Note: Descriptions are shown in the official language in which they were submitted.
(1)
B~:,KGROUNI) Ol~ T~ll'' INVI~'NTION
~ield ol tlle Invention
I`he invention relates to an apparutus aI)(l metho(l for
loa(iill~ loosc matcrial onto A (!onveyor, ror subsecluent filling of a conve--
yance, particulally for use in uIl(Ierground excuvatiorls when muckinlJ.
10 Prior ~rt
In unclerground exc~avation, rock which has heen fragmented
by blasting is removed from tlle working ~rea during a "muckingJ" operation.
The rock or tnuck pile commonly has a steep angle of repose which can be
15 difficult to penetrate with u bucket or other irnplement used for removin~
the muck. If a louding apparatus carryir-~,r the bùcket or equivalent utilize.;
tractive force from ground contactirlg meaIls~ eg. wheels or crawler tracks,
which can be termed mobile mounting means, rapid wear of the mounting
means and power train producing the tractive effort res~lts due to scuffin~
20 and heavy forces incurred.
Loading appalat-~s ~or muckin~ operations commonly in-
clude a conveyor assembly having a gathering device at one end, for example
a buc~cet, a backhoe, gathering arms or a scraper, which is adapted to load
25 material onto a fixed apron or hopper for feeding onto a low~r portion
of the conveyor. The gatheling deviees sometimes require a high degree of
operator skill, usually suffer frorn high wear rate and low capacity and, if
used with an articulated boom9 require some considerable head room for
operation which can be inappropriate in a low head room area. The apron of
the eonveyor assembly is forced into the muck piie by driving the apparatus
forward, resulting in the rapid wear of the àrive train flS outlined above, and
also in wear of the gathering devices. (,ommonly, excessive undulations or
urldesirable gradierlts Or the ground supporting the apparatus, and resilience
(2)
of tires or suspension result in poor control of the scraper, bucket or apron,
with consequent poor control of the plane of the resulting road bed under the
rnuck heap. The scraper or bucket of the gathering device usually loads the
conveyor in a series of discrete feeding strokes interspersed with non-
productive recovery strokes, and thus material is fed intermittently onto the
apron reducing potential production.
Attempts have been made to reduce the intermittent
nature of feeding of material onto the conveyor by use of auxiliary or
10 essentially continuous feeder devices designed to feed material onto the
conveyor at a more constant rate than buckets, etc. Some devices use
vibrating or reciprocating fingers adjacent the leading portion or apron of
the conveyor to loosen material in the muck pile to facilitate entry of the
apron or penetrating lip as the conveyor is advanced into the muck pile.
15 Many of these devices have an excessive number of parts which are exposed
to wear when disturbing a muck pile, and it is felt that they would not be
appropriate for material normally encountered in the harsh enviroment OI
mucking operations in hard rock excavAtion~ Devices oî these general types
are shown in United States Patents ~1,855,998, (Shannon); ~1,903,672
20 (Hauge); #1,414,398 (Dennis) and #lS878,037 (Vodoz). Other loading devices
having a vibrating trough or plate adjacent the leading portion of the
conveyor have been used in coal mining in ~!ombination with vibrating or
shaking conveyors. The plate is mounted directly on the conveyor to shake
therewith9 but such devices would be inappropriate in hard rock mining, and
25 furthermore, are limited by a very shallow angle of operation, thus requiringexcessively long conveyors to attain a reasonable discharge height onto a
waiting conveyance.
SUMMARY OF THlE INVENTION
The invention reduces difficulties and disadvantages of the
prior urt by providing a loading apparatus which enables a pentrating means
at a forward end of a conveyor assembly to be fed essentially continuously
into a muclc heap for a relatively long working stroke, without the use of
(3)
complex and separate gathering devices, thus increasing productivity and
decreasing maintenance problems. During the working stroke, material from
the heap is distributed onto the conveyor in an essentially continuous manner
as the conveyor is advanced into the muck h~ap. The apparatus can secure
5 itself to stationary surroundings to provide an anchor so that the penetratingmeans can be forced into the muck pile by advancing means reacting against
the anchor~ thus eliminating necessity for the tractive ef fort which is
normally required, and reducing wear of wheels or crawler tracks and the
drive train components that are usually used.
A mobile loading apparatus according to the invention has a
body and a conYeyor assembly mounted on the body. The conveyor assembly
is adnpted to transport material from a front portion of the conveyor
assembly to a rear portion thereof along a longitudinal conveyor axis. The
15 apparatus has advancing means cooperating with the conveyor assembly to
cause essentially axial movement of the conveyor assembly as a reaction to
force from the advancing means. The apparatus also has penetrating means
mounted adjacent the front portion of the conveyor. The penetrating means
is adapted to be rotationally oscillated about a horizontal trensverse
20 penetrator axis disposed normally to the longitudinal axis to facilitate
penetration of the material to be loaded onto the conveyor assembly.
Anchoring means can be provided to cooperate with surroundings adjacent
the apparatus to resist reaction to penetration forces generated on the
penetrating means. When the advancing means cooperates with the
25 anchoring means to force the penetrating means into the material to
facilitate loading of the material onto the conveyor, this penetration is
independent of tractive effort from wheels or crawler tracks. The front
portion of the conveyor nssembly preferably is hinged to the rear portion for
swin~ing about a horizontal transverse conveyor axis, and preferably forward
30 elevating means extend between the front portion of the conveyor assembly
(~)
and the body so ttlat actuation of the elevating mearls swings the front
portion about the transverse conveyor axis and r aises or lowers the
penetrating means. In one embodirnent, in which the mobile mounting means
are wheels running on railroad tracks, the anchoring means can be releasably
5 engaged to the rigid structure adjacent the apparatus, eg. the traclcs~ and
the advancing means extend between the anchoring means and the body so
that, when actuated, the apparatus rolls towards the material to be loaded,
thus forcing the penetrating means into the material. Tn a second
embodiment which is mounted on endless crawler tracks~ the conveyor
10 assembly has a conveyor supporting frame carrying the conveyor, and the
supporting frame i5 movable relative to the body along the longitudinal
axis of the conveyor assembly. In the second embodiment, the anchoring
means secures the body itself to stationary surroundings, and the advancing
means rnoves the conveyor assembly relative to the body. In each case, the
15 penetrating means is guided in a controIled direction by either the rails
carrying the body, or the body of the apparatus which supports the conveyor
assembly RS it moves relative to the body. In each case, the force to drive
the penetrating means into the muck heap is transferred through the body
and anchoring means to the surroundings, and thus scuffing and drive train
20 wear is essentially eliminated. In some embodiments, particular modes of
oscillation of the penetrating means can be selected to suit particular
loading conditions. The penetrating means can be raised so as to penetrate
the muck heap at a higher position, if so desired. Also, in the rail mounted
first embodiment, the conveyor assembly can be mounted for swivelling
about a vertical swivel axis to load material disps)sed to one side of the
apparatus.
A method accordin~ to the invention is for use with a
loading apparatus having a body and a conveyor assembly mounted on the
30 body and adapted to transport material from a front portion of the conveyor
assembly to a rear portion thereof along a longitudinal conveyor axis. The
(5)
front portion has a penetrating means and the method is characterized by
advancing the penetrating means into the material to be loaded~ and, when
required, simultaneously rotationally oscillating the penetrating means about
a horizontal transverse axis disposed normally to the longitudinal axis to
5 faciliate loading of material onto the conveyor. The method is further
characterized by, prior to advancing the penetrating means into the material
to be loaded, anchoring the body relative to the surroundings with anchoring
means and forcing against the anchoring means to overcome resistance to
penetration OI the material. If desired, prior to advancing the penetrating
10 means into the material to be loaded, the method can be further
characterized by swinging the conveyor assernbly about a vertical swivel
axis so as to approach material disposed to one side of the conveyor
assembly.
A detailed disclosure following, related to drawings, des-
cribes preferred apparatus and method according to the invention for several
embodiments7 the invention being capable of expression in apparatus and
method other than those particularly described and illustrated.
DESCRIPTION OF THE DRAWINGS
Figure 1 is a sirnplified fragmented top plan view of a rail mounted
2S loading apparatus according to the invention, shown on a
portion of a movable rail bed, with portions of the ap-
parutus shown broken away for clarity,
Figllre 2 i9 a sirnplified fragmented side elevation of the apparatus
of Figure 1, drawn at a larger scale than Figure 1, the
apparatus being shown in full outline in a lowered position
and partially in broken outline in a raised position,
t6)
Figure 3 is a simplified fragmented transverse section generally on
line 3-3 of Figure 2, showing swivellable mounting means,
Figure 4 is a simplified fragmented transverse section generally on
line 4-4 of Figure 2, showing swivelling means,
Figure 5 is a simplified front view of a rail clamp showing
cooperation with a rail,
Figure 6 is a simplified longitudinal section generally on line
6-6 of Figure 5,
Figure 7 is a simplified top plan view of the rail clamp,
Figure 8 is a simplified fragmented section genera:lly on line
8-8 of Figure 5,
Figure 9 is a simplified top plan of a second embodiment of the
invention, shown in full outline in a lowered and retracted
position, and partially in broken outline in extended
positions, with anchoring means thereof shown in broken
outline extended,
Figure 10 is a simplified fragmented side elevation of the second
embodiment of Figure 9, drawn at a larger scale than
Figure 9, the apparatus being shown in full outline with a
portion retraeted, and partly in broken outline with the
portion extended and/or raised,
Figure 11 which appears on sheet 2 of the drawings, is a simplied
fragmented section generally on line 11-11 of Figure 10
showing an advancing cylinder and a portion of the body
and conveyor assembly,
l~Y)14~3
~7)
Figulel2 which appears on sheet 2 ol the dr~wing~, is a ~simplified
transverse section on lin~ 12-12 of Yigure 10 showing
alternate anchoring o; levelling me~ln~i,
Figure 13 i~i a fragrnented, partly-sectioned, side view of the
penetrating lllean~; of I~igure 1, with an alternative tflndem
oscillating cylinder assembly,
Figure 14 is a fragrnented, partly-sectioned, simplified side view of
the tandem cylinder assembly of Figure 139
Figure 15 is a simplified electrical/hydraulic schematic of a clrcuit
to actuQte the ¢ornpound assembly of Figure 13,
15 Figure 16 is a fragmented, simplified side elevation of a third
embodiment of an oscillating cylinder and adjacent
conveyor structure,
Figure 17 is a fragmented, simplified partial longitudinal section of
ao oscillating means associated with the thild embodiment, as
seen on line 17-17 of Figure 18,
Figure 18 is fra~mented simplified transverse section on line IB - 18
of Figure 17
DETAILED DISCLCISURE
Figures 1 through 4
Referring to Figures 1 and 2, a rail rnounted loading
apparatus 10 accordin~ to the invention is shown supported on a pair of
spaced rails 12 of a railroad track carried on a movable rail platform 14
whîch has a forward end 15. The platform 1~1, which cnn be of the type
31
~)
de.scribed in Canadian Patent #719,987, is supported on the ground 16 and, by
known means, is advarlced in direction of an arrow 17 towards a muck pile or
loose material to be excavated not shown. The rails 12 are securely fixed to
the pletform 14 to withstand penetration forces as will be described, and if
the platform is not used, alternative means OI securely fixing the rails is
5 reqllired.
The apparatus 10 has a body 20 supported on Eront and rear
wheeled bo~ies 22 and 23 respectivly, each bogie carrying two pairs of
flanged wheel~, severally as, adapted to engage the rails 12. The wheels 25
10 and associated bogies serve as mobile mounting means for ~uL,po.lin~ and
permittin~ movement ol~ the body on a supporting surface, namely the rails.
The apparatus has a ~onveyor assembly 27 mounted on the body and adapted
to transport mat~rial from a front portion 29 of the conveyor assembly to a
rear portion 30 thereof along a longitudinal conveyor axis 32. The conveyor
15 assembly has a conveyor supporting frame 34 which is divided into front and
rear conveyor frames 35 and 36 which are hinged together at a horizontal
transverse conveyor hinge axis 38. Thus, the front portion of the conveyor
assembly is hinged to the rear portion thereof for ~ ing ebout a hinge at
the hinge axis 38. The c~,..veyor assembly also includes a chain conveyor 40,
20 in which four endless parallel eonveyor chains, shown in broken line, extend
around front and rear sprocke$ shafts 41 and 42 respectively journalled on
the rsspective conveyor portions, pass over idlers, not shown, and are driven
by chain trasmission drive means 45 cooperating with the chains as they pass
around the rear portion. A chain conveyor is preferred for heavy duty work
25 and steep conveyor ~ngles, but i~ desired a cleated belt conveyor or other
means can be substituted.
Parallel elevating cylinders 47 and 48 extend between the
front portion 29 of the conveyor assembly and the body 20 ancl serve as
30 elevating means so that, when actuated, the front portion swings about the
transverse conveyor axis 38 and raises or lowers the portion 29~ Connections
~3~
~9)
of the cylinders 47 and 48 to the front portion 29 and the body 20 are
common hinge connections to permit swivelling of the conveyor as will be
described. The cylinders 47 and 48 serve as forward elevating means
extending between the front portion and structure associated with the rear
5 portion, in this instance the body. A penetrating means 50 according to the
invention is hinged adjacent an extreme forwarcl end of the front portion of
the conveyor assembly for limited rotation about a horizontal transverse
penetrator axis 53 which is disposed normally to the longitudinal conveyor
axis 32 and is also concentric with an axis of rotation of the sprocket shaft
10 41. The penetrating means 50 is a shallow wedge-like apron or shovel that is
forced into the muck pile and has a reinforced penetratol~ tip 52 to ~esist
wear as it is forced into the muck pile. The penetrating means is described
in greater detail with reference to Figure 13. The penetrating means also
has upwardly extending arms 57 and 58, and a pair of spaced parallel
15 oscillating cylinders 61 and 62 extend from the arms 57 and Sû respectively
to interconnect to brackets 63 and 64 respectively of the front portion. It
can be seen that actuation of the oscillating cylinders 61 and 62 acting on
the arms 57 and 58 swings the penetrating means from a datum position
shown at 66 which is an extension of an upper surface of the conveyor
20 through upper and lower angles 67 and B8 which can be about 85~ and 30
respectively. Clearly, the angles 67 and 68 are variable and can be zero9
depending on the location of the penetr~ting means relative to fixed rock
and to the front portion 29. The means 50 can QlSO be made to oscillate at
particular frequenci~s through relatively small angles as will be described.
Wi~h reference aLso to Fieures 3 and 4, the body 20 has chassis
members 70 and 71 to which the front and rear bogies 22 arld 23 are
swivellably connected in a normal manner as for rail mounted carria~es.
The body also has an outer frame 74 connecting the chassis members which
~ carries the conveyor assembly 27 and structure associated therewith. Thus,
the outer frame 74 carries a power plant 73 for moving the apparatus along
the rails as required, and also ~or powering the conveyor ass0mbly 27 and
actuatirlg the various hydraulic and electrical components. The member 71
(10)
and the bogie 23 are mounted for relative swivelling movement
therebetween and are coupled together through ~ swivel bearing assembly 77
having a swivel axis 78 ag seen in Figure 3. As seen best in Figures 1 and 4, a
swivel cylinder 79 extends transversely betw,een a central portion 76 of the
body 20 and the outer frame 74 and is adapted to swing the outer frame
5 relative to the bogies about the swivel QXiS 78. The bogie 22 is connected to
~he central portion 76 of the body 20 by a bogie swivel bearing 80; and a
cylinder body 81 of the cylinder 79 is connected by trunllion mounts to the
portion 76. The chassis member 70 has a plate~like horizontal base with a
rectangular opening 69 to aecept the central portion 76 therein as a sliding
10 fit. The opening 69 is of sufficient size to provide clearance for r~lative
limited lateral swinging movement o~ the portion 76. As the combination of
the frame 74 and the conveyor assembly 27 is swung about the swivel axis
78, the front portion 29 swings between limits 2g.1 and 2~.2 and the rear
portion 30 swings between limits 30.1 and 30.2 as shown in Figure 1. If
15 necessary, stabilizers, not shown, can be provided to extend downwardly
from outer portions of the frame74 toengagethe~platformto prevent over
turning of the apparatus when the upper portion approaches the limits of
swinging relative to the ch~ssis. Thus, it can be seen that the conveyor
assembly is mounted on the body for limited lateral swinging about an
20 essentially vertical swiYel axis so flS to permit collection of materi~l
disposed to one side of the front portion of the eonveyor when in a central
position.
An advancing cylinder 82 has a cylinder upper end con-
nected to a bracket 83 connected to the body 20 and an extensible and
retractable piston rod 84 connected to a releasable rail clamp 85 which can
be ¢lamped onto an ~djac~nt rail 12 or adjacent rail platform structure. Any
clamp of sufficient gripping force can be used, and is preferably operated
remotely. A lift cylinder 88, broken outline, extends between the advancing
30 cylinder 82 and the body so as to raise the rail clamp 85 when required, so as
(11)
to avoid interference with obstructions adjacent the ground, and structure
associated with the rail when the apparatus 10 is mobile. A similar
advancing cylinder 90, and respective lift cylinder, not shown, are provided
on an opposite side of the body to engage the opposite rail or equivalent with
a similar rail clamp 91. The advancing and 1ift cylinders are connected to
5 respective structure through partial universal joints or equivalents to permit limited lateral and vertical swinging of the cylinders
It can be seen that, when the two rail clamps are clamped
on appropriate rails, and the advancing cylinders 82 and 90 are retracted,
10 the apparatus 10 is moved in direction of the arrow 17 so that the penetrating
means 50 is forced into the muck pile, and as will be described, when the
rneans 50 is oscillated, material is fed at relatively low energy requirements
onto the conveyor. The apparatus is thus moved forwardly independently oî
tractive effol t from the wheels, and thus the wheels may
15 freewheel while the advancing cylinders are actuated, thus eliminating
scuffing and drive train wear . It can be seen that the rail clamps 85 and 91
serve as anchoring means which are adapted to cooperate with surroundings
adjacent the apparatus, that is to releasably engage rigid structure, ie. the
rails9 so as to resist reaction to penetration forces generated on the
~0 penetrating means, or in other words~ to permit the advancing means to
force against the anchoring means to drive the penetrating means into the
muck pile. The advancing cylinders 82 and ~0 are seen to be extensible and
retractable means extending between the anchoring means and the body and
serve as advancing rneans cooperating with the anchoring means to force the
25 penetrating means into the material to be transported onto the conveyor,
but equivalent advancing means could be substituted. In this p~rticular
instance, the wheels are adapted to run on tracks, preferably on a movable
rail platform, and the anchoring means is a releasable rail clamp adapted to
engage at least one of the rails or tracks, but clearly, eguivalent wheels and
30 complementary tracks, or equivalents can be substituted, l,vith other means
to permit the anchoring means to engage non-moving or rigid surroun~ings.
(12)
Figures 5 through 8
The rail clamp 8$ hus a clamp body 92 having a pair of
spaced side portions 93 and 94 rigidly connected by a bridge portion 9S. The
side portions 93 and 94 carry cylinder brackets 96 and 97 having outer end
5 portions having aligned bores and being spaced apart to receive ~ clevice 98,
broken outline, which is connected to the rod 84 of the advancing cylinder 82
of Figure 2. As best seen in Figures S and 6, the bridge portion 95 has a
lower surface 99 resting on the rail 12, shown in broken outline, and extends
rearward:ly and inter-connects the bracke$s 96 and 97, thus essentially
10 preventing rocking of the clamp on the rail. The ~ide portions 93 ar~ 94 are
essentially mirror images of each other, and thus the side portion g4 only
will be described, mostly with reference to Figure 8.
Referring to Figure 8, the side portion 94 has a base
15 portion 101 fixed to a cam portion 102 by a bolt 103. I`he portion 101 has a
bore 104 carryirig a compression coil spring 105~ and an adjustable spring stop
106 which extends from an end of the bore for adjustment as required. A jaw
member 108 has an inner face 109 inclined at an angle to a centre line 107 of
the rail 12, and is adjacent a similarly inclined cam face 110
2û o~ the cam portion 102. The jaw member 108 has an outer face carrying a
hardened tooth insert 111 which is Etdapted to grip d side face of an upper
portion of the rail as seen in Figure 5. The jaw member 108 can move
axially between a retracted position shown in full outline, and an extended
position 108.1 shown in broken outline7 and stop means prevent the member
25 from falling out of the clars~p. A plunger 113 is fitted as a sliding i:`it within
the bore 104 and has an inner end having a bore to receive the sprin~ 105 and
an outer end held in contact with the jaw member 108. It can be seen that
force from the spring lOS forces the jaw member 108 in direction of an arrow
114, and cooperation between the faces 109 and 110 moves the jaw portion in
30 direction of an arrow ~12, that is inwardly towards the axi~ 107 to grip the
(13)
rail. The side portion 93 on an opposite s;;de of the rail has a similar jaw
member 115 as seen in Figures 6 and r, which can move inwardly
simultaneously with the member 108. Ang]Le of the teeth on the hardened
insert 111, and on a corresponding tooth insert 11~ on the jaw member 115, is
such that the teeth tend to grip the rail as a result of a reactiorl to thrusting
5 forces from the penetrating means, which nct on the clamp in a direction
opposite to the arrow 114.
As seen in Figure 7, the tooth inserts 108 and 116 are
disposed directly opposite to each other so as to grip the rai~equally
10 therebetween. As seen in Figure 6, the tooth insert 116 has a eentral portion117 positioned so dS to be intersected by an axis 118 which passes through a
clevice pin 119 of the clevice 98 and is aligned with an ~xis of the rod a4 of
the ~linder 82 of Figure 2. The clevice 98 i5 drawn in a position of
maximum rod extension for the cylinder 82 which is at the begirming of A
15 stroke. Thus the insert 116 has a eentral portion directly aligned with the
line of îorce from the advancing cylinder at the beginning of a stroke, which
reduces a tendency of the 3aws to slip initially on the rails as a result of
application of the thrust force on the penetrating means. The jaw portions
grip the rail initially due tG ~orce from the springs, but reaction to force
20 from thrusting of the penetrating means causes relativs movement between
the body 92 and the jaw portions which forces the jaw portion towards the
rail and augrnents E~ripping force on the rail. Because the cental portion of
the teeth is intersected by the line of acticn of the advancing means~
gripping is initiated with negligible turning force upplied to the clamp, thus
25 reducing tendency of the clamp to be rotated off the rail.
Thus, in summary, at the beginnin~ of thrusting, the line of
action erom the force of the advancing cylinders is adapted to pass through
the central portion of each jaw gripping the rails. Cripping force is initiated
30 by resilience of the coil springs acting on the jaw members and is further
augmented by the camming action o~ the jaw members sliding against the
(14)
cam faces of the side portions. It can be seen that the clamp has a body, at
least nne jaw member which is resiliently urged relative to the body, and at
least one inclined surface whieh cooperates with the jaw member and the
body to move the jaw member so as to engage the rall or other rigid
5 structure. To release the clamp, the advancing cylinder is extended and thus
the body 92 is moved forwardly in direction of the arrow 114, which
movement permits the jaw port;on to move in a direction opposite to the
arrow 112, thus reducing gripping and releasing the clamp.
10 OPERATION
~t
ln operation, referring mainly to Figures 1 and 2, the
movable rail platform 14 is positioned so that the forward end lS thereof is
closely adjacent the muck pile, and the apparatus 10 moves, for exRmple by
15 power applied to the wheels 25, so that the front portion 29 is positioned tobe aàjacent the muck pile. The elevating cylinders 47 and 48 are actuated
so that a lower surface of the penetrating means 50 is closely adjacent the
ground 16 so that the means 50 carl approach a lower portion of the muck
heap. The advancing cylinders are extended to full extension and the
20 respective lift cylinders are actuated to position the r~il clamps 85 and 91 on
the appropriate rail 12, the rail clamps then being actuated so that they grip
the rails 12. The advancing cylinders 82 and 90 are retracted equally, thus
forcing the penetrating means into the muck heap, and pushing material onto
the conveyor assembly. As resistance to penetration increases, the operator
25 can rotationally oscillate the penetrating mean~ about the penetrator sxis
53t ie. by s..ill~i.)g the penetrating means up and down through the angles 67
and 68 which assists in penetration. When desired the front portion 29 can
be raised by extending the elevating cylinders 47 and 4~, so that the
penetrating meani penetrates th~s muck heap at a higher elevation. Material
30 disturbed by oscillations of the means 50 falls onto the means 50 and is
pushed rearwardly onto the conveyor and moved upwardly along the portion
29 onto the portion 30 from where it is discharged into a waiting
conveyance9 not shown, from a rear end of the rear portion 30~ The
(15)
rear end of the conveyor assembly moves forwardly during the stroke of the
advancing cylinders and discharges materia] in to the eonveyarlce. When the
cylinders 82 and 90 are fully retracted~ the advancing ceases. The rail
~lamps are released by initial extension of the advancing cylinders, which
are then fully extended to reposition the rail clamps in a more forward
position, and the rail clamps are again actuated to grip and the cycle is
repeated.
The oscillations permit the tip of the penetratin~ means to
penetrate into the muck heap in an essenti~lly continuous manner, thus
10 producing an essentially continuous stream of material falling onto the
conveyor assembly, and essentially elirninating the intermittent feeding of
material onto the conveyor assembly which is inherent in prior art apparatus
using scrapers, buckets, etc. If the cylinders 47 and 48 are not actuated to
raise the penetrating means 50, the means 50 follows a path dependent on
15 inclination of the rails and this improves control of the angle of the resulting
bed. The penetrating means ean be oscillated at various frequencies using
the cylinders 61 and 62, or alternative oscillating cylinder assemblies as will
be described with re~erence to Figures 14 through 18. A typic~l range of
frequencies might be between ten and several hundred cycles per minute for
20 a maximum total displacemellt of the tip 52 of about thirty centimeters. It
would be usual to have a smaller amplitude of osciUation of perhaps five to
ten centimeters and to combine the higher frequency with the smaUer
amplitude, and vice versa as desired.
~5
ALTERNATIV~,S AND EQUIVALENTS
Fi~ures 9 throu~h 12
A second embodimenl loading apparatus 131) differs from
the loading apparatus 10 of Figures I through 4 by substituting a track laying
30 or crawler track mounting means 132 for the wheels 25 and railroad track 12.
Also, because the crawler tracks 132 can be positioned relatively easily on
3~
(161
the ground 131, the swivelling conveyor assembly of Figures 1 through 4 has
been replaced with a non-swivelling alternative conveyor assembly 134,
which also has other differences as will be described. The apparatus 130 has
a body 135 mounted on the crawler tracks 132 and a plurality OI roller
bearing assemblies 13'7 which support the conve3ror assembly to permit
5 longitudinal movernent of the conveyor assernbly ~s will be described wi~h
reference to Figure Il. The conveyor ~sembly 134 has a longitudinal con-
veyor axis 133 and a conveyor supporting frame 129 carrying Q conveyor, the
frame 129 hRYing front and rear portions 139 and 140, the front portion being
hinged to the rear portion for swinging about a horizontaI transverse
10 conveyor hinge axis 142. The rear portion 140 is carried on a longitu~inal rail
or ram means 141 complementary to the bearing assemblies 137 as will be
described wilh reference to Figure 11. The ram or rail means 141 is mounted
in the bearing assemblies 137 which serve as a complementary ram socket or
linear bearing guide means 148. The resulting combination of ram and socket
15 permits longitudinal movement of the conveyor supporting frame in
direction of an arrow 144 from a retracted or rearmost position of the
conveyor assembly as shown, to a foremost or extended position of the
conveyor ~ssembly, not shown. It is noted that rubber tired wheels or
equivalents can be substituted for the crawler track mounting means. The
2û body contains a suitable motor and hydraulic pumps~ and other known
equipment for driving the crawler tracks~ and for operating various hydraulic
and electrical equipment as will be described.
The body carries a pair of parallel conveyor adv~ncing
a5 cylinders 146 and 147 which extend between the body and the r~m means 141,
which is secured to and thus is effectively part of the rear portion 140 o~ the
conveyor assembly. Thus, erom the position shown in Figure 10, actuation of
the cylinders 146 and 147 ~dvances the conveyor assembly axially in direction
of the arrow 144 so th~t the ~orward portion 139 attains a position 139.1 when
30 the advancing cylinders are fuIly actu~ted. The rear portion 140 moves with
(17)
-the front portion 139 and moves along the body until an extrem e rear end 151
of the portion 140 becomes close to a rear end of the body. A rear elevating
cylinder 149 extends between a rear portion 150 of the ram means 141 and the
rear portion 140, and can raise the rear portion to a raised position 140.1, as
shown in E~igure lo to provide clearance for tlle end 151 of the conveyor over a5 conveyance, not shown~ which can be positioned to receive material faLling
from the eonveyor. Thust the rear portion is adapted for swinging ~bout the
conveyor hinge axis 142 and9 because the cylinder 14~ is mounted on the ram
means 141, it can accomodate the longitudinal sliding of the real portion
when the advancing cylinders 146 and 147 are actuatedO
1~
lReferring also to Figure ll,which shows one side of the rear
portion 140, one typical beaPing assembly 13~ of the several on each side is
described. The assembly 137 has upper and lower horizontallyjournalled
rollers 136 and 138 which sandwich the ram or rail means 141 therebetween,
1$ adjacent horizon~al surfaces of the means 141 being hardened tracks which
are engaged by the rollers to permit longitudinal movement and to prevent
vertical movement of the rear portion 140. A vertically ~ournalled roller 143
engages an outer vertical face of the means 141 to prevent lateral movement
of the rear portion 140. The rollers 136, 138 and 143 are mounted on
20 eccentrics to permit fine adjustment of the rollers relative to $he means 141to control lost motion and accomodate wear, and a dust seal 145 sweeps a
face of the rear pQrtion 140 to reduce bearing contamination. A series of
similar bearing assemblies 137 are mounted on each side of the body 135 and
are also spaced along the body to support the rear portion in all positions and
25 thus provide the linear bearing 148 which provides the ram socket for
m~unting the ram means 141.
Referring mainly to Figure 10, a penetrating means 152 is
mounted adjacent the front portion 139 and i9 hinged adjacent an extreme
30 forward end of the front portion for limited rotation about a horizontal
transverse penetrator axis 154 dispos~d norma~y to the longitudinal axis 133
of the conveyor. The means 15~ has a penetrator tip 156 which is reinforced
to reduce wear when fsrced into a muck pile during mucking und is similar
to the means 50 of Figure 1. A pair of spacecl oscillating cylinders 157 and
158 extend between brackets secured to the forward portioll 139 and
r espective arms 159 and 160, which arms extend upwardly from the
5 penetrating meuns. In A manner similar to that as described with reference
to Figures 1 through 4, actuation of the cylinders 157 and 158 swings the
penetrating means about the axis 154 through an arc shown by undesignated
arrows. A pair of parallel elevating cylinders 163 and lS4 extend between
the ~ront portion 139 and a forward portion 161 of structure movable wilh the
10 ram rneans 141, so as to swing the front portion about the axis 142~The
elevating cylinders 163 and 164 thus follow longitudinal movement of the
conveyor and, for convenience, the combination of the complete conveyor
assembly 134, the ram means 141, the penetrating means 152 and the cylinders
149, 157, 158, 163, and 164 is terrned an excavating assembly 165 which 5s
lS movable "en masse" relative to the body 135 in response to actuation of the
cylinders 146 and 147.
When the rear portion 140 is in a rearmost position as
shown, extension of the elevating cylinders 163 and 164 swings the front
20 portion from a retracted lowered position~ shown in full outline and desig-
nated 13g in Figure 10, to a retracted raised posi~ion, shown in broken outline
and designated 139.2, in which the penetr~ting means is in a similar
retracted raised position 152.2~ However, if the advancing cylinders are
actuated when the front portion is lowered, the front portion and means 152
25 assume extended lowered positions 139.1 and 152.1, broken outline, from
which when the front portion is raised, the front portion assumes an
~xtended raised position 139.3, shown in broken outline.
The body 135 has two operator positions 166 ~nd l67
30 provided with neces~ary duplicate controls. The operator position 166 can be
used when the apparatus is being moved, ie~ when positioning the apparatus
prior to mucking, and the position 167 is used primarily wher, loading or as
(19)
desired. The body 135 has a pair of laterally extensible rams 171 and 172,
which are shown in broken outline in an extended position in Figure 9 so as
to contact portions of rock face 174 defining opposite side walls of a tunnel
so as to essentially prevent movement of the body during mucking. The body
135 also has a pair of lon~itudinally exte!nsible support legs 177 and 178
which are adapted to extend downw~rdly from a rear portion of the body to
an extenàed position as shown in broken outline in Figure 10. As shown in
Figure 12, the support legs extend from a transverse beam 180 ~djacent a
rear of the body 135 and, if required, a similar transverse beam, not shown,
can be mounted adjaeent the front of the apparatus and a seconb pair of
15 support legs, not shown, can be fitted.
In operation, the loading apparatus 130 functions similarly
to the apparatus 10 of Figures 1 through 4, v,1ith the exception that the
anehoring means, n~mely the laterally extending rams 171 and 172, and if
20 required the legs 177 and 178, secure the body 135 to adjacent fixed
struch~re, ie. the adjacent rock, and thus the body itself does not move
whilst the penetrating means and conveyor is advanced into the muck pile.
This contrasts with the previous embodiment where the whole apparatus,
with the exception of the anchoring means, moves as the penetrating me~ns
25 is advanced in~o the muck pile. Simil~rly to the first embodiment, in the
second embodiment the advancing means, ie. the cylinders 146 and 147,
cooperate with the conveyor ~ssembly to cause essentially axial movement
of the conveyor assembly as a reaction to force from the advancing means
which is independent of tractiYe effort from the wheels.
3~
A typical sequence o~ operation for the apparatlJs 130 is as
follows. Tlle operator, in the position 166, actuates the crawler tracks 132
until the penetrating means, in the lowered retracted position as shown in
full outline in Figure 10, is closely adjacent the muck pile. If heavy mucking
is expected, the laterally extending rams 171 and 172 are e~tended to engage
~20)
the roek ~ 174, and if inclinQtion of the body requires adjusting, the
support legs 177 and 178 are extended, inclependently from each other7 as
required~ to position the linear bearing 148 of the ram socket at the desired
inclination relative to the ground 13L The operator then assumes the
position 1~7 and ~ctuates the advancing cylinders 146 and 147, with the
5 penetrating means 152 positioned elosely adjacent the ground, that is the
front portion 139 is lowered as shown in Figure 10. As the advancing cylinders
move tile conveyor assembly 134 forwardly, the penetrating means advances
into the muck pile, and when a particular resistance to penetration is felt,
the oscillating cylinders 157 and 158 are actuated so as to extend an~ r etract
10 at a particular frequency, which rotationally oscillates the penstratin~
means about the axis 145 to facilitate penetration into the muck pile.
Similarly to the previollsly described embodiment9 if desired the elevating
cylinders 163 ~nd 164 can be extended to raise the front portion 139, so that
the penetrating means describes a higher path thl-ough the muck pile. Muck
15 falling onto the penetrating means is moved rearwardly onto the conveyor,
to pass up the forward portion 139, along the rear portion 140 and is
discharged from the back of the rear portion 140 onto a waiting conveyance,
not shown. The rear portion 140 moves axially~ and thus distributes material
axially into the waiting conveyance.
When the advancing cylinders reach the end of their
strolces, they are retracted so th~t the conveyor assembly moves rearwardlv
and the front portion is again lowered to ~sume the full outline position
~hown in Fig~ure 10. If sufficient of the material remains, the apparatus does
30 not require repositioning between strokes of the ad~rancing cylinders. The
above cy~le is repeated as needed until the muck pile i5 e~sentially removed,
the body remaining stationary throughout to relieve the power train of wear.
The laterally extending rams and advancing cylinders are then retracted and
the crawler tracks are actu~ted to move the apparatus 130 forwardly, so as
(21)
to position the penetrating means closely adjacent rem~ining portions of the
muck heap once again. The latera~ly extending rams 170 and 171 and the
support legs 177 and 178 are extended as required to lock and position the
body as requiredO
Thus, it can be seen that the laterally extending r~ms serve
as anchoring me~ns mounted on the ~ody and adapted to extend outwardly
there~rom to engage an adjacent surface of the surroundings to prevent
essentially movement of the body relative to the surface. Thus the rams are
adapted to CooperQte with the surroundirlgs adjacent the appar~tus to resist
10 reaction to penetration forces generated orl ~he penetral:ing mearls. Also,
the conveyor advancing eylinders 1146 and 147 ssrve as the advancing means,
equivalent to the advancirlg cylinders 82 and 90 of Figure 17 and in fact are
extensible ~nd retractable means extending between the body and the
conveyor assembly to move the conveyor assembly towards the material yet
15 ~o be loaded. The elevating cylinders 163 and 164 are equivalent to the
cylinders 47 and 48 of Figure 1 and serve as forward elevating means
extending between the front portion of the conveyor assembly and structure
associated with the rear portion, which in this instance is the ram means, so
that actuation of the elevating rne~ns swings the front portion about the
20 transverse conveyor axis and raises or lowers the penetrating means. Thus
th~ horizontal transverse conveyor hinge axis permits relative swinging
between the front and rear portions of the conveyor, which occurs when
either, or both~ portions are raised or lowered. Also, the osci~lating
cylinders 157 and 158 and associated structure are equivalent to the cylinders
25 Bl and 62 and associated structure of Figure 1, and serve as oscillating means
cooperating with the penetrsting means to oscillate the penetrating means
~bout the transverse penetrator ~xis~
~22)
In summary, it can be seen th~t a meth~d oï loading mat-
erial according to the invention is for use with an apparatus having a body
and a conveyor assembly mounted on the body and adapted to transport
material from a front portion of the conveyor to a rear portion thereof along
a longitudinal conveyor u~sis. The front portion has a penetrating means and
5 the method is characterized by: advancing the penetrating means into the
material to be loaded, and, when required9 simultaneously rot~tionally
oscillating the penetrating means about a horizontal transverse axis disposed
normally to the longitudinal axis to facilitate loading of material onto the
conveyor. trO overcome resistance to penetration, prior to advan~ing the
10 penetrating means into the material to be loaded, an anchoring means is
anchored relative to the surroundings and is forced against to overcome the
resist~nce to penetration of the material. In the first embodiment5 after the
anchoring means is anchored relative to the surroundings, the remainder of
the apparatus is moved by advancing means reacting against the anchoring
15 means, thus forcing the penetr~ting means into the muek heap. In the
second embodiment, the body is anchored relative to the surroundings and
the conveyor assembly is moved forwardly relative to the body to advance
the penetrating means into the muck heap.
20 Figures 13 and 14
The penetrating means 50 of Figures 1 through 4 and 152 of
Pigures 9 through 12 are shown with relatively conventional double-acting
oscillating cylinders. An alternative tandersl oscillating cylinder assembly
a5 201 can be substituted for each oscillating cylinder of either embodiment as
previously described. The cylinder assembly 201 in Figure 13 is shown
cooperating with the penetrating means 50 of Figures 1 through 4, but it can
be substituted to osciUate the penetrating rneans 152 of Figures 9 through 12.
(23)
Referrring mainly to Figure 13, the penetrating means 50
has upper and lower plates 203 and 20'1 secured together by an inner curved
wall 205 and by two spaced parallel similar sidewalls a~ opposite sides of the
upper and lower plates. One side wall 207 only is shown, and the plates and
side walls forrn a closed box-like assembly terminating at the tip 52. An
upper end of the side wall 207 projects upwardly to the arm 58 which i5
connected to a first piston rod 209 OI the cylinder assembly 2011. A simil~r
second piston rod 212 extends rearwardly frorll the assembly 201 to connect
to the bracket 63 of Figure 2.
The front portion 29 of the conveyor assembly 27 is shown
partly iJI broken outline and has a lower rnember 214 extending between side
members 215 and 216 which define sides of the forward portion. The lower
member teminates at an upwardly curved lip 218 which, similarly to the wall
214, is curved concentrically with the common pent t~a$or axis 53 which is
15 also concentrh~ with the fronl sprocket shaft 41. One of the conYeyor chains
40 is shown passing around the shaft 41 which is hollow and encloses a fixed
spindle 221 which journal~ the penetrating means 50. An upper edge 223 of
the curved wall 205 is shown in e datum position in whieh the lower plate
204 is generally horizontal, that is parallel to ground 160 Angles 222 and 224
on opposite sides of the edge 223 eorrespond to the angles 67 and 68 which
represent maximum upward and downward rarlges of movement OI the tip 52
of the penetrating means 52 relative to the datum, shown at positions 52.1
and 52.2. Clearly, when the edge 223 is in an uppermost position, shown in
broken outline at 223.1, there is sufficient clearance to prevent interference
25 with the chain. Likewise, in a lowermost position of the penetrating rneans,
not shown, the upper edge 223 is no lower than the lip 218 of the lower
member 214. This is to direct muck relatively smoothly on to the conveyor1
and also to reduce ingress of muck between the chain and forward portion
29.
~2~)
The penetrating means 50 can be fitted with an optional
inclination read~out me~ns 225 which has a forward portion shown in Figure
13, and a rear portion shown in Figure 15 to be described. The front portion
of the means 225 has a push-pull control cable 227 having a core 228
connected to the arm 589 the core being slidable within a cable sheath 229
which is secured by a bracket 231 to the portion 29. As the means 50 swings
through the angles B7 and 68~ the core movles axially wi~hin the sheath 229,
and ~n outer end of the core 228 moves over a scale as will be described in
Figure 15, which movement reflects movemen$ of the penetrating mSans and
its position relative to the front portion 27.
The compound oscillating cylinder 2û1 can have an
automatic oscillating and read-out means 235 which h~s a forw~rd portion
shown in Figures 13 and 14, and a rear portion shown in Figure 15. The
forward portion includes a secorld push-pull control cable 237 having a core
lS 238 connected to a bracket 239 which is connected to a rear portion of the
cylirlder assembly 201. The cable 237 has a sheath 241 connected to a
bracket 242 extending from the rod 212, and movement of the bracket 239
relati~,e to the bracket 24~9 which is fixed relative to the front portion 27, is
reflected by movement of the core 238.
Referring to Figure 145 the tandem osci31ating cylinder
assembly 201 has a long stroke cylinder assembly 247 at a forward end ~nd a
short stroke cylinder assembly 249 at a rear end. The cylinder 247 has a
body 251, a piston 252 slidable vuithin the body and connected to the piston
25 rod 207, and outer ~nd inner cylinder end portions 254 and 255 respectively.
Fluid ports 257 and 258 communicate with portions of cylinders adjacent the
cylinder end portions and are connected to fluid conduits of a fluid circuit to
be described with reference to Figure 15.
(25)
The cylinder assembly 249 has a cylinder body 260, a piston
261 slidable within the body and connected to the piston rod 212, and an outer
cylinder end portion 262. The end portion 255 of the cylinder assembly 247
also seals the end of the cylinder assembly 249, and it can be seen that the
cylinder bodies 251 and 260 are rigidly connected together and axially
aligned. The piston 261 has a piston rod extension 265 which extends on a
side of the piston 261 opposite to the rod 212, and is axially aligned with the
rod 212 and has the same cross-sectional area. The inner cylinder portion
255 has a bore 267 which can receive the full length of the extension 265
when the piston 261 is adjacent the end portion 255, as shown. An outer
portion of the bore 2~7 is sealed at 269, so as to essentially eliminate fluid
leakage into the bore 267, and an inner portion of the bore 267 is connectecl
to a bleed hole 270 which relieves minor b~ild-up Of either air or
hydraulic fluid within the bore 267. The cylinder body 260 has fluid por~s
272 and 273 which communicate with opposite ends of the short cylinder
15 assembly and the flu~d circuit of Figure 15. Because the rod 212 and the
extenson 265 have equal cross-sectional areas, the cylinder body 260 shifts
equal distances in either direction as a result of equal fluid volume changes
on either side of the piston 261, which results in equal oscillations of the
penetratin~ means as will be described. The bracket 239 is secured to the
20 cylinder body 260 and thus reflects movement of the cylinder bodiefi relativeto the piston rod 212, which, as previously indicated, is connected to
structure mounted with the bracket ¢3 of the front portion.
In operation, the long stroke cylinder assembly 247 receives
25 hydraulic fluid through the ports 257 and 258? and the short stroke cylinder
249 eceives distinct and separate hydraulic fluid through the ports 272
~ ~ h~
(26)
and 273. Thus the two piston rods extend or retract relative to the
respective cylinders by an amount dependent on the fluid from the circuit
OI Figure 15. Briefly, the long stroke cylindler can be used to set a particular~ngle or datum inclination of the penetr~ting means 50, i.e. 67 or 68 as
shown in Figure 13, and the short stroke cyli7lder can be used to apply an
5 oscillation to the means 50 so that the tip 52 oscillates through a relativelysrnall amplitude 276, which may be in the range of between one and thirty
centimetres as previously described. The amplitude 276 is shown when the
penetrating means is generally horizontal~ but it can t)e applied when the tip
of the penetrating means i~ in ~ lower position 52,2, disposed at an~ngle 68,
10 or at an upper position 52.1 when the means 50 is disposed at the angle 67, or
when the means 50 is at any intermediate position~ The angles 87 and 68 are
dependent on loading conditions and material characteristics and cnn be
selected by the operator to suit.
15 Fi~ure 15
An electrical/hydraulic circuit 280 is used to actuate the
tandem oscillating cylinder assembly 201 of Figures 13 and 14, and a similar
tandem oscillating cylinder assembly 282, which are connected in parallel to
actuate the penetrating means 50. The first and second push-pull control
cables 227 and 237 are shown extending from the arm 58 and bracket 239
respectively and have inner ends ~84 ~nd 285 respectively. The inner end
284 has a pointer 286 connected to the core of the cable 227 which sweeps
over a scale 287 which represents the full swing of th~ penetrating means
and thus permits an operator to visualize the attitude or inclination of the
oscillating means relative to the front portion 29 of the conveyor assernbly
27 when embedded in a pile of muck. Thus a mid position on the scale
represents approximately a mid position of swing of the penetrating means.
The inner end 285 of the push-pull control cable 237 i5 adaplced to
30 reciprocate a trig~er 288 between a pair of spaced rollers 290 and 291 of a
I
(27)
rocking, double-pole reversing limit switch 293. Spacing between the rollers
can be adjusted to adjust the amplitude of osciLlation. The limit switch 293
is connected electrically to ~ manual switch 296 which is ~lso connected
electrically by wires 294 and 295 to a solenoicl-operated, four~wQy valve 298
5 having a closed centre pos;tion. The valve 29B receives fluid under pressure
from a variable displacernent, pressure compensated hydraulic fluid pump
300 and communicates with the fluid ports of the short stroke cylinders of
the tandem cylinder assernblies 2û1 and 282, through a double lock valve 301.
A fixed displacement hydraulic fluid pump 30~ supplies pressurized fluid to a
10 manually operated four-way valve 306 having a centre position in v~hich a
pump port is blocked and both cylinderg are connected to tank. The valve
308 supplies fluid at pilot pressure through conduits 308 and 309 as required
to a pilot-operated, four-way valve 311 having a closed centre position. The
valve 311 outputs fluid pressure from the pump 300 through conduits 314 and
15 315 as required through a double lock valve 317 to the ports of the long
stroke cylinder assembly 247. Undesignated conventlonal hydraulic
components such as pumps ~nd relief valves ~re shown and are not discussed
in detail.
In operation, both pumps 300 and 304 are operated to
supply fluid pressure as required as the apparatus approaches the muck heap
with the front portion of the conveyor assembly in a lowered position as
described, and the penetrating means at a desired in~lination, which can be
Rscertained from as~ç~inE the position of the pointer 286 on the scale 287.
25 The switch 296 is in neutral and the m~nual valve 306 feeds pilot pressure tothe valve 311 which positions the means 50 at the desired inclination. If
oscillation is reguired, the switch 296 is then moved to the automatic mode
which energizes the limit switch 293 which is triggered adjacent outer limits
(2~)
of the strokes of the short stroke cylinder assemblies by the trigger 288 of
the second pushpull cable 237. If the switch 296 is returned to neutral, the
automatic switching due to the limit switch 293 is deactivated and the
oseillation stops. If the datum inclination of the mehns 50 is to be changed,
the rollers 290 and 291 and the switch 293 are moved together a~ially to
establish a repositioned range o oscillation of the trigger 288. The trigger
oscillates about a mid position disposed equally between the rollers. The
mid position relative to total ran~e of axi~ll adjustment or muvement of the
switch 293 etc. reflects datum inclination of the mearls 50 relatiYe to full
10 sweep of the means 50. The double-lock valves 301 and 317 are provided to
prevent unintentional movement of the penetrating means.
The tandem eylinder assemblies 2û1 and 282 and the associated
circuit 280 disclose optional automatic application of oscillation to the
15 penetrating means7 with means to adjust the particular daturn inclination of
the penetrating means about which the penetrating means oscillQtes, and
also msans to adjust the amplitude of oscillation. In this embodiment the
function of setting the datum inclination and of providing oseillation are
two distinct functions which are effected by the two distinct cylinders
XO arranged in tandem. Automatic oscillation is thus simpler for an operator
than manually reversing the directional valves of a conventional single
cylinder as shown for the oscillating cylinders 61, 62, 157 and 158. A pot-
ential disadvantage of manually reversing the valve as suggested above is
that the range of oscillation of the penetrating means gradually moves
25 because the chambers on opposite sides of the piston receive equal flow, but
have ineguRl displacernents due to the piston rod in one chamber. This
pa~ticular disadvantage is not found in the tandem cylinder assembly of
Figure 14 or in the embodiment of Figures 16 -18 as follows.
30 Figures 16 through 18
~A third ernbodiment of a cylinder assembly and associated structure
is an oscillating means that can be substituted for the
~29)
oscill~ting eylinders 61 and 62 of Figures 1 through 4, or 157 and 158 of
Figures 9 through 12, or the cylinder assembly 201 of Figures 13 and 14. In
~igure 16 the third embodiment 321 is shown mounted on the front portion 29
so as to oscillate the penetrating means 50 about the penetrator axis 53.
The third embodiment includes a double-rod hydraulic cylinder assembly 323
having a cylinder body 324 and a piston 326 slidable within a bore of the
body. A piston rod 328 is hinged to the bracket 63 and passes through a
sealed end cap 330 of the cylinder 323 to connect to one side of the piston
326. A piston rod extension 332 extends from an opposite side of the piston
to pass ~hrough a second sealed end cap 334 andis enclosed within ~ forward
portion 335 o the cylinder body to prevent contamination of the exposed
end of the extension 332. The rod 328 and rod extension 332 have eguAl
cross~ectional areas, and thus the cylinder assembly 323 is an equal
displacement double rod cylinder for both extension and retraction. Fluid
ports, not shown, supply hydraulic fluid to chambers on either side of the
piston and a protective casing can be fitted. A braeket 336 connected to a
rear portion of ehe body 324 carries a first feedbaclc rod 338 which is
coupled through a universal joint 34û to a second feedback rod 341. The rod
341 is rnounted for axial movement in linear bearings 343 secured to the
front portion 29 so that axial movement o~ the cylinder body 324 relative to
the piston rod 328 is re~lected as axial movement of the rod 341 in
accordance with the double-headed arrow 34$. Clearly, reciproceting axial
movement of the cylinder body results in rotational oscillation of the
penetrating means 50 about the penetrator axi~ 53.
Re~erring mainly to ~igure 17, the second feedb~ck rod 341
is supported in linear bearings as required along the length of the front
portion 29, and has an aft end coupled to a second universal joint 347 which
is conneeted to one end of a pointer rod 349 which has a pointer 351 Rt an
opposite end thereof. The pointer 351 sweeps over a scale 3S3 which is
(30)
secured to a portion of the ~onveyor assembly adjacent the operator so th~t
the operator can observe, by the ]ocation of the pointer on the sc~le, the
inclination of the penetratin~ means relative to the front portion 29, and by
inference also relative to the ground. The fleedback rods and other structure
associated with the pointer rod 349 and scale are termed an inclination
5 readout means 357 which cooperates with an automatic oscillation means
359 as will be described. Aet portions of the~ means 357 and 35~ ~re enclosed
within a casing 361, which hRs a window~ not shown, to permit the scale 353
to be read by the operator. The casing 361 carries a pair of brackets~363 and
36~ which carry linear bearings 3~6 and 367 which mount the pointer rod 349
10 for axial movement relative to tha casing.
The automatic oscillating means 359 includes a sensor rod
370 and a dash-pot rod 371, the rods 371) and 371 being fixed to the brackets
363 and 3~4 and disposed parallel to the rod 349. The rod 370 carries a
15 follower 3~3 for relative sliding movement there-along, the follower having
an anchor means 375 seeured to the rod 349 so th~t the movement of the rod
349 results in simultaneous parallel movement of the follower 373~ The
dash pot rod carries a dash pot assembly 377 which includes a dash pot
cylinder body 379 h~ving end caps 381 and 382 which sehl the dash pot rod
20 and permit longitudinal movement of the dash pot assembly along the rod
371. The rod 371 carries a dash pot piston 384 which, QS seen in Figure 18,
has a pair of metering openings 385 which per~rlit controlled pussage of fluid
therethrough. The cylinder body 379 carries first and second sleeves 387 and
388 which are slidable axially relative to the cylinder body and carry first
25 and second brackel:s 389 and 390 respectively. The brackets 389 and 390
have right hand ~nd left hand threaded bores respectively which receive
right hancl and left hand threaded shaft portion3 392 and 393 respectively.
The shafts are rigidly connected at a centre port;on to form a combination
reverse thr~eded shaft ~nd the centre portion is journalled in a centre
(31)
bearing and bracket 39~. Thus, rotation of the shafts 392 and 393 moves the
sleeves 387 and 388 equally in opposite dire,ctions relative to the bracket 394
on the body 379. The brackets 389 and 390 also carry first and second
proximity switches 395 and 396 which extend frorn the sleeves 387 and 388
and nre guided on the sensor rod 370 so ~s to be positioned on opposite sides
of the follower 373. Spacing between the first and second brackets 389 and
39D determines axial movement of the follower 373 before it comes within
range of the proximity switch 395 or ~9~ Electrical wires 398 and 399
extend from the switches 395 and 396 to interconnect with a four-way,
closed centre position directional valve, not shown, which controls the flow
of fluid relative to the chambers on the opposite sides of the piston 326 of
the cylinder 323. The directional valve i~ equivalent to, and c~n be similar
to9 the valve 298 of Figure 15.
In operation, the penetrating means 50 i5 set at a desired
angle as it penetrates the muck heap, as shown ~o the operator by the
pointer 351 on the scale 353. This is usually at a slightly downwardly
inclined angle, and the oscillation of the penetrating means about the axis 53
can be automatically controlled by the operator as follows. The spacing
between the proximity switches 395 and 396 is adjustable by rotation of the
20 combirlation threaded shafts 392 and 393. ~his determines amplitude of
oscillQtion of the tip 52 of the penetrating means which, ~s previously
stated3 can range from a few degrees to perhaps up to 35 degrees. When the
follower 373 is di~posed at a mid-postion between the proximity switches
25 395 and 396, that is the follower is within a transverse plane containing thebracket 394, the pointer 3Sl represents a mid-position of oscillation of the
penetrating rneans. The position of the bracket 394 relative to the brackets
363 and 364 reflects the datum inclination of the penetrating means rel~tive
to the complete amplitude of swing of the penetrating means which
30 oscillates equally on either side of the d~tum inclination. As shown in
Figure 16, the piston 32~ is generally adjacent the middle of the stroke
within the cylinder 3231 and the bracket 394 will similarly be in a position
generally adjacent the middle of the rod 371.
(3~)
Assuming that fluid is flowing into the rear chamber of the
cylinder 323, the cylinder body 324 moves aft, swinging the penetrflting
means 50 upwards per arrow 40n, and also moving the pointer rod 349 aft.
The follower 3~3 follows the aft movelment of the rod 349 until the
proximity switch is triggered, at which time the directional ~alve, not
5 shown, reverses ancl fluid then drains from the rear chamber of the cylinder
323 and fluid flows into the forward chamber. This causes the rod 349 and
follower 373 to rr ove forwardly, until the Iproximity switch 395 is actuated,
thus repeating the process. The dash-pot assembly 377 resists accidental
movement on the rod 371 due to friction of the seals in the end caps, and the
1~ resistance to flow of flllid through the openings 385 in the p~ton 384.
HoweverJ the assembly 377 can be moved along the rod 371 by the ~ollower
373 as will be described. It can be seen that rotation of the combination
threaded shafts 392 and 393 would vary spacing between the proximity
swit~hes, and thus range of osclllation of the tip.
To change the datum inclination of the penetrating means
50, the main switch controlling the electrical wires 398 and 399 is de-
activated so that the proximity switches are inoperative. This is done when
the follower 373 is moving along the rod 370 in a direction which approaches
20 a postion on the rod 349 which would reflect the desired new datum
inclination of the penetrating means. When the follower 373 eontacts the
proximity switch 395, resistance to movement due to the dash-pot is
overcotne and the autornatic oscillating means 359 is moved "en massel' aft
vvith the follower 373, which movement iæ of course re~le~ted by the pointer
25 351 sweeping the sc~le 353. Fluid in the dash-pot flows from one ~hamber to
~nother chamber through the openings 385 in dash-pot piston 3840 The
follower malntains the ~ft movement until the braclcet 394 attains a position
reflecting the new desired datum inclination of the penetrating means, at
which time th0 valve controlling 10w to the cyiinder 323 is shif~e~ to
30 prevent further movement. The proximity switches 395 and 396 are then re-
energized and the ollower 3'73 then returns towards the proximity switch
395 so that oscillation again resumes alltomatically if desiredO
(33)
Thus, in summary, both cylinder assemblies 201 of Figure 14
and 282 of Figure 16 and associated structure provide oscillating means with
means to establish a datum inclination of the penetrating means, and means
to oscillate the penetrating means about the de~tum inclination. In both
cases, the means to oscillate the penetrating means is a fluid actuated
5 double piston rod cylinder in which equal fluid displacement results in equal
rod movement in either direction. The cylinder has fluid ports to receive
and discharge fluià, and a direction~ valve means cooperates with the
conduits to alternatively direct ~luid to, or receive fluid from, the fluid
ports. In each embodiment feedback means, responsive to position of the
10 penetrating means, actuates the directional valve means at limitsJof range
of oscillation of the penetrating means. Also in both cases9 the automatic
oscillating means includes the means to establish the datum inclination of
the penetrating which is a limiter assembly having a mid-position disposed
equally between two limiting means. In Figure 15~ the limiter assembly
15 includes the rollers 290 and 291, the limit switch 293 and associated
structure. In Figure 17, the limiter assembly includes the two proximity
switches and associated structure. In both cases, the limiter assembly is
positionable within a range in which the mid position thereof reflects the
datum inclination of the penetrating meflns, and the limit;ng means
20 cooperates with the directional valve to alternated lluid flow for each
stroke. In both cases the means to oscillate the penetrating means about the
datum inclination includes a follower means cooperating with the feedback
means and is reciprocable about the mid position and between the two
limiting means~ In Figure 15, the follower means is the trigger 288 and in
25 Figure 17 the follower means is the follower 373. The follower means
actuates the limiting means altern~elv as the oene~ratir~ means approaches
limits of oscillation. In both c~se~ the oscillating rneans ~ has adjustment
means to move the limiter assembly to attain a changed mid position thereof
which is reflected by a change in datum inclination of the penetrating
30 means.
