CA1057316A

CA1057316A - Conveyor folding and moldboard operation for excavating and loading systems

Info

Publication number: CA1057316A
Application number: CA307,124A
Authority: CA
Inventors: Charles R. Satterwhite
Original assignee: Unit Rig and Equipment Co
Current assignee: Unit Rig and Equipment Co
Priority date: 1975-03-03
Filing date: 1978-07-11
Publication date: 1979-06-26
Also published as: CA1052399A; CA1055535A; CA1055533A; CA1055534A

Abstract

CONVEYOR FOLDING AND MOLDBOARD OPERATION
FOR EXCAVATING AND LOADING SYSTEMS
Abstract of the Disclosure The present invention relates to an excavating wheel.
The wheel is comprised of a pair of spaced apart side plates each extending radially outwardly with respect to a central axis of rotation. A plurality of stationary walls each extend between the side walls and each have outwardly projecting material cutters. A plurality of movable walls each extend between the side walls and cooperate with one of the stationary walls to define a digging bucket. The walls thereby define a plurality of digging buckets positioned immediately adjacent one another to define the entire periphery of the excavating wheel. Each of the movable walls are supported for pivotal movement between a material receiving position and a material dumping position. A unit is provided which is entirely enclosed and which is responsive to the rotation of the wheel for positively pivoting the movable wall of each digging bucket to the material receiving position during one portion of the rotation and for positively pivoting the movable wall of each digging bucket to the material dumping position during another portion of the rotation. The unit is comprised of a spring connected to each movable wall for normally positioning the movable wall in the material receiving position and a cam mounted on each movable wall. A part is provided which is positioned over the material receiving portion of a conveyor for cooperation with the cams of the movable walls to pivot the movable walls to the material dumping position against the action of the springs.

Description

10573~6 This is a division of copending Canadian patent application ' Serial No. 245,~69 which was filed on 16 February 1976.
BACKGROUND AND SUMMARY OF THE INVENTION
The present invention re]ates to improvements in molclboards and conveyor folding and operation which are particularly applicable to excavating and loading systems ' of the type disclosed and claimed in the above-identified ; co-pending application.
'~' According to an embodiment of the invention, an auxiliary conveyor is mounted behind a main conveyor. The discharge end of the auxiliary conveyor is mounted for pivotal movement ~ , generally outwardly and downwardly. This movement raises ,,~, the material receiving end of the auxiliary conveyor. The ,'; upper and rear,ward portion of the main conveyor is then ''~, pivoted downwardly into the space provided by the upward ', movement of the material receiving end of the auxiliary ~,'. co,nveyor. The auxiliary conveyor is then rotated over the discharge end of the main conveyor. This substantially reduces the overall height of the excavating and loading r 20 system for travel and storage purposes.
- In accordance with an embodiment of the invention, a third conveyor can be mounted at the discharge end of the ..:
,; auxiliary conveyor. This third conveyor is mounted to ,~ pivot up under the auxiliary conveyor to reduce the overall , length and height of the excavating and loading system for travel purposes.
In accordance with an embodiment of the invention, a -, moldboard is mounted generally behind and beneath the excavating wheel assembly. The moldboard assembly has a ~ 30 scraper blade and a bearing plate. The moldboard is pivotally supported, and a linkage connects the moldboard to an ' - 2 -,...

~L057316 al-l.<lr;ltlls ~hicl~ col~trols thc vcrtic<ll position of tllc exca~;ltillU wllccl asscml)ly. lhe hlade of the moldhoard functiolls to remove ridges that might otherwise remain between the wheels of the excavating wheel assembly, and to clean the excavation. Ihe bearing plate of the moldboard is utilized in the operation of the excavating and loading system to partially support and to stabilize the excavating wheel assembly. l`he angular positioning of the bearing plate also varies as the moldboard is raised and lowered to facilitate initiation and termination of the excavation.
In accordance with an embodiment of the present invention, the auxiliary conveyor assembly has two in-line conveyors.
The innermost conveyor is arranged to selectively discharge material onto the outer conveyor or into a vehicle. The outer conveyor is adjustable in attitude with respect to the inner conveyor to control the discharge height of the outer conveyor.
Variably positionable deflector plates are mounted at the - discharge ends of the inner and outer conveyors to direct the discharged material.
In accordance with one aspect of the present invention there is provided an excavating wheel comprisillg:
a pair of spaced apart side plates each exten~ing radially outwardly with respect to a central axis of rotation;
; a plurality of stationary walls each extending between the side walls and each having outwardly projecting material cutting means;
a plurality of movable walls each extending between the side walls for cooperation with one of the stationary walls to define a diggillg bucket;
said plurality of stationary walls and said plurality ~L0573~6 of movable walls cooperating to define a plurality of digging buckets positioned immediately adjacent one another to define the entire periphery of the excavating wheel;
each of said movable walls being supported for pivotal movement between a material receiving position and a material dumping position; and movable wall pivoting means entirely enclosed by the digging buckets and the side walls and responsive to rotation of the excavating wheel for positively pivoting the movable wall of each digging bucket to the material receiving position during one portion of said rotation and for positively pivoting the movable wall of each digging ; bucket to the material dumping position during another portion of said rotation; said movable wall pivoting means comprising:
a spring connected to each movable wall for normally positioning the movable wall in the material receiving position;
a cam mounted on each movable wall; and . means positioned over the material receiving portion . of a conveyor means for cooperation with the cams on the movable walls to pivot the movable walls to the material dumping position against the action of the springs.

10573~
DESCRII'TION OF 1l1 r DRAI~INGS
The present invention taken in conjunction with the invention disclosed in copending Canadian patent application Serial No. 245,869 which was filed on 16 February 1976 will be described in detail hereinbelow with the aid of the accompanying drawings, in which:
FIGURE 1 is a side elevation of an excavating and loading system comprising a first embodiment of the invention;
- FIGURE 2 is a partial plan view of the excavating and loading system illustrated in Figure l;
FIGURE 3 is a partial front elevation of the excavating .
and loading system illustrated in Figure l;
FIGURES 4 and 5 are enlarged views, respectively, of the rear and central portions of the excavating and loading system illustrated in Figure l;
FIGURE 6 is an enlarged view of the forward portion of the excavating and loading system illustrated in Figure 1, showing a first embodiment of the improved moldboard of the present invention;
FIGURES 7 through 12 are illustrations of various systems for actuating the rear plates of the digging buckets of an excavating and loading system incorporating the invention;
FIGURE 13 is a side elevation of an excavating and : loading system comprising a second embodiment of the invention;

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~2952 ., FIGURE 14 is a side elevation of an excavating ,~ and loading system comprising a third embodiment of the 1, invention;
,j FIGURE 15 is an enlarged side elevation of the i~! forward portion of the excavating and loading system . .jl shown in. Figure 14; :-FIGURE 16 is a plan view of the forward portion of an excavating and loading system incorporating a fourth jl embodiment of the invention;
ll FIGURE 17 is a front elevation of conical cutter ¦ members which may be utilized in conjunction with any of . . the various embodiments of the invention;
FIGURES 18, 19 and 20 are partial side elevations of the conveyor folding apparatus of the invention;
1I FIGURE 21 is a partial side elevation of a second ~! moldboard assembly incorporating the invention;
¦~ FIGURES 22a, 22b and 22c are diagrams illustrating the op~ration of the moldboard assembly of Figure 21;
I FIGURES 23 and 24 are partial side elevations of ¦ a third moldboard assembly incorporating the invention;
I FIGURES 25 and 26 are side elevations of a ; fourth moldboard assembly incorporating the invention;
¦ FIGVRE 27 is a side elevation of a fifth moldboard ! assembly lncorporating the invention;
~j FIGURES 28a, 28b and 28c are diagrams illustrating the operation of the moldboard assembly of Figure 27;

j, -6-~.' ,,1 ' l'i I!

~057316 ..
`-B29~2 ,, ~IGURE 29 is a side elevation of a sixth -~.
moldboard assembly incorporating the invention;
FIGURE 30 is an enlarged side elevation of ~, the interconnection of the inner and outer conveyors of :
; 5 ', the auxiliary conveyor assembly; and jl ~IGURE 31 is a side elevation of the use of the t auxiliary conveyor assembly used to selectively load two vehicles.

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~1 !l ,1 :

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B2952 DETAIL~:D DESCRIPTIO~1 Referring now to the Dra~inys, and particularly to Figures 1 through 6, a first e~bodiment of an excavating and loading system 20 incorporating the invention is ~~ shown. The system 20 comprises an apparatus which can be , used to excavate and load materials on vehicles for transportation. The system is of the type which travels along constantly excavating materials and lifts and loads the materials on a conveyor system. The material is then ~j transported to and discharged in a vehicle such as a il dump truck or the like. The system is especially adapted for use in excavating in open areas, in forming trenches, -I and the like, and also in confined areas, such as mines ¦ where vertical clearance is limited. As will be parti-~, cularly described and pointed out hereinafter the embodi-'! ments of the invention incorporate improvements in the I' moldboards and conveyor configuration and operation.
¦~ The system 20 comprises a vehicle 22 including ¦l a main frame 24 which is supported by four wheels 26 for movement along a surface S. Each of the wheels 26 li comprises a pneumatic tire 28 whereby the excavating and loading system 20 is adapted for movement over highways and other paved surfaces as well as for operation , in unpaved areas, such as during an excavating operation.
¦¦ A first engine 30 is supported on the main frame

2~ 1, 24 of the vehicle 22. In accordance with the preferred Ii Il .' 10573~f~

2952 : embodiment of the invention, the first engine 30 is an ' internal cor~ustion engine and functions to drive a plurality of hydraulic pumps 32. The pumps 32 in turn supp~y operating power for various components of the , excavating and loading system 20. For example, one of the pumps 32 supplies operating power for a hydrostatic drive l 34. The hydrostatic drive 34 is coupled to a transmission 1 36 including a brake 38. The transmission 36 provides , dual outputs which are coupled to a for~ard differential 1 40 and a rear differential 42 by a plurality of drive :
,shafts 44. Thus, the hydrostatic drive 34 operates ~y ¦~ means of the wheels 26 to propel the excavating and ~loadlng system 20 both during excavating operations and . .
j~ during travel.
I,, An excavating system 50 comprises the fonYard , portion of the excavating and loading system 20. The l,excavating system 50 includes a subframe 52 which is llsupported on a shaft 54 for pivotal movement relative . Iito the vehicle 22 under the action of a pair of hydraulic ¦~cylinders 56 is supplied by one of the purnps 32 which are i i! driven by the first engine 30.
¦¦ The excavating system 50 further includes an excav~ting wheel assembly 58 which is supported at the ¦'front end of the subframe 52. The excavating wheel l'assembly 58 is driven by a second internal cornbustion ,engine 60 which is supported at the rear end of the I, .
1' _9_ I!

: li I!

B2952 , subframe 52. The engine 60 provides opcrating power for ~J I the excavating wheel assembly 58 but otherwise plays no ' part in the operation of the excavating and loading system ' 20. This arrangement has been found to be highly satisfactory ,, for two reasons. First, it permits selection of the second engine 60 on the basis of the power requirements Il of the excavating system S0 only and not on the basis of ; 1,l the power requirements of the other components of the 1~ excava~ing and loading system 20. Also, due to its 1, positioning at the rear of the subframe 52, the second !j engine 60 acts as a counterbalance for the weight of the , , excavating wheel assembly 58. This permits the use of ¦ hydraulic cylinders 56 of reduced size and also reduces ' !I the ~.ount of power that is required in manipulating IS ¦i the excavating wheel assembly 58.
As is shown in Figure 6, one embodiment of a moldboard 62 of the present invention is supported at ¦! the front end of the vehicle 22 of the excavating and loading system 20 beneath the excavating wheel assembly 58.
0 ¦ The moldboard 62 is connected to the vehicle 22 by a pair ¦ of turnbuckles 64 and is also connected to the subframe 52.
In Figures 2, 3, and 6, the excavating wheel j assembly 58 is shown. Assembly 58 comprises three ~, I
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, 1057316 , .
B2Y52 `i excavating wheels 66A, 66B and 66C, which are rotatably ¦~ supported on the subframe 52 by a shaft 68 and a plurality i~ of bushings 70. The second engine 60 drives a speed ~I reducer 72 which in turn drives a right angle drive 74.
5 ¦ The right angle drive 74 actuates a pair of chain and sprocket drives 76 each including a sprocket 78 driven by the right angle drive 74, a chain 80 driven by the sprocket 78, and a sprocket 82 driven by the chain 80.
As is best shown in Figure 2, the chains 80 and the sprockets 82 are mounted within the subframe 52 and are therefore protected from damage to accumulations of dirt, etc. during the operation of the excavating and loading system 20.
Each sprocket 82 is mounted on a shaft 84 which is rotatably supported in the subframe 52 and which in turn supports a pair of pinions 86. The pinions 86 are each mounted in mesh with a ring gear 88 mounted on one of the wheels 66 whereby the second engine 60 functions to rotate the wheels. In accordance with the preferred ; 20 embodiment of the invention, the center excavating wheel 66B is provided with two ring gears 88 and is driven by two pinions 86, whereas the side excavating wheels 66A
and 66C support a single ring gear 88 and are driven by a sin~le pinion 86. In this manner the center wheel functions to maintain relative timing between the wheels ¦ 66A, 66B and 66C and to maintain equal loading on both sides of the excavating wheel drive system.
The excavating wheels 66 of the excavating wheel ¦ assembly 58 each includes a hub 90 and a pair of rims 92 '` I

:. :
~_~2952 which extend radially outwardly fror.l the hub. The excavating wheels co~prise a plurality of digging buckets , 94 which are equally spaced circ~lferentially around the hub ~0 and which extend between the rims 92. The digging buckets 94 each have a cutting edge 96 including a plurality of teeth 98 and a stationary front wall 100 extending 'I generally radially inwardly from the cutting edge 96.
I Each digging bucket further includes a rear wall 102 which ~i is suoported for pivotal movement between a digging 1¦ position and a dumping position. The rear walls 102 of i'' the digging buckets 94 are actuated by one of the i mechanisms shown in Figures 7 through 12 and are manipulated , , there~y to the digging position when their respective digging buckets 94 are in the lower and forward portion ¦~ of their rotary motion and to the du~ping position when , l, their respective digging buckets are in the upper and. ', rean~ard portion of their rotary motion.
. As is clearly shown in Figures 2 and 3, the three wheels 66A, 66B and 66C comprising the excavating ' 20 ~I wheel asse~bly 58 have an overall width which exceeds I~ that of the remaining components of the excavating and ¦! loading system 20. This has been found to be highly ; 1, advantageous for two reasons. First, by increasing the 1 width of the excavating wheel assembly 58 over that of a ; 25 ¦, conventional ditching machine, an excavating and loading j' system incorporating the present invention is capable of ¦ excavating considerably more material without increasing 1, . 1i1 ll -12-- ,!

~057316 .:
~2952 the speed of rotation of the excavating wheel assembly.
Second, the fact that the excavating wheel assembly 58 is wider than the remaining components of the excavating ~ and loading system 20 permits operation of the excavating ¦ and loading system within the excavation that is being l' formed. This materially reduces the amount of movement of the excavating wheel assembly 5~ that is necessary to position the assembly for excavating and for travel, and , thereby reduces the overall complexity of an excavating , 10 ,l, and loading system incorporating the invention. -The excavating and loading system 20 further includes a loading system 110. The loading system 110 includes a main conveyor 112 comprising an endless belt ' 114 mounted for movement around a course extending ; 15 angularly upwardly relative to the main fra~e 24 of the vehicle 22 and including a material receiving portion 116 , and a material discharge or delivery portion 118. More particularly, the course of the belt 114 is defined by , I a plurality of rollers 120 which are supported on a conveyor I frame 122. The conveyor frame 122 is supported on the main frame 24 of the vehicle 22 and includes an upper portion 1 124 supported for pivotal movement about a horizontal axis ¦l under the action of a hydraulic cylinder 126. This permits control over the ~ertical positioning of the material , discharge portion 118 of the conveyor 112.
.. ~
The belt 114 of the main conveyor 112 extends ' around a relatively small drum 128 mounted at the upper Il .

!

~057316 9s2 end of the frame 122 and around a relatively larye drum 130 mounted on the frame 24. The drums 128 and 130 are rotated by radi~l hydraulic motors 132 and 134, respecti.vely. By , this means the belt 114 is actuated for movement around , the course defined by the rollers 120 to move material from the material receiving portion 116 to the material li discharge portion 118. It has been found that the ,' positioning of the drums 128 and 130 causes a synergistic 1 effect in that the drum 130 functions to cause the belt ' 114 to wrap more tightly around the drum 128 and thereby !~ increase the effectiveness of the motor 132 in moving the belt 114.
A pair of cross conveyors 140 are also supported Il on the ~ain frame 24 of the vehicle 22. The cross conveyors ll 140 are driven by hydraulic motors 142 and function to 1' receive material from the side excavating wheels 66A and 1~ 66C and to deliver the material to the material receiving ' portion 116 of the main conveyor 112. By this means all I! material that is excavated by the excavating wheel assembly 1~ 58 is delivered to the main conveyor 112 for transportation ¦, thereby from the material receiving portion 116 to the ¦i material discharge portion 118.
j Referring now particularly to Figures 1 and 4, this embodiment of the invention further includes a first !i embodiment of the auxiliary conveyor system lS0. The auxiliary conveyor system 150 includes a frame 152 which .
!l ~ -14-1' .

` :
: 1057316 2952 i is secured to the rear end of the frame 24 of the vehicle 22 by a plurality of pins 154. A turntable .l56 is supported on the frame 152 for pivotal movement about a , vertical axis under the action of a hydraulic motor 158.
Il An inner conveyor 160 is supported on the ~ ~
turntable 156 to receive material discharged from the ~ -', material discharge portion 118 of the main conveyor 112.
¦~ The conveyor 160 comprises a frame 162 which is supported !1 on the turntable 156 and an endless belt 164 mounted for f L0 Ii movement around a course defined by a plurality of rollers ¦ 166. The belt 164 is driven by a radial hydraulic motor ! 168, and a hydraulic cylinder 170 is provided for controlling ,I the angular relationship of the frame 162 to the turntable 156.
¦I The auxiliary conveyor system ].50 further .
jl includes an outer conveyor 172 comprising a frame 174 which j is supported on the frame 162 of the conveyor 160 by a ¦¦ pair of parallel links 176. An endless belt 178 is . I supported on the frame 174 for movement around a course . I defined by a pair of drums 180. The belt 178 is driven ¦¦ by small hydraullc motors (not shown) mounted in the drums 180.
¦ . A hydraulic cylinder lS2 extends between the frame 162 of the conveyor 160 and the frame 174 of the conveyor 172 for actuation to manipulate the conveyor 172 Il between the positions shown in full and in dashed lines in 25~ Figure 4. When the conveyor 172 is positioned as shown . Ii in full lines in Figure 4, it functions to receive material ;' I

. I _ . !!

~l057316 ~ ;
B2952 . from the conveyor 160 and to discharqe the mat~rial fro~
the end of the excavating and loading system 20 remote from the excavating system 50. On the other hand, when ' the conveyor 172 is positioned as shown in dashed lines in Figure 4, material is discharged directly from the , conveyor 160. As will be described in detail, this ,, arrangement is hiqhly advantageous in that it permits the positioning of a dump truck or similar vehicle under I the discharge end of the conveyor 160 while another !i vehicle is being loaded from the conveyor 172, and vice versa.
l It will be appreciated that the hydraulic motor 158 ~a~ be actuated to pivot the turntable 156 and the ,~ conveyors 160 and 172 supported thereon through an arc ll of approximately 180. The excavating and loading system 20 may also be operated with the auxiliary conveyor " system 150 removed, if desired. These conditions cause , substan~ial changes in the overall weight distribution ~1 of the co~ponent parts of the excavating and loading ¦~ syste~ 20.
I¦ As is best shown in Figures l, 2 and 5, the 1~ ~ehicle 22 is equipped with a counterbalancing system 190 comprising four ballast tanks 192, 194, 196, and 198 I! located at forward and rearward positions on opposite 1 sides of the vehicle 22. In the use of the excavating and I .

. -16-'; .

~ 1.

:~L057316 .
B~ 52 loading system 20, water is selectively pumped to and ~-from the tanks comprising the counterbalancing system 190 whereby changes of the tYeight distribution of the ~ excavating and loading system 20 caused by manipulations ' of the auxiliary conveyor system 150 are co~pensated for.
Il Thus, if the excavating and loading system 20 is operated i with the auxiliary conveyor system 150 removed, water is pumped out of the tanks 194 and 198 and into the ¦I tanks 192 and 196. Similarly, if the hydraulic motor ~ 158 is operated to pivot the auxiliary conveyor system I 150 towards one side of the vehicle 22, the tanks on the ¦~ opposite side of the vehicle are filled with water ¦, whereby the change in weight distribution caused by the ¦~ manipula~ion of the auxiliary conveyor system 150 is lS ¦, completely counterbalanced.
A11 of the hydraulic motors and all of the hydraulic cylinders comprising the loading system 110 are j~ operatively connected to the pumps 32 which are driven ¦, by the first engine 30. Thus, the excavating and loading !. system 20 comprises separate excavating and loading ¦, systems 50 and 110, respectively, which are driven by ¦, independent power sources. This arrangement has been found to be advantageous in that it permits optimum utilization of both systems. For example, in certain 1l instances it may be necessary to provide maximum . l operating power to the excavating system 50 and to simultaneously provide maximum operating power to the I I .
I' !
, ~057316 . . ' B2952 loading system 110. SUCh a situation is accommodated much more readily by means of the present invention than would otherwise be possible.
Various systems for actuatiny the rear walls ', 102 of the digging buckets 94 of the excavating wheels ' 66A, 66B and 66C are shown in Figures 7 tnrough 12. In each instance the rear wall actuating system is located ', entirely within the margins of the excavating wheels.
,, This may be compared with certain prior art systems ¦ characterized by external bucket wall actuating apparaius.
,I Referring particularly to Figure 7, an actuating ',l syste~ 200 comprises a plurality of push rods 202 each ¦ of which is connected between one of the rear walls 102 l,, and a chain 204. The chain 204 is generally unconstrained ¦I but extends around a sprocket 206 which is supported on 1 the shaft 68 and which is secured against angular !'l movement relative to tne shaft 68 by suitable brackets (not shown). As the digging wheels are rotated about ¦I the shaft 68 under the action of the second engine 60, t li each push rod 202 comes into engagement with the sprocket , l' 206 whereupon its respective rear wall 102 is pushed ! outwardly to the material dumping position Subsequently ¦ as each digging bucket is rotated to the lower and forward llportion of its-circular path, the chain operates through the ,~ 25 ~push rod 202 to positively return the rear wall 102 to ~ 1, the material digging position. This positive actuation ,. 11 . ~

'1.
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.... . .

~0573~6 V
B2952 , of the rear wall 102 in both directions has been found to be vastly superior to the arrangement that has been used heretofore wherein the rear portions were allowed -, to return to the digging position under the action of I gravity. Two factors involved in this superior performance jl are the positive discharge of sticky materials such as clays ~j and t~e positive shedding of such sticky material from the movable bucket walls. ~ -j~ An actuating system 208 that is similar in 1l many respects to the system 200 is shown in Figure 8.
Ii The system 208 incorporates a plurality of push rods 210 ¦! each connected between a chain 212 and the rear wall 102 !i of one of the digging buckets 94. The principal difference 1 between the system 208 and the system 200 is that the Ij chain 212 of the system 208 is equipped with a plurality ,l of rollers 214. The rollers 214 are mounted for movement ¦l aroùnd a saddle 216 which is fixed to the shaft 68.- By , jl this means, the rear wall 102 of the digging buckets 94 I are positively actuated to the dumping position as each i 20 bucket is rotated to the upper and rearward portion of its circular path and is positively returned to the digging position as the bucket is rotated to the lower ¦ and forward portion of its path.
I Another actuating system 218 is shown in Figure 9.
¦ The system 218 includes a crank 220 which i5 fixed to the shaft 68. A collar 222 is rotatably supported on the crank 220, and a plurality of push rods 224 extend from the collar 222 to the rear walls 102 of the digging buckets 94. One of the rear walls 102 is connected to 10573~6 B~952 the collar 222 by a rod 226 which is fixed to the collar 222. By this means, the collar 222 is constrained to rotate with the digging wheel whereby the push rods 224 / and 226 function to positively actuate the rear walls 102 ,' to the dumping position when their respective digging buckets are in the upper and rearward portion of their travel about the shaft 68 and to positively return the , rear.~ard walls 102 to the digging position when their j, respec.ive digging buckets are in the lower and forward jl portion of their travel.
I~ Still another actuating system 228 is shown in , , ~, Figure 10. The system 228 comprises a plurality of cams 230 each fixed to one of the rear walls 102 of the ¦I digging buckets 94. The cams 230 are positioned for ~l engagement with a roller 232 which is supported on an i '~ arm 234 that is fixed to the shaft 68. Each rear wall ~1 102 is also provided with a spring 236 which functions to ! return the rear wall 102 to the digging position. Thus, j, upon rotation of a particular digging bucket to bring its ,~ cam 230 into engagement with the roller 232, the rear j' wall 102 of the digging bucket is actuated to the ¦' dumping position. As soon as the cam 230 comes out of ! engagement with the xoller 232, the spring 236 returns ll the rear wall 102 to the digging position.
!i Referring now to Figure 11, an actuating system 238 is shown. The system 238 comprises a cam track 240 j !
¦!
1 ' ,' .

!

~)57316 952 ; which is supported on the shaft 68 and ~Jhich is fixed ' against rotation with respect thereto. The rear wall 102 of each digging bucket 94 is equipped with a cam follower 242 including a roller 244 mounted in the cam track 240.
~l The shape of the cam track 240 is such that each rear wall 102 is actuated to the dumping position when its digging bucket 94 is in the upper and rean~ard portion -~
~, o' its rotation about the shaft 68 and is returned to I' the digging position when its respective bucket 94 is ,, in the lower and forward poxtion of its rotation.
'! Yet another actuating system 246 is shown , in Figure 12. In accordance with the system 246, a ~ 1~ pne~matic cylinder 248 is provided for actuating the rear -. I! wall 102 of each diggin~ bucket 94 between the digging , 15 ¦, and the dumping positions. Each pneumatic cylinder 248 j is equip~ed with a valvé 250 for controlling the flow !i of compressed air from a manifold 252 to the cylinder : 1i , ;~ ; 248. Each valve 250 is in turn equipped with a cam follower 254 which functions to open its respective valve ~, 20 1' whenever it is moved inwardly. ' J.~ !i The cylinders 248 and their respective valves ~' j' 250 are mounted for rotation about the shaft 68 with the digging buckets 94 comprising the excavating wheels.
A cam 256 is supported in fixed relation to the sha~t 68.
~; 25 ¦1 Thus, as each digging bucket rotates into alignment with , ~, the cam 256, its respective cam follower 254 is actuated " 1, ,., 11 ~ 21~
, .11 .. I, !
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B2952 by the cam 256. This operates the corresponding valve 250 to admit compressed air to its pne~atic cylinder 248, whereupon the rear wall 102 is actuated to the dumping position. In a particular arrangement shown, the rear walls 102 of the digging buckets 94 are returned to the digging position by individual springs 258. However, it will be understood that the actuating system 246 may be modified to provide for return of the rear walls 102 I under pne~matic action, if desired. It will be further 1 understood that the cylinders 248 can comprise hydraulic cylinders rather than pneumatic cylinders.
Referring now to Figure 13, an excavating and loading svstem 20l comprising a second embodiment of the ' invention is shown. The excavating and loading system 20' is similar to the excavating and loading system 20 described hereinbefore in that it comprises a vehicle 22', an excavating system 50', and a loading system 110'. One '~ differe-.ce between the system 20 and the system 20' is that ¦~ the first and second engines 30 and 60 of the system 20 j, are replaced with electric motors 30' and 60' in the ` !i system 20'. Another difference is that the electric motor ', 60' is positioned in a forward location and in that the i' angular positioning of the excavating system 50' is controlled j' by hydraulic cylinders 56' which are arranged somewhat j 25 ,i differently from the hydraulic cylinders 56 of the excavating l; and loading system 20. This permits the cylinders 56' to 1l!
~ -22-I . .

10573~6 ,.......................................................................... .

~952 ; pivot the excavating system 50' to points above and below the highest and lowest points on the remainder of the --~, excavating and loading system 20' and thereby adapts the 'I excavating and loading system 20' to tunneling operations.
I, The use of the excavating and loading system 20' in tunnelin~ -' ~ operations is further facilitated by the use of the electric Il motors 30l and 60' whereby the emission of dangerous exhaust ¦i gases is completely eliminated.
¦~ Referring now to Figures 14 and 15, there is ,, .
I shown an excavating and loading system 270 incorporating a third embodiment of the invention. The excavating and ¦¦ loading system 270 comprises a vehicle 272 including a ¦ main 'r&me 274 supported on a pair of opposed track I asse~1ies 276 for movement over a surface S. The track ¦ asse~mb~ies 276 are preferably conventional in design and ' compr~se a pair of sprockets 278 and 280 rotatably , supported on a subframe 282 and in turn supporting an endless track 284. Each track assembly 276 further , I includes at least one motor (not shown) mounted on the ; 20 I subframe 282 and adapted for actuation by means of power , I supplied from a prime mover mounted on the vehicle 272 ¦ to propel the vehicle through one of the sproc~ets and the endless track 284 mounted thereon.
Each track assembly 276 is supported for pivotal ' 25 I movement relative to the main frame 274 of the vehicle 272 I about the axis of the rear sprocket 280. A hydraulic '' 11 !1 -23-Ii :,.. , li.

~52 cylinder 286 is provided on each side of the vehicle 272 and is connected between the main frame 274 of the vehicle and the subframe 282 of the adjacent track assembly 276.
The hydraulic cylinders 286 are preferably actuated in ' tande~ to control the angular relationship of the track ' , assemblies 276 relative to the remaining components of the , excavating and loading system 270.
As will be appreciated by those skilled in the i art, the hydraulic cylinders 286 are typically initially j actuated to lower the forward portion of the excavating ~' and loading system 270. This causes the excavating and loadincj I, system to initiate a downwardly inclined excavation, ¦' whereby the excavating and loading system 270 digs itself I,' into t~ cut or excavation to be formed. When the desired 1 5 1l degree o' inclination has been established, the hydraulic ,l cylinders 286 are actuated to return the component parts of the excavating and loading system to the orientation , illustrated in Figures 14 and 15, whereby the excavating and loading system continues to excavate on the established ' inclina~ion until the desired depth of the excavation is reached.
The hydraulic cylinders 286 are then actuated ; to cause the excavating and loading system to form the ' bottom of the cut or excavation at a predetermined angular . , .
;,5 I relationship with respect to grade. When the excavation has been finished, the excavating and loading system 270 !' Ii .
I, -2 4 -.. li .i .. I .

_~952 can be removed by means of the inclination t~lat ~as used to dig ~he excava~ion and loading system into the excavation.
The hydraulic cylinders 286 may also be utilized to form an upwardly inclined ramp at the opposite end of the excavation, whereby the excavation and loading system 270 digs itself out of the excavation.
! The excavation and loading system 270 further includes an excavating wheel assembly 290 which is - li pre~erably substantially identical in construction and ¦, operation to the excavating wheel assembly described I, hereinbefore in connection with the excavating and loading ¦' syste~ 20. Thus, the excavating wheel assembly 290 comprises ~hree ex-avating wheels spanning substantially continuously ¦1 acxoss .he front of the vehicle 272 and having an overall lS i' width at least equal to that of the remainder of the li excavating and loading system. The three excavating ¦ wheels 292 are all rotatably supported on axles 294 by suitable bushings, and each wheel 292 comprises a series 1l of diggi~g buckets 296 which are substantially equally 1I spaced around the periphery of the wheel.
¦I The digging buckets 296 of the excavating wheels 292 comprising the excavating wheel assembly 290 each comprisesa fixed bucket wall 298 extending inwardly j' from a plurality of replaceable digging teeth 300 of the 1'l type commonly used in excavation equipment. Each bucket 296 also includes a movable wall 302 supported for pivotal li movement between a material receiviny position and a material Ii 1l -25-.` ii ~2952 ~ discharging position. Thus, as each excavatiny wheel 292 is rotated, the movable wall 302 of each digging bucket 296 ' comprising the wheel is first positively moved to the 1 material receiving position and is subsequently moved , positively to the material discharging position. Any of ! the various mechanisms illustrated in Figures 7 through 12 inclusive may be utilized for the actuation of the movable I~ wall 302 of the digging buckets 296 comprising the excavating ¦i wheel assembly 290 of the excavating and loading system 270.
o 1! A major distinction between the excavating 1 system 10 illustrated in Figures 1 through 6 and the excavating and loading system 270 illustrated in Figures 14 ¦ and 15 involves the fact that the excavating wheel assembly , 290 OL- the excavating and loading system 270 is supported lS ¦ on a suoframe 310 which projects from the bottom of the front end of ~he vehicle 272 and which supports a moldboard 311.
The su~frame 310 includes spaced, parallel portions 312 which extend between the excavating wheels 292 comprising the excava.ing wheel assembly 290 and which support the I excava.ing wheels 292 by means of the axles 294. In the embodiment of the invention illustrated in Figures 14 and 15, the subframe 310 is fixedly mounted on the vehicle 272, and the hydraulic cylinders 286 comprise the sole means for adjustment of the inclination of the excavation formed by the excavating and loading system 270. However, it is also contemplated that the subframe 310 may be supported ,.......... I' .
.'.
1, l .~ ,1 :; li I I , ~057316 i' B~ 52 , on the vehicle 272 for pivotal movement under the action ,. of suitable hydraulic actuators connected between the !; frame 274 of the vehicle 272 and the subframe 310. .
¦ The excavating and loading system 270 is further S ¦ distinguished from the excavating and loading system 20 in that a single engine 314 mounted on the vehicle 272 is utilized to supply all of the operating power for the excavating and loading system 270. The engine 314 drives ¦ a plurality of hydraulic pumps 316, which in turn supply loperating power for many of the components of the excavating ~.
l and loading system. The engine 314 further has an output shaft 318 which extends through a clutch 320 to a universal ¦joint 322. The universal joint 322 connects the shaft ~318 to a shaft 324 which extends to a right angle drive 326.
; 15 IThe rght angle drive 326 actuates a pair of relatively small diameter sprockets 328 which are coupled through a pair of chains 330 to a pair of relatively large diameter sprockets 332. The sprockets 332 drive a series of pinions 334 Iwhich are mounted in mesh with ring gears 336 secured on ¦the excavating wheels 292. By this means the output of ¦Ithe engine 314 is directly coupled to the excavating wheel ¦lassembly 290 through a drive train extending in part through Ijthe subframe 310 and hence between.the three excavating ¦wheels 292 comprising the excavating wheel assembly.
¦l It will be understooa that the spaced, parallel ¦jportions 312 of the subframe 310 comprise hollow box-like ~ -27-ll I
I

1~ ~0573~6 . :
~952 members of the type illustrated in Figurcs 2, 3, and 6 in conjunction ~ith the excavating and loading system 20. The spaced, parallel portions 312 therefore serve not only to , support the excavating wheel assembly 290, but also to , enclose the sprockets 328, the chains 330, and the sprockets -332 of the drive system for the excavating wheel assembly.
A major design feature of the excavating and loading system 270 involves the fact that the excavating wheel assembly 290 is supported on the subframe 310 by !~ means of three axles 294 which are secured to the spaced, jl parallel portions 312 of the subframe 310 by means of flanges 234', and suitable fasteners. This leaves the ¦ inter-ors of the spaced, parallel portions 312 entirely open, ~hereby the diameters of the sprockets 332 may be ¦¦ selected to provide the particular speed and torque inputs to the excavating wheel assembly 290 that are required for

3 a given ~xcavating situation. On the other hand, if a single a~le extending the entire width of the excavating i wheel assembly were to be used, the maximum diameter of Il the sproc~et 332 would be substantially restricted.
¦l The ability to vary the speed and torque inputs to the excavating wheel assembly 290 by changing the ! sprocket wheels 332 has been found to comprise a substantial I! advantage. Thus, the operation is carried out quite easily il by merely exchanging the sprockets 332 and adjusting the ~, lengths of the chains 330. Moreover, changing the sprockets 332 jl 28-.~ o B~ 52 does not effect the design criteria of the upstream components of the drive train. On the other hand, if another component of the drive train were to be changed in order to provide ' required torque and speed inputs to the excavating wheel , assembly 290, various downstream components might also ' have to be changed in order to accommodate increased loads.
The excavating and loading system 270 further , includes a loading system 340. The loading system 340 comprises a main conveyor 342 which receives excavated o ~! material directly from the center excavating ~7heel 292 of ¦¦ the excavating wheel assembly 290 and which transports the l, excavated material upwardly and rearwardly to a discharge ; ¦I point at the extreme rear end of the vehicle 272. The !¦ system 310 further includes a pair of cross conveyors ¦1 ` 344 which receive excavated material from the two outside excavating wheels 292 of the excavating wheel assembly 290 ¦! and whicn transport the material to the main conveyor 342.
¦~ As is ~est shown in Figure 14, the rear portion of the I main conveyor 342 is selectively pivotable about the axis 1 of a pin 346 under the action of hydraulic cylinders 348 ! mounted on the opposite sides of the vehicle 272.
.~ Ii The excavating and loading system 270 may also be provided with an auxiliary conveyor system 350. In 1~ such instances, the auxiliary conveyor system 350 is 1¦ connected to the extreme rear end of the frame 27~ of the vehicle 272 and is utilized either to discharge the excavated material into trucks or other vehicles or to .~ i -29-.' I

,., 11 ~057316 2952 discharge the excavated material latcrally with respect to the excavation being formed. The auxiliary conveyor system 350 is preferably idcntical in construction and , operation to the auxiliary conveyor system 150 described ', in detail hereinbefore in conjunction with the excavating ' and loading system 20.
An additional feature of the excavating and i loading system 270 comprises an operator's compartment 352 li positioned at the top of the front end of the vehicle 272 l' to facilitate concurrent observation of all of the operating ! instru.~entalities of the excavating and loading system 270.
I The operator's compartment 352 includes the usual operator's ¦~ seat 35~ and a console 356 comprising the usual gauges, ¦I switche3 and controls which are necessary for complete I regulation of the operation of the excavating and loading ¦I syste~ 270.
Figures 14 and 15 further illustrate an alternative `
jt usage o~ excavating and loading systems incorporating the !l invention. As will be appreciated by those ~killed in ¦! the art, the excavating wheels 292 of the excavating ¦ wheel assembly 290 are so constructed that the orientation of the center excavating wheel may be reversed with respect ¦ to the axle 294. Similarly, the outside excavating wheel 1 292 which is usually positioned on the right-hand side ¦! f the vehicle 272 may be mounted on the left-hand side thereor, and the excavating wheel 292 which is usually Il .
Il .

¦!
Il ~57316 B2952 mounted on the left-hand side of the vehicle may be mounted on the right-hand side thereof. At the completion of these steps, the excavating wheels 292 comprising the ; excavating wheel assembly 290 are oriented as shown in Figures 14 and 15. It will be noted that the orientation , of the mechanism which actuates the movable walls 302 of the digging buckets 296 of the excavating wheels is preferably not changed as the orientation of the excavating j wheels 292 is reversed. Thus, even though the excavating l, wheels rotate in the reverse direction, the movable wall 302 of each digging bucket 296 continues to be positively moved to the material receiving position as the digging buc~et moves through the lower forward portion of its Il rotatio~ and to be positively moved to the material ~; discharging position as the digging bucket ~s moved through the u~2er rearward portion of its rotation.
The orientation of the excavating wheels 292 of the excavating wheel assembly 290 in the manner illustrated li in ~igures 14 and 15 is considered to be particularly ¦ advantageous for the excavation of asphalt paving and ~ I similar materials. Thus, with the excavating wheels so oriented, the digging teeth 300 of the digging buckets 296 are moved downwardly and therefore engage the pavement or l~ similar material from above. This produces an anvil effect 1 so that the material is removed in the form of small pieces - i which are readily handled both by the excavating and loading Il .

, I

I, . `~

J
B2952 system 270 and by the trucks or other vellicl~s which will be utilized to receive the excavated material. Conversely, if the excavating wheels 292 of the excavating wheel , assembly 290 were operated in the conventional manner with the teeth 300 moving upwardly, the asphalt pavement or i similar material might tend to break away in the form of large plate-like sections. Such sections have proven to i be difficult to handle unless they are first further reduced I to relatively small pieces.
I Referring now to Figure 16, there is shown an ¦, excavating and loading system 370 comprising a fourth ¦, embGdi~ent of the invention. The excavating and loading syste~ 370 comprises a vehicle 372 which is preferably !~ substanLially identical in construction and operation to J~ 15 ¦i the vehicle 22 described hereinbefore in conjunction with ,; il ' the excavating and loading system 20. An excavating wheel , .
' assembly 374 is supported at the front end of the vehicle , 372 by means of a subframe 376. The excavating wheel I! assembly 374 comprises three excavating wheels 378 extending ll substantially continuously across the front of the vehicle 372 and having an overall width at least equal to that of the remainder of the system. The excavating wheels 378 are , prefera~ly substantially identical in construction and ~ operation to the excavating wheels utilized in the excavating ! and loading system 20.

. .
., , .

952 In the operation of the excavatin~ and loading system 370, material excavated by the center excavating wheel 378 is discharged onto a main conveyor 380 and is ~ transported thereby to a discharge point at the rear of the ! vehicle 372. Material excavated by the two outside excavating wheels 378 is discharged onto a pair of cross conveyors 382 which in turn discharge the excavated material onto the main conveyor 380. The excavating and loading 1 system 370 may also be provided with an auxiliary conveyor ¦~ system similar to the auxiliary conveyor system 150 of j the excavating and loading system 20, if desired.
¦ The major distinction between the excavating and loadir.g system 370 and the excavating and loading system 20 1~ compris~s the fact that the axis of rotation of the three I excavating wheels 378 comprising the excavating wheel assembly 374 is angularly offset with respect to a line extending perpendicularly to the longitudinal axis of the j vehicle 372. This has been found to be advantageous in j the excavation of relatively hard materials in that it ~ prevents the formation of ridges in the spaces between the excavating wheels comprising the excavating wheel assembly.
The cross conveyors 382 are also angularly offset so as to be properly positioned to receive material excavated by ! the two outside excavating wheels 378. Nevertheless, the ~! cross conveyors 382 discharge the excavated material onto ¦ the main conveyor 380 which extends parallel to the , , - I!
ll .1, ' B2952 longitudinal axis of the vehicle 372.
The excavating wheel assembly 374 of the excavating . and loading assembly 370 is driven by an engine 384 which is , mounted on the subframe 376 and which is positioned so .~ as to counterbalance the weight of the excavating wheel : assembly 374. The engine 384 has an output shaft 386 which ~ is coupled through a clutch 388 to a speed reducer 390 .: l and hence to a chain drive 392. The chain drive 392 is in , turn coupled through a shaft 394 to a right angle drive , 10 1~ 396. The right angle drive 396 in turn functions to ; 1 rotate the excavating wheels 378 of the excavating wheel ¦, assembly 374 by means of a pair of chain and sprocket ; i~ drive ~.ecnanisms extending between the excavating wheels 378.
1l Those skilled in the art will appreciate the j 15 il fact that due to the angularly offset positioning of the ! excavating wheel assembly 374, the excavating and loading system 370 functions to form an excavation extending between a plane 398 and a plane 400. This presents no problem lj except ~or the fact that the portion of the excavatian ij adjacent the plane 398 is formed entirely by the outside , teeth of the excavating wheel 378 adjacent thereto. To this end, the circular outside surface of the excavating ,I wheel 378 adjacent the plane 398 may be provided with .` il auxiliary cutting teeth 402 which function .o assist in l, the formation of the adjacent portion of the excavation.
, Figure 17 illustrates an accessory which may be utilized in conjunction with any of the various embodiments of ., j, '' -34-1l, 1, :' 1, , 1.

!
952 ' the invention described hereinbefore. Thus, the outside ,excavating,wheels 404 o~ an excavating wheel assembly 406 incorporating the invention may be provided with conical cutter members 408. The cutter members 408 are detachably ' ! mounted and are preferably provided with replaceable cuttin~
' teeth 409 of the type commonly utilized in excavating Ij machines of various types.
~, The purpose of the cutter members 408 is to form , tap2red side walls on the opposite edges of a cut or lo ! excavation formed by the excavating wheel assembly 406.
I I Assuming that the overall depth of the excavation does not exceed the radius of the excavating wheels 404, the side walls of the excavation will be tapered from top to bottom.
On th other hand, if the total depth of the excavation ' 15 ~l exceeds the radius of the excavating wheels 404, oniy the I lower ~ortion of the side walls of the excavation will be ' I~ tapered. In either event, it is often advantageous to i ~ provid- tapered side walls on an excavation, particularly ; ! in those instances in which the material being excavated , j does not have sufficient substance to retain a vertical side wall configuration.
Figures 18, 19 and 20 illustrate an alternate embodiment of the excavating and loading system incorporatin~
,' , the present invention. As will be appreciated by those of ¦~ skill in the art, the rear portion of the conveyors of an ; , excavating and loading system 420 is illustrated. This !!
il ' ~!

~!

i 1057316 B2952 excavating and loading system 420 can be utilized with , any of the excavating wheels previously illustrated and ,' described. The system 420, in addition, has a main ~ conveyor 412 similar to the one illustrated and described S ! in reference to Figures 1 through 6. As was previously -pointed out, the main conveyor 412 has a conveyor frame ¦¦ 414 supported on a main vehicle frame 416. The conveyor ~¦ frame 414 includes an upper portion 424 supported for - ,I pivotal movement about a horizontal axis 422 under the 11 action of hydraulic cylinder 426. This permits control ¦l over the vertical position of the material discharge end 419 of the upper conveyor portion 424.
The loading system 420 also includes a turntable assembly 425 supported on frame 452. Turntable assembly 1 425 supports an auxiliary conveyor assembly 450 identical to the auxiliary conveyor illustrated in Figures 1 through 6.
Conveyor assembly 450 includes an inner conveyor 460 for receiving material discharged at the material discharge ¦¦ end 419 of the main conveyor 412. The conveyor 460 comprises I a frame 462 with flanges 427 which extend down and are pivotally attached at 428 to the turntable assembly 425.
This pivotal attachment at 428 allows rotation of the auxiliary conveyor 450 in the forward and reverse 1, direction of arrow 430 to allow the raising and lowering 1 of the material receiving end 432 of auxiliary conveyor assembly 450. A hydraulic cylinder 434 is provided for . ~. causing the frame 462 to rotate about pivot 428.
l .
~ ~ -36-ll - , ~OS7316 ~2~ 2 ' The auxiliary conveyor system 450 can include an outer conveyor 472 having a frame 474, which is ,j' 3; supported from the frame 462 of the conveyor 460 by a pair Il of parallel links 476. A hydraulic cylinder 482 extends S ¦I between the frame 462 of conveyor 460 and the frame 474 ~, ~
' ¦¦ of the conveyor 472 for actuation to manipulate the conveyor 472. The upper link 476 and the cylinder 482 are pivotally connected to frame 474 by a selectively removable pin 436.
, The particular conveyor configuration illustrated in Figures 18 through 20 has important advantages which ¦ can be appreciated when it is considered that the size of ! the system 420 in some applications can be substantial. It is important to note that the discharge end 419 of the lupper portion 424 of the main conveyor 412 can extend to ¦substantial heights. In addition, the clearance height of ¦the auxiliary conveyor 450 can be considerable when it is understood that the conveyor is designed to extend to a ¦height substantially above a material transporter. This l~height can present problems in the transportation of the !1 excavating and loading system 420 from one site to another.
~This is particularly important when overhead clearance is llimited. ,~.
¦ In Figure 18, the system is shown in its fully-extended pos tion, but according to the particular feature ,' l . I
' ;
. 1, .32952 ', of the present invention, the conveyors 412 and 450 are adapted to be folded to a minimal clearance configuration.
The folding of the conveyors to a minimal clearance confi-' guration is illustrated in Figures 19 and 20.
1. The first step in the folding operation is . illustrated in Figure 19. In this Figure, hydraulic cylin~.er 434 is actuated to rotate the auxiliary conveyor 450 in the , direction of arrow 430, thus moving material receiving end ¦l 432 upward and to the rear. This position is illustrated i in Figure 19, the conveyor 450 positioned out of the folding path of conveyor 412. Hydraulic cylinder 426 is then actuatea i to rotate the material discharge end 419 of the upper conveyo portion 424 of the main conveyor 412 through a folding path in the direction of arrow 438. This movement continues until the discharge end 419 reaches the folded position illustrated in Figure 20. The auxiliary conveyor 450 is then rotated by hydraulic cylinder 434 from the position illustrated in I Figure 19 to the position illustrated in Figure 20 with the material receiving end 432 adjacent to and positioned I above the discharge end 419. In this manner, the material discharge end 419 is substantially lowered in height below the auxiliary convëyor assembly 450, thus reducing the clearance required to transport the excavating and loading system 420.
i The auxiliary conveyor 450 is also particularly adapted to facilitate transportation of the excavating and loading system 420. This is accomplished by disconnecting !
I
I -3~- .

I
I

952 the outer conveyor 472 and rotating the same to the position 472' illustrated in Figure 20. This folding of the outer conveyor 472 is accomplished by removing the pins 436 which allows the outer conveyor 472 to rotate in the direction of arrow 440 up under the frame of the inner conveyor 460 where a suitable latching means (not shown) ,, is utilized to retain the outer conveyor 472 in the folded position.
!~ It will be appreciated that the folding of I the conveyors as illustrated in Figures 18 through 20 provide particular advantage in the reduction of the clea.ance required for transporting the system 420 and redu-_s the rearward extension of the conveyor.
~, Referring now to Figure 21, there is shown a ~I forward portion of an excavating and loading system 500 ! with a moldboard assembly 502 mounted thereon. Those of , ordinary skill in the art will appreciate that this - ll embodihent of the moldboard assembly 502 and the other embodimonts hereinafter disclosed have particular ~ 20 ¦1 advantages when used with excavating and loading systems ¦ ~j of the type disclosed herein where a large heavy excavating wheel assembly is mounted on a subframe which is cantilevered from the front of the main vehicle frame. This heavy !i excavating wheel assembly creates vertical loads as the 1, vehicle translates during the excavating process. In 1~ addition, digging resistance on the excavating wheel ,, 1. :

i -39-, 1, 1, ,. , .

.

10573~6 B2~52 assembl~ varies as different types of material are encountexed by the excavating wheel. This will also create variable vertical loads which will tend to create a xocking ox bouncing motion of the fxame of the vehicle. This proble~
is fuxther complicated when the excavatin~ loading system is operated in a soft soil allowing the wheels to sink in the soil as the vextical loads are generated.
;i To counter this action, the moldboaxd assemblie incorporating the pxesent invention utilize a drag plate i which is positioned between the excavating wheel and the .
~' fxon~ of the vehicle frame and is designed to counteract thes~ undesirable vertical loads by contacting the soil surface. In some e~bodiments, this contact pressure is ¦ increas~d and decreased as the grade on which the excavating il, ~nd loading syste~ is excavating varies. In addition, j means are provided for varying the vertical pressure of the dxag plate.
The moldboard assembly 502, shown in Figure 21, has a blade portion 504 extending across the width of the I system ;00. The blade 504 is positioned below and to the l rear OL the excavating wheel assembly 506 to pick up j material dropped from the wheel assembly 506. In addition, if the wheel assembly 506 is configured, as illustrated in ¦~ Figure 3 with a plurality of spaced excavating wheels, 1, ridges will be formed between the individual wheels during !, the excavation operation. In operation, the blade 504 will 1, .
o ~!
1,l '.: - .. Il .

~057316 , ,2952 i' cut the ridges formed between the excavating wheels to provide a smooth-bottomed excavation. The blade 504 is a concave surface which crowds material forward until it 1 is picked up by the excavating wheel assembly 506.
i~ An additional function performed by the moldboard ; ¦~ assembly 502 is in stabilizing the excavating and loading ¦I system 500 during operation. This is accomplished by drag plate 508, sometimes called a drag shoe. The drag plate 508 Il is mounted behind the blade 504 and is positioned to contact l¦ the ground surface. The plate 508 supports the vertical ¦ component of the excavating wheel assembly's digging force and serves to stabilize the excavating and loading system 500 and resist vertical bouncing action.
¦ As those of ordinary skill in the art will I appreciate, the position of the blade 504 and the plate 508 ¦! must vary as the direction of the operation of the excavating and loading system 500 changes. To accommodate these changes, the blade 504 and plate 508 are rigidly attached together by a flange 512. It is envisioned that the blade 504 and plate 508 could alternatively be connected as illustrated in Figure 27. This flange 512 prevents angular ch~lnges between the lorientation of the blade 504 and plate 508 with respect ,l¦ to each other. A pair of link arms 514 are pivotally connected to the subframe 516. The subframe is in turn supported from ¦i a shaft 518 to rotate about a horizontal axis with respect ¦I to the main frame 520 of the excavating and loading system 500 A pair of hydraulic cylinders 522 are provided to rotate the ¦,subframe 516 with respect to the main frame 520.
I!
Il -41-, lOS~3i6 A pair of hydraulic cylinders 524 are connected between the main frame 520 and the flange 512 for rotating the :Link arms 514 with respect to the subframe 516. Thus, by selectively actuating hydraulic cylinder 524, the relative orientation between the blade 504 and plate 508, and the excavating wheel assembly 506 can be adjusted by the operator of the vehicle. The cylinders 524 preferably extend angularly outwardly from the frame 520 to the flanges 512 so as to stabilize the moldboard assembly 502 against lateral movement.
The particular configuration illustrated in Figure 21 provides advantages inherent in the operation of the moldboard assembly 502 which those of oridinary skill in the art will appreciate by referring to Figures 22a, 22b and 22c. In Figures 22a, 22b and 22c, a simplified link diagram of the operation of the moldboard assembly 502 in various cutting applications is illustrated.
In these Figures, the circular outline represents the excavating wheel assembly 506, the triangular link defined ~, ~
,SI by points A, B and C represents the subframe 516. Point "A"
;, represents the shaft 518 connecting the subframe 516 and the main frame 520. The point i'C" represents the axis of rota-s tion of the excavating wheel assembly 506 with respect to ;
,: the subframe 516. Line "B-E" represents link arms 514 ,,~. .
which support the blade 504 and plate 508. The point "B"
represents the pivotal connection between the arm 514 and the subframe 516. The link "D-E" represents hydraulic cylinders 524. The point "D" represents the pivotal connec-tion of the cylinder 524 to the main frame 520 while the point "E" represents pivotal connection between the .,.
., .

':

~5731t~

52 cylind~r 524 and the flange 512 on the blade 504 and drag E)late 508.
In Figure 22a, the use o~ the excavating and ~ ]Loading syst~m 500 and operation of the moldboard assembly 502 'j ,; in forming a level cut is illustrated. In this application i the drag plate 508 is relatively parallel to and flush with 1 the ground surface S. A plate 508 presses against the i surface S and provides vertical support for the excavating 1, wheel assembly 506. The link "D-E", representing a 0 1i hydraulic cylinder 524, can be adjusted in length to compensate for plate wear or so that the support pressure of the drag plate 508 can be adjusted to suit the soil ', conditions.
The particular advantages of the embodiment ~5 l,l of Figure 21 are also illustrated in Figures 22b and 22c. In ' these Figures, the grade of the excavation is greatly exaggerated to better illustrate the desired angular relationship of the excavating wheel assembly 506 and moldboard assembly 502.
0 , In Figure 22b, the apparatus is used to dig along a downgrade. The particular geometric relationship ~, of the moldboard causes the plate 508 to be automatically I depressed relative to the surface S, thus stabilizing the system as the excavation progresses. In Figure 22c ~5 , the system 500 is illustrated digging along an upgrade.
In this situation it can be seen that the drag plate 508 !;

!l -43-~,~2952 of the blade is raised relative to t~e surface, thus relieving drag. These configurations, illustrated in Figures 22a, 22b, and 22c, are automatically provided by the ', geometry of the apparatus.
This operation is the result of the use of a `' , four-bar type linkage wherein the links AB and DE are approximately parallel and where the blade 504 and plate 508 are fixed relative to the link BD.
~, Thus, it can be seen that a moldboard assembly 1, 502 is providQd with a blade which is raised and lot~ered ;' !~ in an am.ount proportional to the raising and lowering of the excavatin~ wheel assembly 506. In addition, the drag l! plate increases the vertical pressure on a downgrade and decra2~e~ the pressure on an upgrade.
¦, In Figures 23 and 24, a third embodiment of a moldboard assembly, incorporating the present invention, l' is illustrated. The moldboard assembly 550 is supported ,i from ~ rigid frame type excavating and loading system 551.
! The rigid frame system 552 is of the type having a subframe 554 which supports the excavating wheel assembly 556. The I' front wheels 558 are provided with a frame 559 movably connected to subframe 554 by arms 561. The rear wheels (not I! shown) are rotatably connected to subframe 554. A hydraulic i 25 ! cylinder 557 is connected between frame 559 and subframe 554.
', ¦' By controlling the operation of cylinder 557, the height , of subframe 554 with respect to the frame 559 can be adjusted 1, .

11~

~l -44-: ~057316 .
952 The moldboard assembly 550 is connected to the frame 554, as illustrated in Figure 23. The embodiment utilizes an elonqated blade 560, ~hich is pivotally attached t , at 562 behind excavating wheel assembly 556. A drag plate 564 is pivotally attached at 566 to the blade 560. A turn buckle is pivotally attached between the drag plate 564 and the frame 554. A selectively operable hydraulic I cylinder 570 is connected between the frame 554 and the ', pla~e 56~.
; 10 li The moldboard assembly 550 is mounted on the ,l, fxa~e Oc the excavating wheel assembly and can be raised and lo~erea as the excavating wheel is raised and lowered.
' The or-e~tation of the blade is not varied by the raising 1~ and lo-~ering of the excavating wheel assembly 556. The 1~ position of the blade 560 and the drag plate 564 are selecti~ely controlled by operation of hydraulic cylinder , 570 In Figure 24, operation of the moldboard assembly 550 ' is illus~rated. The cylinder 570 is actuated and elongated, ~ thus mo~ing the blade 560 down~ This downward movement also .1 l ; moves the drag plate 564 downward increasing the pressure I on the plate. It is apparent that if the cylinder 570 ¦l is shortened, the blade 560 will be raised and the drag , plate pressure will be reduced.
¦, In Figures 25 and 26, a fourth embodiment of ¦', a moldboard assembly 600 incorporated in the present 11 invention is illustrated. The moldboard assembly 600 is . ,i I' ~ -45-,, ~, , 1' .

~0573~6 i, ..
952 1, specifically adapted for mounting on another fixed fra~e type system. The moldboard assembly 600 is mounted on an excavating and loading system 602 which is identical in , construction to the vehicle illustrated in Figures 14 and 15.
As was previously described, the excavating wheel assembly i 604 is supported from a frame 606, which is connected by j hydraulic cylinder 608 to a track assembly 610. The I excavating wheel assembly 604 is raised and lowered with I respect to the track assembly 610 by means of a hydraulic ' cylinder 608.
. I In Figure 26, the details of the moldboard assembly 600 are illustrated. A blade 612 and a fixed position bearing plate 614 are provided on the assembly 600.
! The upper end 616 of the blade 612 is restrained in a ¦ slot 618 of the frame 606. The end 616 is retained in ¦ the slot and is allowed to move in the slot in the forward ¦ and reverse directionsof arrow 620. A pair of link bars 622 are pivotally connected to the frame 606 at 624 and ¦ pivotally connected to the blade 612 at 626. Hydraulic ¦ cylinders 628 are connected between the frame 606 and extending ends of the links 622. Links 630 are pivotally j connected between the links 622 and the rear of the bearing I plate 614.
¦ It will be apparent to those of ordinary skill I in the art that by operation of the hydraulic cylinder 628, the blade 612 will be caused to move in the forward and revers directions or the arrowb 620 and be rcstrained ' .

~057316 ~2952 by the slot 61~. The bearing platc 614 wi]l move in a likewise manner.
It is to be pointed out that the moldboard assembly 600, illustrated in Figures 25 and 26, operates in a manner similar to the moldboard assembly illustrated in Figures 23 and 24. ~he moldboard assembly 600 is raised and lowered with the excavating wheel assembly 604 as the frame 606 is raised and lowered. The blade edge and drag plate positioned on the blade is controlled by a hydraulic ~ -, 10 ll cylinder and can be operated to increase drag plate pressure ¦, as the blade is lowered.
It is also envisioned that the bearing plate 614 ~! coulc b connected to blade 612 at 632 in a manner which 1I permi.s angular freedom between the plate and the blade.
¦! Figure 27 illustrates a fifth embodiment of a ¦~ moldbo~rd asse~bly incorporating the present invention.
In this embodiment, an excavating and loading system 650 is illl~strated having a subframe 652 and a wheel frame 654 , , suppor'ing treaded wheels 656. The subframe 652 is ' 20 ¦i pivotally connected to wheel frame 654 at pivot 655.
, A hydraulic cylinder 65~ is provided selectively to raise and lower the subframe 652 with respect to the ~' wheel frame 654. This in turn controls the digging height ¦! of the excavating wheel assem~ly 660 supported from frame l' 652.

., I
. l '' .
~ 47-.~ I
i,, ., ' ,.
~' .. ~ ' ' ~057316 ~2~52 The molclboard assembly 662 has a blade 66~ which is rigidly carried by a pair of arms 666. ~rms 666 are pivotally mounted on the wheel frame 654 and a pair of hydraulic cylinders 668 connect the arms 666 to the frame 652.
By selectively actuating the hydraulic cylinders 668, the position of the arms 666 and blade 664 can be varied.
, The drag plate 670 is pivotally attached at 672 to the rear of the blade 664. A second pair of hydraulic ' cylinders 673 are connected between the drag plate 670 and the j arms 666 to pivotally adjust the relative position of the drag ?late 670 with respect to the blade 664. This provision !~ of pivotal adjustment of the plate 670 could also be used with : 1, the e,~bodiment illustrated in Figure 21.
I' In operation, as the frame 652 is raised and 1~ 1 lower~, the geometry of the moldboard assembly 662 is ' such ':~' the blade 664 and plate 670 are raised and ' lowered proportional to the amount that the frame 652 and excavating wheel assemblies 660 are raised and lowered.
Ii The geo~etry is such that the drag plate bears with j~ decreas-d pressure as the blade is lowered and with ~' increased pressure as the blade is raised. In addition, a separate control for the position of the drag plate l! iS us~a.
The particular configuration illustrated in ~5 l~ Figure 27 provides advantages inherent in the operation ! of the moldboard assembly 662 which those of ordinary . 1 :~ tl ,. ~i Il -48-!
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10573~6 .

B~452 ! skill in the art will appreciate by refcrring to Figures :, 28a, 28b, and 28c. In Figures 28a, 28b, and 28c, a ! simplified link diagram of the operation of the moldboard I~ assembly 662 in various cutting applications is illustrated.
' In these Figures, the circular outline represents the excavating wheel assembly 660 and the triangular link defined by points A, B, and C represents the subframe 652.
Point "A" represents the pivot 655 connecting the subframe , 652 ana the frame 654. The point "C" represents the ! axis of rotation of the excavating wheel assembly 660 with respect to the subframe 652. Link "D-~" represents link arms 666 which support the blade 664 and plate 670. The i link "B-E" represents hydraulic cylinders 668. The point , "B" represents the pivotal connection between the subframe lS 1 652 and the cylinders 668. The point "D" represents the pivotal connection of the arms 666 to the frame 654 while the point "E" represents pivotal connection between the cylinder 668 and the link arms 666.
I In Figure 28a, the use of the excavating and I loading system 650 and operation of the moldboard assembly 662 in forming a level cut is illustrated. In this application, the drag plate 670 is relatively parallel to and flush with the ground surface S. A plate 670 presses li against the surface S and provides vertical support for 2' the excavating wheel assembly 660.

~057316 ,, ~_~952 The particular advantac3cs of the embodiment of Figure 27 are also illustrated in ~igures 28b and 28c.
In these Figures, the grade of the excavation is greatly exaggerated to better illustrate the desired angular S relationship of the excavating wheel assembly 660 and moldboard assembly 662.
1 In Figure 28b, the apparatus is used to dig j along a do~mgrade. The particular geometric relationship of the moldboard causes the plate 670 to be automatically j, raised relative to the surface S, thus reducing the plate ¦' pressu~e. In Figure 28c, the excavating and loading ; 1I sys,e.~ 650 is illustrated digging along an upgrade. In ¦~ this situation, it can be seen that the drag plate 670 is ¦ lowere~ relative to the surface, thus increasing drag.
¦~ Thes~ configurations, illustrated in Figures 28a, 28b and ! 28c, a-e automatically provided by the geometry of the ¦ apparatus.

This operation is the result of the use of a four-~ar type linkage wherein the links AB and DE are ¦, approximately parallel and where the blade 664 and plate i 1l 670 are fixed relative to the lin~ DE.
il Thus, it can be seen that a moldboard assembly 662 is provided with a blade which is rais~d and lowered 1' in an amount proportional to the raising and lo~lering of 1! the excavating wheel assembly 660. In addition, the drag !j plate increases the vertical pressure on an upc~rade and decreases the pressure on a downgrade.
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~2952 , In Figure 29, a sixth ~mbodim~nt of a moldboard assembly incorporating the invention is illustrated. In this Fisure, an excavating and loading system 710 is , illustrated. Loading system 710 has a main frame 712 with ~ a forward mounted operator cab 714. A track wheel assembly 716 is connected to the frame 712 of the loading system 710 ' as previously described, in respect to other embodiments.
An excavating wheel assembly 718 is supported , on the front of the loading system 710. The assembly 718 has excavating wheels with movable bucket walls as illustrated in Fisures 7 through 12. An excavating wheel subframe l 719 is ?ivotally attached at 720 to a protruding portion ' 722 o~ the frame 712. Excavating wheels 724 are pivotally ¦l attac:~-d to the frame 719 and are driven by shaft 725.
According to a particular feature of the present , invention, the position of the excavating wheel assembly ¦' 718 and a moldboard assembly 726 are controlled by a I, crank G~m linkage. The crank arm linkage has a crank ¦¦ arm 728 which is pivotally attached at 730 to the upper ~ ¦~ portion of the front of main frame 712. A hydraulic ' cylinder 732 is connected between the main frame 712 ¦~ and tne crank arm 728 to selectively control the rotation of the crank arm 728 about the pivot 730. A connecting I link 734 is pivotally connected between the crank arm ¦~ 728 and frame 719. The excavating wheel assembly 718 ¦ will be caused to rotate about pivot 720 in the forward il !1 -51-~' ii i ~057316 ~_~952 and reverse direction of arrows 736, as the cylinder 732 is operated. This in turn, ~ill raise and lo~er the excavating wheels 72~ with respect to the ground surface "S" to control the diggin~ depths.
A blade 738 is rigidly attached to a pair of ' arms 740 which are in turn pivotally connected to the por~ions 722. The blade 738 is positioned under and to the rear of the wheel 724 to pic'~ up and crowd material in z for~zrd direction. A control link 742 is pivotally I connected between the arm 740 and arm 728. This link 742 I, is provided with means for selectively alterating the ! leng-h t'-.ereof and is utilized to set the position of the il2~-9 738 with respect to the wheel 724. In a like~ e manner, it ~an be seen that by rotating the j arm 723 by ~eans of the cylinder 732, the arms 740 will ' be ro ated, thus raising and lowering the blade 738. A
drag tlate 744 is pivotally attached at 746 to the rear ¦ of the blade 738. A hydraulic cylinder 748 is connected between blade 738 and plate 744 to selectively control i! the relztive position of the plate 744 and blade 738.
As those of ordinary skill in the art will ,1 appreciate, the blade 738 will be raised and lowered j' proportional to the movement of the excavating wheel 724 ¦ while the pressure exerted by the drag plate 744 can be ~1 independently adjusted by the hydraulic cylinder 748 as '~ a particular situation dictates.

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, -52-` 1057316 B2952 In Figures 30 and 31, a second embodiment of -~
the connection of the inner and outer conveyors of the auxiliary conveyor assembly is shown. In Figure 30, the extending end of an auxiliary conveyor assembly 800 is shown. This auxiliary conveyor assembly 800 has an inner conveyor assembly 802 which extends from the excavating and loading system. The auxiliary conveyor system 800 ' further comprises an outer conveyor assembly 804. The !;
l~ outer conveyor assembly has a frame 806 which is supported l from the frame 808 of the inner conveyor assembly 802.
, An endless belt 810 is supported by the frame 806 for !I movement around a course defined by a pair of parallel " jj drums 812 and 814. The belt 810 is driven by small ,', hydraulic motors (not shown) mounted in the drums 812 ~15 I, and 814. An endless belt 818 is supported on the frame 808 and is driven by a hydraulic motor (not shown) along the length of the conveyor 802 and around drum 820.
Conveyors 802 and 804 are interconnected by a pair of links 822 which are pivotally connected between the ~0 1l frames 806 and 808. The links 822 are preferably connected to the frames 806 and 808 by means of ball joints for increased reliability and stabilizing structure is preferably provided to eliminate side swing of the conveyor 804. A
I; first pair of variable length double-acting hydraulic '5 ~ cylinders 824 are connected between the frames 806 and 808 "
, at a position spaced away from and generally parallel to i' the links 822. A second pair of hydraulic cylinders 826 are connected between the frames 806 and 808.

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-~_~32952 The hydraulic cylinders 826, when actuated, move the conveyor 804 from a position receiving material from conveyor 802 where the material is transported to , and discharged at drum 814. On the other hand, the , conveyor 804 can be moved to a position where material is '. discharged directly from the conveyor 818 at the drum 820.
!' The hydraulic cylinders ~24 are provided to adjust the height of the outer end of the conveyor 804.
This is accomplished by varying the lengths of hydraulic j~ cylinders 824 to raise and lower the outer end so that ¦, it is adjacent to a truck into which material is discharged.
The ac.ion of hydraulic cylinders 824 rotates the outer ! COn~J2yO~ 804 in the forward and reverse direction of j; arro~ 828, as shown in Figures 30 and 31.
l; I! A deflection plate 832 is pivotally connected ' to the outer conveyor 804 adjacent to the drum 812. A
! pair of hydraulic cylinders 834 are connected between the ¦I plate 832 and the frame 806. These cylinders 834 can Il be actu~ted to control the position of the plate 832.
jl During discharge into a vehicle over drum 820, the j, deflection plate 832 can be appropriately positioned to ¦ deflect the material into the vehicle as illustrated in Figure 31. A similar deflection plate 836 is pivotally I attached adjacent to the end of the outer conveyor 804.
ll A pair of hydraulic cylinders 838 are connected between !l 1.
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i , ~52 arms 837 connected to the plate 836 and the frame 806. The cylinders 838 control the position of the plate 836 which is in turn utilized to deflect material exiting from the conveyor asse~ly 804 into a dump truck.
The configuration of utilizing the system to load separate dump trucks is utilized in Figure 31. -i In this embodiment, dump trucks 850 and 852 are shown in a side-by-side relationship respectively positioned under ; the ends of the inner and outer conveyors. As can be 0 seen, and as previously described, material can be -,s ~ , ,selectively discharged directly from the end of the inner ;
conveyor 802 and into the waiting vehicle 850. The deflection plate 832 is manipulated to direct the discharge of material from the conveyor. As has also been previously described, the conveyor 804 can receive material from the conveyor 802 and can be rotated down to the horizontal position identified in Figure 31 as 804'. In this position -material is discharged from the end of the conveyor 804' I and the deflection plate 836' is utilized to direct the :0 , material into the dump truck 852.
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In use, the dump truck 850 is first positioned under the end of the inner conveyor 802. The outer ! conveyor is positioned to allow the material to be discharged from the end of the inner conveyor 802 and into the dump , truck 850. While dump truck 850 is being filled, a second dump truck 852 can be placed adjacent to the dump truck 850.

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, 1l 10573~6 Upon completion of the filliny of the dump truck 850, the conveyor 804 can be moved to a position where it receives material from conveyor 802 and dischar~es thc material into the dump truck 852. Thereafter, the duinp truck 852 can move and other dump truck can be positioned under the inner conveyor 802.
Thus, in accordance with the invention described herein, an excavating and loading system comprising a vehicle has an excavating wheel assembly supported on 10 one end thereof for excavating the material and transferring the material to a main conveyor. An auxiliary conveyor is mounted behind the main conveyor for pivotal movement , .
generally outwardly and downwardly. This movement raises the material receiving end to the auxiliary conveyor.
The upward and rearward portion of the main conveyor is then pivoted do~mward into the space provided by the outward movement of material receiving end of the auxiliary conveyor. The auxiliary conveyor is then rotated over the discharge end of the main conveyor. This substantially reduces the overall height of the excavating and loading system for travel purposes.

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~0573~6 . .
B2952 In addition, the outer portion of the auxiliary conveyor is provided ~ith means for allowing the outer portion to be folded bac~ up wlder the inner portion of the auxiliary conveyor to further reduce the upward and rear.~ard extension of the system for travel purposes.
In accordance with another embodiment of the present invention, an excavating and loading system with an excavating wheel assembly at one end is disclosed.
~ Various mold~oard configurations are described supported , generally behind and beneath the excavating wheel assembly.
The mold30ard assembly is pivotally supported, and a link~e connects the moldboard to apparatus which controls the ve-'ical position of the excavating wheel assembly.
,, The mol~oara is automatically lowered as the excavating 1I wheel assembly is lo~qered to initiate an excavation and ~' is raised as the excavating wheel assembly is raised to ¦, termina e an excavation. The moldboard itself provides ~i stabil-zation to partially support the excavating wheel 1, assembly. Various mechanisms are disclosed for varying ¦~ the sup?ort force provided by the moldboard assembly.
j In accordance with other embodiments in the present invention, an excavating and loading system is , described comprising a vehicle having an excavating wheel ~' at one end thereof and a main conveyor and auxiliary l, conveyor at the other end. The au~iliary conveyor assembly has two in-line conveyors. The innermo;t conveyors ' - S 7 ~

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B~952 arranged to selectivel~ discharge material onto the other conveyor or into a vehicle. The outer conveyor is adjustable in attitude with respect to the inner conveyor to control the discharge height OL the outer conveyor. Deflector plates are mounted at the discharge ends of the inner and outer , , conveyors to direct the discharging material therefrom.
Although particular e~bodiments of the invention ~ have been illustra~ed in the accompanying Drawings and ,", 1:
.1 desc-ibed in the foregoing Detailed Description, it will ~, be understood that the invention is not limited to the embodi~ents disclosed, but is capable OL numerous ~1 rearr2-.~ements, modifications, and substitutions of parts ¦ and el_~.ents without departing from the spirit and scope of the invention as aefined in the appended claims.

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Claims

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. An excavating wheel comprising:
a pair of spaced apart side plates each extending radially outwardly with respect to a central axis of rotation;
a plurality of stationary walls each extending between the side walls and each having outwardly projecting material cutting means;
a plurality of movable walls each extending between the side walls for cooperation with one of the stationary walls to define a digging bucket;
said plurality of stationary walls and said plurality of movable walls cooperating to define a plurality of digging buckets positioned immediately adjacent one another to define the entire periphery of the excavating wheel;
each of said movable walls being supported for pivotal movement between a material receiving position and a material dumping position; and movable wall pivoting means entirely enclosed by the digging buckets and the side walls and responsive to rotation of the excavating wheel for positively pivoting the movable wall of each digging bucket to the material receiving position during one portion of said rotation and for positively pivoting the movable wall of each digging bucket to the material dumping position during another portion of said rotation; said movable wall pivoting means comprising:
a spring connected to each movable wall for normally positioning the movable wall in the material receiving position;
a cam mounted on each movable wall; and means positioned over the material receiving portion of a conveyor means for cooperation with the cams on the movable walls to pivot the movable walls to the material dumping position against the action of the springs.