Note: Descriptions are shown in the official language in which they were submitted.
32~
TWO WHEEL AGRICULTURAL FEED BAGGER
.
Description
Technical Field
This invention relates to an apparatus for
loading agricultural feed stock into expansible storage
receptacles or agricultural bags and more particularly to
an improved apparatus for more rapidly and more complete-
ly filling the storage receptacles or agricultural bags.
Background o~ the Invention
Horizontally expansible silage storage bags
have become known and used as an alternative to permanent
storage structures, such as barns or silos. Such storage
bags are desirable from an economical standpoint and are
advantageous in that they are easily loaded and the stored
material is readily accessible.
A currently existing apparatus for loading such
receptacles is disclosed in U.S. Patent No. 4,046,069 to
EggenmullPr et al wherein an apparatus for bagging silage
is shown. A loading channel supports an unfilled bag and
guides the silage from a press roll having spirally lo-
cated teeth about the outer periphery of the roll. Feed
stock is fed into a hopper where it is forced by a reci-
procating member into the press roll whose teeth force
the feed stock into the storage bag. A gate is held
against the closed end of the storage bag with cables
connected therefrom to a drum on the apparatus, which
drum has a brake arrangement applying tension to the
cables so that as the storage bag is filled the brake
will release the cable and the apparatus will move away
from the gate.
1243~
A modification of the Eggenmuller et al '068
patent is disclosed in U.S. Patent No. 4,337,80~ to John-
son et al wherein substantially the same apparatus is
provided except that the pass roll has randomly located
groups of teeth, each group having four teeth, about the
periphery thereof for forcing the feed stock into a trun-
cated triangular tunnel (as sectioned transverse to the
direction of movement of the feed stock) and then into
the storage bag. A feeder roll is rotated in the bottom
of a feed hopper to advance the feed stock into the press
roll. A disc brake arrangement is used to add the re-
sistance to the cable on the drum so as to pay out the
cable as the storage bag is filled. A sprocket drive
arrangement is employed to drive both the feeder roll and
the press roll.
In both of the prior art apparatus described
above the press roll is mounted in bearings on opposite
sides of the housing and, due to the nature of the wear
on the parts of the press roll, must be frequently re-
placed which necessitates almost completely disassemblingthe apparatus to remove and replace the press roll. The
spirally located single teeth of Eggenmuller '0~8 and the
randomly located groups of teeth of Johnson et al both
create unusually heavy loads on the drive apparatus for
the feed roller and must be operated at relatively low
speeds to avoid clogging or jamming thereof. Eggenmuller
et al '068 requires a reciprocating feeder in the hopper
where Johnson et al '805 requires a power driven feeder
roll to feed the material from the hopper into the feed
- 30 roller. In both cases the added movable parts of the
reciprocating member or of the feeder roll takes power to
operate and provides additional apparatus for potential
failure and service. In both prior devices the material
~2~3.~4~
had to be fed evenly across the full width of the appara-
tus otherwise the bag was filled unevenly causing pockets
and spoilage.
Both Eggenmuller et al '068 and Johnson et al
'805 require brake operating cables connected to a gate
at the closed end of the bag so that when the braking
force is exceeded by the pressed material in the bag, the
apparatus will move relative to the gate on the end of
the bag. The cables frequently rub the sides of the bag
causing bag punctures. It is difficult to rewind the
cable in a single layer on the drum. The bag must be
kept absolutely straight or the cable will cut into the
curved side of the bag and puncture the bag.
The present invention is directed to overcoming
one or more of the above enumerated problems.
Summary of the Invention
In accordance with the improvements of the
present invention, an apparatus is provided having a
housing mounted on a chassis supported on two wheels.
The housing includes a hopper, a passageway and a tunnel.
The hopper receiving feed stock and advancing it directly
into a press rotor in the passageway with the rotor hav-
ing pairs of spaced teeth about the periphery thereof.
Clean out bars extend from the housing into the open area
between the spaced teeth to strip the feed stock from the
teeth as the feed stock is forced through the more rec-
tangularly (in cross-section) shaped tunnel into the
collapsible storage bag carried by a molding channel
~ portion of the tunnel.
A power source drives the rotor at relatively
high speeds. Portions of the drive are immersed in oil
for cooling and l~brication. Flanges are provided on the
1~43~
q
rotor within the confines of the passageway ~f the hous-
ing so that the toothed portion o~ the rotor can be re-
moved and replaced or repaired without major disassembly
of the housing. The tunnel is specially shaped and in-
cludes side and back walls diverging from the passagewaywhereby a relatively short rotor with the pairs of teeth
and driven at a relatively high speed expands the feed
stock in all directions as it leaves the rotor area. The
feed stock is advanced rapidly through the shaped and
extended tunnel for guiding and packing the feed stock
into the bag with minimal air pockets in the feed stock.
srakes are provided on the wheels and are set
at a predetermined loading so that as the bag is filled,
the brake force is overcome and the apparatus is moved
forward relative to the bag. Appropriate conveying appa-
ratus is provided for the hopper to convey material dir-
ectly into the hopper.
The improved apparatus runs at a higher rate of
speed so as to fill the bag more rapidly and without air
pockets. The apparatus has a readily replaceable rotor
to reduce down time for substituting different rotors,
for service and for repair of the rotor. The apparatus
eliminates the cable drum and cables for applying a load
to the material in the bag thereby eliminating the pro-
blem of the cable puncturing the bag during filling. Theteeth on the rotor are in pairs whereby the rotor can be
run faster without clogging and without overloading of
the drive, resulting in a lower operating cost. The
loaded bag has substantially no air pockets thereby re-
~ 30 ducing spoilage while storing more feed stock in eachbag.
~Z~3~
Brief Description of the Drawings
Fig. l is a perspective view of the bag loading
apparatus of the present invention with an agricultural
bag in operative position thereon;
Fig. 2 is a broken away perspective view of a
wheel brake arrangement for use on the bag loading appa-
ratus of Fig. 1;
Fig. 3 is an enlarged bxoken away perspective
view of a portion of the hopper and passagewav of the
housing with an improved rotor in the passageway;
Fig. 4 is a perspective view of one end of the
rotor showing the flange connection between the r~tor and
the mounting shaft;
Fig. 5 is a partial cross-sectional view taken
along the lines 5-5 of Fig. 4;
Fig. 6 is a side partial cross sectional view
of the bag loading apparatus of Fig. l;
Fig. 7 is an enlarged partial cross sectional
view showing the relationship between the rotor and the
clean out bars;
Fig. 8 is a perspective view of the front por-
tion of the housing of the apparatus;
Fig. 9 is an enlarged broken away partial view
of the bag mounting mechanism as mounted on the housing;
Fig. lO is a broken away plan view of the bag
loading apparatus of Fig. l;
Fig. 11 is a partial broken away side perspec-
tive view of the actuating cable for the feed stock con-
veyor; and
~ 30 Fig. 1~ is a brokPn away cross sectional view
of the pivot for the feed stock conveyor as mounted to
the frame of the housing.
~L2~3~
-- 6 --
Description of the Preferred Embodiment
Referring now to the drawings, and in particu-
lar Fig. 1, a feed stock compacting and loading apparatus
20 is shown connected to a partially filled silage recep-
tacle or ~ag 22 supported at one end by a back stop 24staked and supported by props on the ground 26. The
backstop may be in the form of a blank wall or the end of
another bag 22. A tractor, only one wheel 28 of which is
shown, is connected through a tongue 29 and power take-
off 30 to the compacting apparatus 20. The power take-
off 30 serves to drive a rotor 32 while the tongue 29
connects the apparatus to the tractor ~or use in moving
the apparatus or for use in transmitting movement of the
apparatus to the tractor. Feed stock such as corn, hay,
alfalfa, and the like is fed to a self-contained conveyor
34 which, in the illustrated form, feeds the feed stock
from the side of the apparatus in to a hopper 36, which
hopper is part of a housing 40 of the compacting appara-
tus 20.
Referring more in detail to the conveying appa-
ratus 20, the apparatus comprises a housing 40 affixed on
a frame or chassis 42, which is supported by wheels 46
mounted on stub axles 44 extending sidewardly from the
opposite sides of said frame. WheeL brakes 48 are opera-
tively associated with each wheel and as shown in Fig. 2,
the brakes are connected for actuation through conduits
50 connected to a hydraulic pump 52 mounted on the frame
adjacent one of the two wheels. In Fig. 1 the pump 52 is
mounted to the frame just inside the wheel 46 on the
right side of the apparatus. A handle 54 is pivotally
mounted on the hydraulic pump 52 which when actuated,
loads the brakes to a predetermined setting as determined
by a reading on the gauge 56 connected to the hydraulic
pump.
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-- 7 --
The housing 40 is comprised of the hopper 36
connected to a passageway 58 which opens into a tunnel
60, all supported on the chassis or frame 42. The hopper
36 has a front wall 64 connected to a cross beam 66 on
the frame 42, has side walls 68 and 70 and a rear wall
72. The rear wall is sloped and is tangent to the curved
bottom wall 74 of the passageway 58. As can be seen in
Figs. 6 and 7, the bottom wall 74 curves slightly upward-
ly forward of the axis of the rotor and terminates at the
entrance to the tunnel 60 which results in a short fall
off from the bottom wall 74 of the passageway to the
bottom wall of the tunnel 60. The side walls 68,70 close
the ends of the hopper and the ends of the passageway
and, in the passageway IFig. 3), have reinforcing bearing
plates 76 affixed thereto with an aperture 78 therethrough
through which a stub shat 80 and a bearing sleeve 82
extend (Fig. 5~. The bearing sleeve 82 on each end of
the rotor is positioned around the shaft 80 and is welded
to a flange 84 disposed on the inside of the each wall
68,70, respectively, of the passageway 58. The stub
shaft 80 on the left end of the passageway extends freely
through the bearing plate 76 and wall 68 and in the pres-
ent form has no additional elements affixed thereto. The
stub shaft 80 on the right side of the passageway extends
through the bearing plate 76 and wall 70 and has a sprock-
et wheel 86 rigidly attached thereto exterior of the
passageway 58. Between the flanges 84 is affixed a tube
88 of the rotor 32 with the tube having flanges 90 welded
on either end thereof. Bolts and nuts 92 pass through
- 30 lugs on the flanges 84 and 90 for affixing the rotor 32
to the stub shafts 80. The hopper is constructed to feed
the feed stock by gravity directly into the passag~way 58
and rotor.
~3;~
-- 8 --
Affixed around the periphery of the tube 88 are
a plurality of pairs 92 of knives or teeth 96 which teeth
have a concave surface on the trailing edge thereof and a
convex surface on the leading edge thereof. Each tooth
96 of a pair of teeth is spaced from the other tooth 96
of the pair a preset amount. In the illustrated form of
the invention, the pair 96 of teeth on one side of the
tube 88 are diametrically opposite a similar pair of
teeth on the opposite side of the tube. It is to be
understood that the teeth do not have to be diametrically
opposite each other, although there is some advantage
thereto. One tooth 96 of one pair 92 of teeth lies in a
plane transverse to the axis of the tube and is spaced
from the plane of the adjacent but circumferentially
displaced tooth of the next axially located pair of teeth
by an amount equal to the spacing between the two teeth
of each pair of teeth. The teeth all lie in planes that
are transverse to the axis of the tube and which planes
are all equally spaced apart along the axis of the tube.
The pairs 92 of teeth are in rows, with the axes of the
rows parallel to each other and parallel to the axis of
the rotor. In the illustrated form, there are a total of
six rows of pairs of teeth, with the axis of each row
being spaced approximately 60 from the axis of the ad-
jacent row so that, as can be seen in Fig. 6 from the endof the rotor, there are six equally spaced rows of teeth
about the periphery of the rotor. As illustrated, there
are 30 pairs of teeth equalling 60 teeth on the rotor but
more or less number of pairs and number of teeth may be
provided depending on the feed stock being stored and the
speed and horsepower of the source of power being used to
drive the system. As an example, the owner may find it
necessary to change tractors while filling a bag. If he
~L3~
9 _
is going to less horsepower, he can install a rotor with
fewer pairs of teeth 96 and resume bagging with minimal
loss of time. Substituting a larger tractor will dictate
using a rotor with more teeth.
As can be seen in Figs. 3 and 4, diametrically
opposite teeth 96 are secured as by welding to the shaft
80 side of the flanges 88 with mating teeth 96 secured to
the inner sides of the flanges 90 and the tube 88. The
result is pairs of teeth spanning the flanges 84,90 with
the spacing between the teeth of each pair equaling the
space between the teeth 96 of all other pairs. By having
the pairs 92 of teeth 96 on the flanges on the ends of
the rotor 32 eliminates a problem area in the prior art
where feed stock was not processed by the rotor at the
ends of the rotor resulting in bunching up of feed stock
and/or less than adeguate flow of feed stock resulting in
air pockets on the sides of the bag. In addition, the
prior art devices required more time to fill the bag.
The cross beam 56 of the frame 42 between the
hopper 36 and tunnel 60 has a plurality of equally spaced
apart clean out bars or prongs lO0 projecting downwardly
and slightly rearwardly therefrom into alignment with the
space between the pairs of knives or teeth 96 on the
rotor 32. The bars or prongs 100 are welded to the under-
side of the box shaped cross beam 66 with a protectiveplate 102 projecting down over the junction between the
prongs lO0 and the cross beam 66 so as to provide a slight
overhanging wall between adjacent prongs and to support
the prongs in proper alignment between the pairs of teeth.
- 30 The leading edge of each bar or prong lO0 terminates in
closely spaced relation to the outer surface of the tube
88 and is located slightly forward of the front face of
the tube 88. As the rotor 32 rotates, the pairs of teeth
~Z43;~43L
-- 10 --
sweep past the adjacent prongs 100 with a prong extending
between each pair of teeth to sweep the feed stock from
the teeth of the rotor. The plate 102 is in close prox-
imity to the path of the knives or teeth 96 as they sweep
past the plate, helping to clear the feed stock from the
rotor and to keep it clean. The bars or prongs 100 and
plate 102 align with the back wall 103 of the tunnel 60
for a purpose to be explained hereinafter.
The tunnel 60 is made up of an expanding cham-
ber 62, a forming chamber 63 and a guide portion 65. The
expanding chamber 62 has an upwardly sloping back wall
103 with diverging side walls 104 and 106 connected to
the outlet or mouth 107 of the passageway 58. The back
wall 103 forms an angle of approximately 88 with the
longitudinal axis of the apparatus and aligns smoothly
with the front face of the cross beam 66. The bac~ wall
103 and the side walls lD4,106 merge into a short arcuate
shaped top wall 112. A bottom wall 114 is supported on
the frame and is attached to the bottom edge of the pas-
sageway 58. The respective side edges of the bottom 114are shaped gradually into a connection with the side
walls 104 and 106. The leading edge 110 of the expanding
chamber 62 ioins into the forming chamber 63 which has
side walls 116,118 which slope gradually upwardly and
inwardly as they approach the upper portions of the side
walls and form into a dome-shaped top wall 120. The
cross-section of the forming chamber 63 transverse to the
direction of flow of the feed stoc~ approaches a rectan-
gle with the short side walls 116,118 sloping slightly
inwardly and with the top wall bowed slightly upwardly in
the midportion. As best seen in Fig. 8, the forming
chamber 63 has curved side corners as it merges into a
3~1
flat bottom wall 121 which is in alignment with the bot-
tom wall 114 of the chamber 62. Beginning at po~nts just
above the curved corners of the forming chamber 63 is a
guide portion 65 which extends from the lower reaches of
the two side walls 116,118, and follows the contour of
the side walls up through and over the dome-shaped top
wall. As shown in Figs. 7 and 10, the guide 65 is sloped
slightly inwardly toward the axis of the apparatus which
tends to compact the feed stock as the feed stock exits
the tunnel 60. The agricultural bag 22 is puckered,
pleated or bunched so that initially it is relatively
short in longitudinal dimension. With the pleating
threaded over the outer surfaces of the forming chamber
63 and guide 65 of the tunnel 60. An extension 123 is
conn~cted to the rear edge of the outside of the forming
chamber 63 to provide added support for the full extent
of the bunched up bag 22. The rear edge of the agricul-
tural bag is resiliently secured to the tunnel 60 and
extension 123 by means well known in the art.
Pivotally mounted on spaced lugs 126 extending
downwardly from the bottom wall 114 of the tunnel 60 is a
support pan 128 which fits below the pleats in the bag 22
and supports and retains the bag 22 on the tunnel 60. A
crossbar 130 is secured to the forward edge of the sup-
porting pan 123 with the outer ends thereof extending
beyond the edges of the pan 128. An o~ercenter actuator
131 is pivoted to support arms 132 attached to the frame
42 on opposite sides of the tunnel 60. Each actuator has
a spring 134 connected to the cross bar and connected
~ 30 through a chain 136 to a pivot 138 on an angled handle
139 which handle is pivoted at 140 to the support 132.
As can be seen in Fig. 9, when the lever 134 is pi~oted
forward to the dotted line position, the supporting pan
3~4::~
- 12 -
128 is lowered so that an agricultural bag 22 can be
threaded over the guide 65, shaping portion 63 and ex-
tension 123 of the tunnel. With the lever 134 pivoted to
the solid line rearwardly extending position of Fig. 9,
the spring is in tension and pulls the pan resiliently
against the lower portion of the pl~ated bag to resili-
ently support the bag on the tunnel 60.
In practice, when a new bag 22 is assembled
with the apparatus by threading the open portion of the
ba5 over the shaping portions 63 of the tunnel, the
closed end of the bag will be in close proximity to the
mouth of the guide 65. Pivoting the actuator 131 into
the tensioning position of the spring, will resiliently
support the bag on the tunnel. Prior to starting the bag
lS loading operation, a gate 24, which is comprised of a
frame 141 supporting resilient interlaced straps or net-
ting 142 therebetween, may be staked to the ground using
stakes 144, a prop or brace 146 extends into engagement
with the top crossbar of the gate and is likewise staked
to the ground so as to support the gate in an upright
position in close proximity to the closed end of the
agricultural bag 22. The bag may be backed by a wall or
by the closed end of an already filled bag.
The power take-off 30 from the tractor is con-
nected into a gear box 150 mounted on the frame 42 of thehousing. The gear box is conventional and has a gear
ratio of 3:1 and drives an output shaft 152 extending
from the gear box through an appropriate bearing and seal
153 into a reservoir 154 mounted on the side wall 70 of
~ 30 the hopper. A sprocket 156 is keyed to the outer end of
the shaft 152 and drives a chain 158 which in turn drives
the sprocket 86 keyed on the outer end of the stub shaft
80 of the rotor 32. A chain guide 162 is mounted inter-
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- 13 -
mediate the sprockets 156,86 to control the tension and
to increase the driving contact between the chains and
the sprockets. The reservoir 154 has an inspection and
filling panel 164 on the side thereof which permits ac~
cess to the sprockets and the chain. The level of oil is
maintained in the reservoir sufficient to submerse parts
of the sprockets 156,86 and the chain 158 so as to pro-
vide lubrication thereto and to afford a degree of cool-
ing of the parts. The relative size of the sprockets
156,86 is such as to provide a further 3:1 gear reduction
between the input shaft 152 and the rotor 32. The effect
of the gear box and sprockets is to reduce the speed of
the power take-off 30 approximately 9:1 in driving the
rotor 32 resulting in a speed of approximately 60 revolu-
tions per minute when the power take-off runs at 540 rpm.
The speed of the rotor can be controlled within the range
of 40 to 80 revolutions per minute. Prior systems re-
duced the speed from the power take-off to the rotor so
that the rotor was driven at approximately 30 revolutions
per minute and within the range of 28 to 36 revolutions
per minute.
Different systems can be employed to feed the
feed stock into the hopper 36. In the illustrated embod-
iment, a conveyor 39 is pivotally and slidably attached
to the frame 42 and hopper 36 of the apparatus so that in
operating position the flight of the conveyor will convey
material dumped into the input end and move the material
up the conveyor and into the open top of the hopper 36.
The conveyor may be driven by a hydraulic motor power~d
- 30 through hydraulic fluid from the tractor through the
conduits 166 extending from the tractor. The frame 167
of the conveyor 34 is pivoted on the frame 42 of the
apparatus by means of the trunnions 168 on the frame 167
12~324~
- 14 -
and the lugs 170 on the frame 42. A pin 171 passes
through the aligned openings in the trunnions and lug so
that the conveyor may be pivoted from one position to
another as required. The conveying portion of the con-
veyor is mounted on a structure 172 that can slide intracks 174 on the frame 167 relative to the hopper of the
apparatus. A cable 179 is secured to the frame 42 at
180, passes through a pulley (not shown) on the undersur-
face of the structure 172 for the conveyor, doubles back
and passes around a pulley 182 on the frame 42 and tra-
verses a path around a pulley 18~ located in the cross
beam 66 and passes between the hopper 36 and the tunnel
60 with the cable passing around a drum 185 supported
between a pair of supports 186 on the frame of the appa-
ratus. A crank 188 and latching arrangement are providedon the drum whereby releasing the latch and turning the
crank will slide the conveyor 34 from a general engaging
position into a position substantially overlapping the
hopper with the input end of the conveyor raised off the
ground by an amount that will permit easy transport of
the apparatus without draggin~ the conveyor on the ground.
In a typical loading apparatus, the length of
the passageway (side to side) is approximately 60" which
feeds into the tunnel 60 having the expanding section 62
expanding the opening to 100" width. The expanding cham-
ber 62 has its back wall risiny at an angle of approxi-
mately 88 with the longitudinal axis of the apparatus
which back wall merges into a small radius curvature at
the top. The dome shaped top is wider and flatter, side
- 30 to side than prior tunnels that had a tendency to be more
triangular in cross-section (narrow at the top). The
forming chamber matches the cross section of the leading
lZ~3~
-- 15 --
edge of the e.~panding chamber. The distance from the
leading edge of the passageway to the leading edge of the
forming chamber is approximately Z4" which when added to
the 12" guide 65 makes approximately 36" back to front
and with a wider and flatter dome-shaped top produced
more uniform compaction of the feed stock and substan
tially eliminated the lumps and air pockets prevalent in
the prior art short rear to front tunnel. The longer
tunnel with the substantially straight back wall and
longer shaping chamber 63 allows the feed stock exiting
the rotor to fully fill the expanding chamber 62 and the
shaping chamber 63 throughout the full cross section
before it enters the bag. Initially, the tunnel and bag
end fill up completely whereupon pressure from the feed
stock forced into the tunnel develops in the tunnel which
builds up until the brake force on the wheels 46 is over-
come whereupon the loading apparatus is inched rearward.
The rearward movement of the loading apparatus causes the
tunnel to move rearward of the feed stock that has filled
the tunnel and the end of the bag with a new portion of
the bag being pulled off the outer surface of the tunnel
and encasing the shaped and compacted mass of feed stock.
The new front to rear expanding shaping and guiding por-
tions of the tunnel contribute substantially to the im-
proved results.
The devices such as made under the Johnson etal Patent 4,337,805 had a substantially circular rear
wall and only about a 6 n horizontal top which did not
permit the feed stock to fully compact and fill up the
~ 30 tunnel before it entered the bag. The feed stock had to
be uniformly fed into the beater bars and rotor to get
any degree of uniformity to the mass of feed stock being
forced into the bag. Frequently, air pockets developed
12~2~
- 16 -
resulting in heat (due to the organic nature of the feed
stock) which caused the feed stock to decompose. Absent
the air pockets, as now provided by the improved appara-
tus, reduces or eliminates heat since there is no source
of oxygen to encourage a chemical reaction. No heat, no
Butyric acid formation (spoilage) and no vitamin A loss.
The shorter rotor 32 (60") with the pairs 92 of
teeth 96 means that less feed stock is grahbed by each
pair and moved through the passageway 58. The less mater-
ial grabbed the less work re~uired to move it. The rotorin the improved apparatus is run faster (70 rpm vs. 30
rpm) and since it is shorter in length (66" vs. 100") it
requires less horse power. The prior art loading appara-
tus required 70-120 horsepower to drive the 100" rotor at
28 to 36 rpm. The improved apparatus requires on the low
side of 60-100 horsepower to achieve the same loading
capacity as the prior art. The lower required horsepower
saves fuel and costs. The pairing of the teeth or knives
96 works on smaller quantities of material at a faster
rate to save power while at the same time providing a
better bagged feed product with less chance of spoilaye.
The higher speeds reduces component wear and stress con-
siderably thus increasing the life of the parts while
decreasing maintenance and down time expense. In prac-
tice it has been found that more or less numbers of pairsof teeth can be provided on the rotor for use with parti-
cular types of feed stock. For instance, if the number
of pairs of teeth are doubled from 30 pairs to 60 pairs
the mixing action and capacity is twice what it was be-
fore.
With the higher rpm ~60 vs. 30), the velocityof the teeth is almost twice as fast, thus striking the
material almost twice as hard. The greater impact flat-
~Z~3~- 17 -
tens the material even more which not only enhances thecompaction but quite probably increases the tonnage forced
into a bag as the flattened material requires less space.
