (namely the feeding, fragmenting 
and discharging means) of machine 1. As may be more specifically observed 
from FIG. 1, the four separate electrical motors M are used to separately 
power different drives and functions for machine 1. Feed motor M.sub.F 
powers feeding means 3 in cooperation with power feed motor M.sub.P which 
powers power feed 8. A rotary motor M.sub.R powers the fragmenting means 
of fragmenting rotor (generally represented as 40) and a discharging motor 
M.sub.D powers the discharging means for conveying discharged wastes D 
from machine 1. 
The feeding means 3 (shown in greater detail in FIGS. 2 and 3) includes a 
hopper 7 for receiving waste materials W and a continuous apron 9 or 
conveying belt for feeding wastes W to waste fragmenting zone 4. The 
feeding means 3 incorporates into its operation a unique feed cleaning 
assembly (generally designated as 13 and shown in more detail by FIGS. 2, 
3, 5, 6 and 9) for effectively cleaning waste residues W from apron 9. 
Apron 9 is preferably constructed of rigid apron sections 9A (e.g. 
heavy-duty metal, plastic, etc.) hinged together by piano hinges 9B which 
are continuously driven about drive pulley 9D and idler pulley 9E 
respectively laterally disposed at opposing ends of apron 9. Apron 9 is 
typically operated at an apron speed of about 10 to about 30 feet per 
minute. Apron 9 may be connected to switching means (not shown) responsive 
to operational torquing forces as applied to impacting rotor 40 so as to 
switch off the apron feed when rotor 40 becomes filled to capacity with 
wastes W in the fragmenting zone 4. 
The depicted apron 9 includes a series of rectangularly-shaped, 
flat-surfaced metal sections 9A hinged crosswise with laterally disposed 
piano hinges 9B alternatingly and intertwinely welded along the sides of 
adjacently positioned sections 9A. Pulleys 9D and 9E may be illustratively 
fabricated from 8" O.D. steel tubing stock 9T. Drive pulley 9D is 
appropriately equipped with a series of parallel hard weld beads 9W 
measuring about a 1/4" radius in size welded crosswise at laterally spaced 
intervals onto tubing stock 9T as shown in FIG. 5 so as to provide 
sprocketed ridges for gripping and propelling apron hinges 9B about drive 
pulley 9D. Shaft support sidewalls 9X (at tube 9T ends) form a sidewall 
closure to tubular tube 9T ends as well as providing mounting for feed 
shaft 9S which may be directly welded to shaft housing apertures 9O of 
sidewalls 9X. It is desirable to prevent wastes W from accumulating upon 
the inner apron 9 surface as well as the feed surface. The inner apron 9 
surface may be cleaned by providing idler pulley 9E with augered flighting 
(left handed and right handed flighting, not shown) which serve to remove 
waste residue accumulations from the underside of apron 9. 
Feed apron motor M.sub.F effectively serves to drive apron 9 by means of 
feed motor drive pulley (not shown) which belt drives feed belt 9F, feed 
running pulley axially mounted feed shaft 9S and apron drive sprocket 9P. 
A power feeder (designated in general as 8), in cooperative association 
with apron 9, uniformly feeds and distributes waste bulk W to fragmenting 
zone 4 at a proper positioning for fragmentation by fragmenting rotor 40. 
Power feeder 8 contains of a series of projecting feeding teeth 8A 
positioned for counterclockwise rotational movement upon power drum 8D. 
Power feed shaft 8S connected to drive sprocket 8P driven by chain 8B, 
drive sprocket (not shown) and motor M.sub.P serves to locomote power 
feeder 8. The feed depth, or clearance, of power feeder 8 is regulated by 
a hydraulic cylinder 8H connected to a suitable hydraulic fluid power 
source (not shown) which provides an adjusting means for adjusting the 
power feeder 8 to the appropriate clearance for feeding wastes W. 
Hydraulic cylinders 8H are also preset to withstand a predetermined back 
pressure so as to permit power feeder to float upon waste materials fed 
upon apron 9. 
In the preferred embodiments, cleaning assembly 13 cooperatively includes a 
rigid conveying apron 9 and an adjustable floating stripper plate 15 
equipped with a scraper blade 15A which tangentially contacts against 
apron 9 and scrapes waste residues W from apron 9. As further shown by the 
cross-sectional views of FIGS. 2, 6 and 9, stripper plate 15 and its 
scraper blade 15A extends crosswise across the entire width of apron 9. 
Apron 9 is suitably constructed of materials possessing sufficient 
rigidity against which floating blade 15A may then apply a sufficient 
scraping force so as to effectively remove waste residues W from the 
transporting surface of apron 9. 
Cleaning assembly 13 preferably includes an adjustable biasing means 17 for 
adjusting the amount of tension applied by the stripper plate 15 against 
apron 9. The stripper plate 15 is designed so as to float along the 
surface of apron sections 9A and hinges 9B as apron 9 is continuously 
driven about drive pulley 9D. Stripper plate hinge 15H (positioned at an 
opposite end of stripper plate 15 from scraper blade 15A) provides a 
floating pivotal or axial mount for stripping plate 15. Hinge 15H may be 
suitably constructed as a piano hinge which extends crosswise across the 
entire width of stripper plate 15. Hinge 15H may be illustratively 
constructed of 2" length by 3/4" I.D. steel bushing stock 15P alternately 
welded to support frame 16 and underside of stripping plate 15 to provide 
a piano hinge of intermeshing and aligned bushing stock hinges 15P hinged 
together by 11/16" O.D. rod stock 15R. 
The depicted cleaning assembly 13 includes two anchor bar hold-down springs 
17 laterally secured at opposing bar 15W ends by hold-down brackets 15L by 
chain links 15Q directly welded or secured to hold-down brackets 15L. 
Hold-down spring 17 comprises an adjustable tension spring 17S equipped 
with an adjusting bolt 17B and nut 17N which permits the tension of spring 
17S to be adjusted to the appropriate stripper plate 15 tension. 
Discharging plate 15B collects wastes distributed by distributor plate 15D 
and discharges the scraped wastes W to the fragmenting zone 4. The 
distributor plate portion 15D of stripping plate 15 includes a 
reinforcement bar 15T and a series of hold-down brackets 15L fitted with 
anchor bar apertures 15O which serve to house a stripper plate anchor bar 
15W. Anchor bar 15W extends across the entire crosswise width of stripping 
plate 15 and externally protrudes outwardly from covering 18 so as to 
permit a machine operator to make external adjustments of anchor bar 15W. 
Hold-down brackets 15L may be fabricated from a series of flat stock plate 
(e.g. four or more) fitted with aligned anchor bar apertures 15O for 
housing and retaining anchor bar 15W. As may be observed from the Figures, 
the distributor plate 15D, scraper blade 15A. hold-down brackets 15L and 
anchor bar 15W freely float about hinge 15H. As may be further observed 
particularly from FIGS. 4-6, anchor bar 15W is externally fitted with 
anchor bar adjusting means (generally shown as 17) which, upon tightening, 
serves to limit the upper movement of stripper plate blade 15A more firmly 
against apron 9 and upon untightening to allow a greater clearance of 
blade 15A against apron 9. The adjustable anchor bar 15W, when properly 
adjusted, serves as a safety stop so as to protect both the stripping 
blade 15 and apron 9 from damage. 
The basic fragmenting components of the fragmenting means 4 comprise a 
fragmenting rotor (generally referenced as 40) equipped with impacting 
teeth 41 carried by rotor 42, and a releasable cradle assembly 30 equipped 
with a striking bar 33 and a grating screen 43. Rotor 42 axially mounted 
to rotor shaft 42S is rotationally driven by running pulley 42R, belt 42B, 
drive pulley 42D and motor M.sub.R. 
The cross-sectional views of FIGS. 3, 5-6 and 9-11 depicts in greater 
detail the cooperative operational relationship between feed apron 9, the 
power feeder 8, stripper plate 15, striking bar 33 and the impacting teeth 
41 of the rotor 42. The adjustable floating stripper plate 15 cleanly 
strips waste materials W from the apron 9. Waste materials W fed onto the 
cutting zone or radii of rotating teeth 41 are fragmented to smaller sized 
particles as teeth 41 impact upon the waste material W supported upon the 
striking bar and projecting onto the fragmenting zone 4. Material 
fragmented by the impacting teeth 41 is then radially propelled along the 
curvature of the screen 43. Screen 43, in cooperation with the impacting 
teeth 41, serves to further fragment by grating the waste materials W upon 
the screen surface and to refine the waste into a desired particle 
screening size until fragmented to a sufficient particle size so as to 
screen through screen 43 for collection and discharge by discharging 
conveyor 51. 
Initial fragmentation of the waste feed W is accomplished within a 
dynamically fragmenting zone 4 comprised of a unique striking bar 33 and a 
cylindrical rotor 42 equipped with a dynamically balanced arrangement of 
breaker teeth 41. The striking bar 33 serves as a supportive anvil for 
shearing waste material W fed to the fragmenting zone 4. Teeth 41 are 
removable and may be bolted to rotor 42. As may be observed, teeth 41 are 
staggered upon rotor 42 and dynamically balanced. Rotor 42, when operated 
at an operational rotational speed of about 1800 rpm, rotates about shaft 
42S in complete balance. This permits it to move freely without excessive 
vibration or unbalance about shaft 42S in a rotationally balanced 
relationship upon rotor 42. 
Upon impacting against waste W supported by striker bar 33, the shearing 
breaker teeth 41 pull and shred the supported waste W in a downwardly and 
radially outwardly direction away from a cutting edge of the striking bar 
33. The teeth 41, which exert a downwardly and radially outwardly pulling 
and shearing action upon waste material W resting upon the anvil 33, are 
preferably positioned (in relationship to a vertical line intersecting the 
axial shaft 42S of the rotating cylinder 42 assigned a value of 0 degrees) 
so as to make initial contact upon the waste W at a radial arc ranging 
from about 26.degree. to about 36.degree. angle. the counterclockwise 
rotating cylindric movement of rotor 42 equipped with tangential disposed 
removable breaker teeth 41 is preferably positioned from about a 
64.degree. angle to about a 76.degree. angular relationship to the striker 
bar 33. The net effect of this arrangement results in a highly effective 
shearing or fragmentation of the waste materials W at the striking bar 33 
site. 
FIG. 3 depicts a cross-sectional view of the cradle assembly 30 and its 
cooperative operational relationship within machine 1. FIGS. 4 and 6-13 
show in greater detail its operative structure. As may be particularly 
observed from FIGS. 6-11, cradle assembly 30 includes an open cradle frame 
(generally designated as 31) equipped at opposite screen 43 ends with 
curved seat sections 31C which mate onto the curvature of discharging side 
of screen 43. Anchoring seats 31A matingly and fixedly retain screen 43 at 
an appropriate cradling position upon cradle frame 31. Frame 31 is 
structurally supported by two laterally disposed curved seat sections 31C 
positioned at each screen length end for cradling screen 43 secured 
together as an open framed structure by supportive cross beams 31B, 
striking bar 33 and latching flange 35F welded to curved section 31C. 
Frame 31 includes a pair of latching support bars 31F which run along the 
entire crosswise length of frame 31 to provide a latch site 35F for 
latching jaws 35J. The latching support bars 31F provide added support for 
the seated cradle sections 31C. As may be observed from FIG. 8, the 
discharging underside of screen 43 is fitted along its peripheral margin 
with crosswise extending interlocking bars or beam 43A for mating 
placement into a series of corresponding notches or grooves of anchoring 
seats 31A provided within cradle frame 31. When screen 43 is positioned at 
a fragmenting position, cradle frame 31 firmly anchors and maintains 
screen 43 at the appropriate position for screening and fragmenting wastes 
W. 
The leading lip edge of frame 31 includes a case hardened striking bar 33 
which extends cross wise across the entire width of cradle frame 31 and 
provides further structural support to the cradle assembly 30. Striking 
bar 33 serves as an anvil firmly bracing wastes W for fragmenting upon by 
impacting rotor 40. Cradle frame 31 is supported at opposite cradle ends 
by caster legs 31L fitted with casters 31W which ride upon caster rails 
16R disposed along inner frame 16 of machine 1. The railed casters 31W 
permit the entire cradle assembly 30 to be withdrawn to a convenient 
working position for removing and replacing screen 43. 
The waste recycling machine 1 of this invention embodies a unique releasing 
means 35 for disengaging a unique cradle assembly 30 from a fragmenting 
position upon subjecting the cradle assembly 30 to an excessive shearing 
force. The cradle assembly 30 includes a striking bar 33 and a screen 43 
uniquely cradled and held in position by cradle frame 31 which, upon 
exposure to excessive shear, will instantaneously disengage from an 
operational position to a non-operating or unlatched position. 
Accordingly, when machine 1 is exposed to a potentially damaging obstacle 
within fragmenting zone 4, which obstacle creates an excessive level of 
shear force within the fragmenting zone 4, the fragmenting workings of 
machine 1 will become disengaged so as to prevent damage to machine 1. 
Cradle assembly 30 embodies a unique shear releasing means 35 or mechanism 
which allows cradled screen 43 and striking bar 33 to cleanly break away 
from the fragmenting zone 4 when subjected to a damaging obstacle which 
creates a damaging force exceeding the threshold of shearability for the 
machine 1. Potentially damaging obstacles such as large sized heavy metal 
objects (e.g. steel rods, tools, etc.) are illustrative of unfragmentable 
objects which are capable of causing considerable damage to both machine 1 
and operating personnel if the fragmenting means 4 cannot be abruptly 
terminated. Similarly, excessive compaction of wastes W within the 
fragmenting zone 4 can also cause damage and injury if the fragmenting 
operation is not promptly terminated. Machine 1, however, is specifically 
designed so as to effectively fragment wastes without excessive compaction 
of wastes W within the fragmenting zone 4. By referring particularly to 
FIGS. 9-12, it will be observed the radial margins of cradle frame 31 are 
axially supported by releasable cradle support means 35 for releasing 
cradle assembly 30 when exposed to excessive shear. The releasing means 
includes a pair of cradle shafts 35S which extend across the entire 
peripheral screen 43 width with each shaft 35S being equipped at one 
terminating end with a pair of radially extending arms 35L and 37L, one of 
which (the adjusting or ratcheting leg 37L) is connected to ratcheting 
adjusting means 37R and the other (shear pin leg 35L) which includes a 
shear pin or bolt receiving aperture 35O. Cradle shafts 35S are equipped 
with collars 35C fitted with latching jaws 35J which, when latched, latch 
onto latching flanges 35F. 
The cross-sectional views of FIGS. 10 and 11 respectively depict the cradle 
assembly 30 in a latched and fragmenting position and an unlatching 
(non-fragmenting) position. FIG. 11 shows the latching jaws 35J in a 
released position with screen 43 and cradle assembly 30 being depicted in 
a non-operative and released position while FIG. 10 depicts the cradle 
assembly 30 in the latched fragmenting position. When it is desired to 
place the screen 43 in a latched and operative position, cradle assembly 
30 is pushed inwardly and upwardly until jaws 35J latch onto latching 
flanges 3SF and secure screen 43 and striking bar 33 in the latched 
position as shown in FIG. 10. 
Cradle assembly 30 includes a pair of axially mounted latchings shafts 35S 
positioned at opposite screen ends with each shaft 35s fitted with 
latching arms 35J anchored (e.g. welded) to latching shaft 35S. Latching 
projections 37J of latching arms 35J shoulder against latching flanges 35F 
of cradle frame 31 when latched and retain cradle frame 31 in a latched 
position as may be observed from FIG. 10. As may be further observed from 
FIGS. 4, 9 and 12, latchings shafts 35S are each externally fitted with a 
shearing leg 35L securely affixed (e.g. welded or bolted) to latching 
shaft 35S. Shearing leg 35L is fitted with a shear pin receiving aperture 
35O for receiving a shear pin or shear bolt 35B. Shear pin leg 35L is 
connected to ratcheting leg 37L by shear bolt 35B seated within a shear 
bolt receiving aperture 35O of shear pin leg 35L and receiving aperture 
37O of ratcheting leg 37L. When secured to shear pin leg 35L, ratcheting 
leg 37L is designed so as to rest at an acute angular relationship with 
shear pin leg 35L. Ratcheting leg 37L is journaled onto collar 35C which 
permits ratcheting leg 37L to freely rotate about collar 35C and latching 
shaft 35S when not securely bolted by shear bolt 35B onto shear pin leg 
35L. 
The releasing means 35 for disengaging the cradle assembly 30 from the 
fragmenting position (latched) as shown in FIG. 10 to disengaged position 
(unlatched) as depicted in FIG. 11 is triggered by a shearing of a shear 
bolt 35B at either or both of the shear apertured bolt locations 35O. As 
may be observed from FIG. 10, latching arms 37J maintain cradle assembly 
30 in an operative fragmenting position until a shearing force exerted by 
a high shear obstacle causes at least one or both shear bolts 35B to 
shear. Shearing of shear bolt 35B disconnects the connecting link between 
shear pin leg 35L and ratcheting leg 37L causing ratcheting leg 37L and 
the latching collar 35C to freely rotate and release latching arms 35J 
from cradle flange 35F. This allows the unlatched cradle assembly 30 to be 
safely removed by gravitational and shearing forces to a safe clearance 
from the damaging effects of an unshearable object lodged within the 
fragmenting zone 4. Depending upon the location and potential damaging 
effect of the shear causing obstacle, either one or both shear bolts 35B 
and support provide screen ends may become unlatched to a protective 
clearance from the obstacle. A particular advantage of the preset release 
mechanism resides in the instantaneous spontaneity for releasing the 
cradle assembly 30 from harmful objects. 
In operational use, clearance adjusting means 37 are adjusted to the 
appropriate clearance for effective processing of wastes. The adjustable 
clearance means 37 for adjusting cradle assembly 30 to appropriate 
fragmenting clearance position is accomplished by ratcheting turnbuckles 
37T which are operatively connected to ratcheting legs 37L. As may be 
observed from FIGS. 9 and 12, one end of each turnbuckle 37T is pivotally 
anchored to turnbuckle mount 37F while an opposite end of the turnbuckle 
37T is pivotally mounted to ratcheting leg 37L by ratcheting leg mounting 
pin 37M. By ratcheting turnbuckles 37T together, ratcheting leg 37L causes 
latching shaft 35S to rotate and draw cradle assembly 30 including the 
cradled screen 43 and striking bar 33 in closer proximity to the impacting 
teeth 41 of rotor 42. By untightening tumbuckles 37T, latching shafts 35S 
rotate in an opposite rotational direction causing a greater clearance and 
distance between cradle assembly 30 and teeth 41. When adjusting 
tumbuckles 37T to the appropriate clearance for smooth operation, the 
operator may listen to the smoothness of the fragmenting process and 
adjust the turnbuckles 37T to the smoothest operation similar to the 
manner an experienced mechanic adjusts a carburetor or timing in 
automotive repair. 
The screen assembly includes screen stop adjusting means (generally 
referenced as 38) which serves as a safety stop for preventing screen 43 
to be drawn too close to impacting teeth 41. The stop comprises a curved 
plate 38P of a concentric curvature mating to the feed side of screen 43. 
Curved plate 38P fits along both outer arcuate margins of screen in 
juxtaposition to covering 18. Adjusting stop nuts 38N welded to stop plate 
38P provide threads for threaded bolts 38B for positionally adjusting stop 
plate 38P. The threaded bolts 38B are connected to adjusting plate 38A 
fitted with a threaded rod 38R mounted to the outside of casing 18. By 
adjusting threaded rod 38R, adjusting plate 38A stop clearance of curved 
stop plate 38P may be, accordingly, adjusted. The adjusting means 38 
includes two adjusting rods 38R positioned at the terminal arcuate ends of 
screen 43 at both screen ends. Thus, the proper alignment for stop plate 
38P is generally accomplished by adjusting the four stop adjusting rods 
38R to the proper clearance for screen 43. As a result, stop plate 38P 
serves as a safety stop to stop screen 43 from being ratcheted by 
adjusting means 37 to an unsafe clearance. 
Discharging conveyor (generally designated as 50) extends lengthwise and 
widthwise along the bottom portion of the device and is driven by motor 
M.sub.D. Materials D fragmented to a particle size sufficient to pass 
through screen 43 gravitate to discharging conveyor 51 which then 
transports the desired material D to a suitable collection point. The 
cross-sectional views of FIGS. 2 and 3 show in greater detail the 
discharging conveyor 51 and the feed apron 9 as well as the fragmenting 
zone 4. Similar to the feed apron 9, the discharging conveyor 51 is 
powered by drive sprocket 51D chain-driven by chain 51B, drive pulley (not 
shown) and running pulley 51R which, in turn, powers running sprocket 51O 
and laterally disposed spacer sprocket 51N positioned at the feed end of 
the machine 1. 
FIG. 14 depicts a screen lifting assembly (generally designated as 60) 
which permits a single operator to replace screen 43 without assistance by 
others. As mentioned, cradle assembly 30 is fitted with castors 31W which 
ride upon caster rails 16R disposed along inner frame 16. This permits 
screen assembly 30 to be removed from fragmenting zone and moved to a 
convenient open position for removing screen 43. The screen lifting 
assembly 60 includes trolley boom 61 equipped with boom mounts 63 which 
anchor and pin onto boom assembly mounts 65 secured to the discharge cover 
area of covering 18 laterally disposed above rails 16R. When using lift 
assembly 60, the operator simply unlatches cradle assembly 30 as shown in 
FIG. 11 and rails cradle assembly 30 to a position directly below boom 
anchor mounts 65. Boom 61 is then inserted via boom mount 63 onto anchor 
mounts 65 and secured thereto with lynch pins 63P. Jack 67 (e.g. two ton 
come-a-long) is secured onto boom 61 and lift chain 69. Screen 43 may then 
be lifted from cradle assembly 30, then trolleyed along boom 61 until 
clear of machine 1. By reversing the aforementioned procedure, a 
replacement screen 43 may be placed upon cradle assembly 30 and railed 
into operational or latched position as shown in FIG. 10. 
The rotor 42 is spin-balanced. The placement of teeth 41 and balancing 
provides a dynamically balanced fragmenting rotor 40 which, when used in 
combination with the striking bar 33 and screen 43, provides significantly 
improved efficacy in the processing of recyclable waste materials W. These 
features allow machine 1 to operate more effectively with less power and 
higher capacity than conventional waste recycling machines. 
FIGS. 5 and 6 show a top and side view of the hinging portion of the 
stripper plate assembly 15. The figures show the releasing means 35 for 
disengaging the cradle assembly 30 and adjustable clearance means 37 for 
adjusting the cradle to the desired waste fragmenting position. 
If desired, the machine 1 may include spiral flightings of feed idler 
pulley 9E and drive pulley 51D which may be respectively utilized to clean 
the underside of apron 9 and discharging conveyor. The boom assembly 
depicted in FIG. 14 shows in greater detail the trolleying features of the 
boom jack 67. FIG. 12 shows the external features of screen stop adjusting 
means 38 showing adjusting threaded rod 38R equipped with adjusting nuts 
for adjusting the clearance stop for screen 43. 
Reference is made to our provisional application 60/022,441 entitled the 
same as this application for which priority is claimed, and the presence 
in said provisional application of engineering drawings and prints.