CA1191488A

CA1191488A - Mobile loading apparatus and method

Info

Publication number: CA1191488A
Application number: CA000429524A
Authority: CA
Inventors: Richard Crawshay; John H. Hradil; Frank Bottomley
Original assignee: Vale Canada Ltd
Current assignee: Vale Canada Ltd
Priority date: 1983-06-02
Filing date: 1983-06-02
Publication date: 1985-08-06

Abstract

MOBILE LOADING APPARATUS AND METHOD

ABSTRACT OF THE DISCLOSURE

Apparatus and method for loading material, particularly for use in underground excavations. Apparatus has a body supported on wheels or crawler tracks, which permits movement of the body on a surface, and a conveyor assembly mounted on the body to transport material from a front portion of the conveyor assembly to a rear portion thereof. Advancing structure cooperates with the conveyor assembly to cause essentially axial movement of the conveyor assembly as a reaction to force from the advancing structure. Penetrating structure mounted adjacent the front portion of the conveyor is adapted to be forced into material to be loaded and is rotationally oscillated about a horizontal transverse axis disposed normally to the longitudinal axis to facilitate penetration of the material.
Use of advancing structure to force the penetrating structure into the material eliminates necessity for tractive forces applied to the wheels or tracks of conventional machines, thus overcoming scuffing or wear problems associated with such wheels or track. The body itself either carries the fixed conveyor assembly and is moved by the advancing structure as a total assembly, or alternatively the body is fixed by anchoring structure and the advancing structure moves the conveyor assembly relative to the body. The front portion of the conveyor can be raised to enter the material at a higher elevation.

Description

(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 ~) 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.

~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.

Claims

(34) THE EMBODIMENTS OF THE INVENTION IN WHICH AN EXCLUSIVE
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
l. A mobile loading apparatus having a body and a conveyor assembly mounted on the body, the conveyor assembly being adapted to transport material from a front portion of the conveyor assembly to a rear portion thereof along a longitudinal conveyor axis the apparatus being characterized by:
(a) 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, (b) penetrating means mounted adjacent the front portion for rotation about a horizontal transverse penetrator axis disposed normally to the longitudinal axis, (c) oscillating means to oscillate the penetrating means about the penetrator axis to facilitate penetration of the material to be loaded onto the conveyor assembly, and (d) means for moving the conveyor assembly relative to the body.
2. A loading apparatus as claimed in Claim 1 further charac-terized by:
(a) the front portion of the conveyor being hinged to the rear portion thereof for swinging about a horizontal transverse conveyor hinge axis, (b) forward elevating means extending between the front portion of the conveyor assembly and structure associated with the transverse conveyor hinge, (35) so that actuation of the elevating means swings the front portion about the transverse conveyor axis and raises or lowers the penetrating means.
3. A loading apparatus as claimed in Claim 1 further characterized by:

(a) the body being mounted on mobile mounting means, (b) anchoring means adapted to releasably engage rigid structure (12) adjacent the apparatus, (c) the advancing means being extensible and retractable means extending between the anchoring means and the body, so that, as the advancing means is actuated, the apparatus rolls on the mounting means towards the material, thus forcing the penetrating means into the material independently of tractive effort from the mounting means.
4. A loading apparatus as claimed in Claim 1 further characterized by:

(a) the conveyor assembly being mounted on the body for limited lateral swinging about an essentially vertical swivel axis so as to permit collection of material disposed to one side of the front portion of the conveyor when in R central position.
A loading apparatus as claimed in Claim 1 further characterized by:

(a) the conveyor assembly having a conveyor supporting frame carrying a conveyor, the supporting frame being movable relative to the body along the longitudinal axis of the conveyor assembly.

(36)
6. A loading apparatus as claimed in Claim 5 further characterized by:

(a) an excavating assembly which includes a ram means, the conveyor assembly, the penetrating means, and the oscillating means for oscillating the penetrating means, the excavating assembly being mounted relative to the body so as to be movable all together relative to the body to enable the penetrating means to penetrate the material to be loaded while the body remains stationary.
7. A loading apparatus as claimed in Claim 6 wherein the excavating assembly is further characterized by:

(a) the front portion of the conveyor assembly being hinged to the rear portion of the conveyor assembly at a conveyor hinge to permit relative swinging therebetween about a horizontal transverse conveyor hinge axis, (b) forward elevating means cooperating with the front portion and the ram means to swing the front portion relative to the ram means.
8. A loading apparatus as claimed in Claim 5 further characterized by:

(a) anchoring means including at least one ram mounted on the body and adapted to extend from the body to engage an adjacent surface of the surroundings to prevent essentially movement of the body relative to the surface, (37) (b) the advancing means including extensible and retractable means extending between the body and the conveyor supporting frame to move the conveyor assembly along the conveyor axis, so that, as the advancing means is actuated, the conveyor is moved towards the material thus forcing the penetrating means into the material independently of tractive effort from mobile mounting means supporting the body.
9. A loading apparatus as claimed in Claim 1 further characterized by:

(a) the rear portion of the conveyor assembly being hinged for swinging about a horizontal transverse conveyor hinge axis, (b) rearward elevating means extending between the rear portion of the conveyor and structure associated with the transverse conveyor axis, so that actuation of the elevating means swings the rear portion about the transverse conveyor axis.
10. A loading apparatus as claimed in Claim 1 in which the oscillating means is further characterized by:

(a) means to establish a datum inclination of the penetrating means, (38) (b) means to oscillate the penetrating means about the datum inclination.
11. An apparatus as claimed in Claim 10 in which the oscillating means is characterized by:

(a) long and short stroke fluid actuated cylinders coupled in tandem, the long stroke cylinder being the means to establish the datum inclination so as to position the penetrating means at a desired angle, and the short stroke cylinder being the means to oscillate the penetrating means about the datum inclination, the short stroke cylinder being responsive to equal fluid displacement to produce an equal stroke in either direction.
12. An apparatus as claimed in Claim 10 further characterized by:

(a) automatic oscillating means, responsive to position of the penetrating means and cooperating with the short stroke cylinder to alternate strokes of the short cylinder.
13. An apparatus as claimed in Claim 1 in which the oscillating means is further characterized by:

(a) an oscillating cylinder assembly a cylinder body, a piston mounted on a double piston rod which has equal cross-sectional areas on opposite sides of the piston, and conduit means communicating with chambers in opposite sides of the piston for fluid transfer in alternative directions, (39)
14. An apparatus as claimed in Claim 3 in which the anchoring means is further characterized by:

(a) a clamp having a body, a jaw member which is resiliently urged relative to the body, and an inclined surface associated with the jaw member and body to move the jaw member so as to engage the rigid structure adjacent the apparatus, a reaction to force from the pentrating means augmenting grip of the clamp.
15. An apparatus as claimed in Claim 3 in which the anchoring means is further characterized by:

(a) a clamp having a body and a jaw member movable of the body to grip the rigid structure, the jaw member having a central portion which is positioned to contact the rigid structure so that, at the beginning of a stroke the central portion is intersected by n line of action of the advancing means, so as to initiate gripping of the clamp with negligible turning force applied to the clamp.
16. An apparatus as claimed in Claim 1 further characterized by:

(a) inclination read-out means cooperating with structure associated with the penetrating means to indicate to an operator inclination of the penetrating means.

(40)
17. An apparatus as claimed in Claim 10 further characterized by:

(a) the means to oscillate the penetrating means being a fluid actuated double piston rod cylinder in which equal fluid displacement results in equal rod movement in either direction, the cylinder having fluid ports to receive and discharge fluid, (b) a directional valve means cooperating with the conduits to alternately direct fluid to, or receive fluid from, the fluid ports, (c) feedback means, responsive to position of the penetrating means, to actuate the directional valve means at limits of range of oscillation of the penetrating means.
18. An apparatus as claimed in Claim 17 further characterized by:

(a) the means to establish the datum inclination of the penetrating means being a limiter assembly having a mid-position disposed equally between two limiting means, the limiter assembly being positionable within a range in which the mid position thereof reflects the datum inclination of the penetrating means, the limiter means cooperating with the directional valve to alternate fluid flow, (b) the means to oscillate the penetrating means about the datum inclination being a follower means cooperating with the feedback means and being reciprocable about the mid position and between the two limiting means, the follower means actuating the limiting means alternately as the penetrating means approaches limits of oscillation.

(41)
19. An apparatus as claimed in Claim 18 further characterized by:
(a) 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 means.
20. An apparatus as claimed in Claim 1 in which the conveyor assembly includes an endless conveyor, and the apparatus is further characterized by:
(a) the forward portion of the conveyor assembly having a forward shaft around which the endless conveyor passes, (b) the horizontal transverse penetrator axis being concentric with the forward shaft.
21. A method of loading material onto a loading apparatus wherein the apparatus has a body and a conveyor assembly mounted on the 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 front portion having a penetrating means, the method being characterized by:
(a) advancing the penetrating means into material to be loaded, (b) when required, simultaneously rotationally oscillating the penetrating means about a horizontal transverse penetrator axis disposed normally to the longitudinal axis to facilitate loading of material onto the conveyor, and (c) when required, moving the conveyor assembly relative to the body.

(42)
22. A method as claimed in Claim 21 further characterized by:
(a) prior to advancing the penetrating means into the material to be loaded, anchoring an anchoring means relative to surroundings and forcing against the anchoring means to overcome resistance to penetration of the material.
23. A method as claimed in Claim 21 in which the conveyor assembly is mounted for longitudinal movement relative to the body and the method is further characterized by:
(a) prior to advancing the penetrating means into the material to be loaded, anchoring the body relative to the surroundings to resist reaction to penetrating forces, (b) moving the conveyor assembly forwardly relative to the body to advance the penetrating means into the material.
24. A method as claimed in Claim 21 further characterized by:
(a) establishing a datum inclination of the penetrating means, (b) automatically oscillating the penetrating means in equal amounts about the datum inclination.