A material conveying system capable of traversing a surface along an elongated path having at least one curvilinear portion. The conveyor structure includes a plurality of framework members arranged in tandem on the surface of the elongated path. There are connectors on each framework member which are cooperable with connectors on each adjacent framework member for coupling the plurality of framework members to form the train. Each framework member has a series of rails to support an upper and lower run of an orbitally moveable crawler chain which engages the surface and which chain is capable of propelling the conveyor along the surface. At least some of the framework members include support structure for supporting an orbitally moveable conveying belt above the orbitally moveable crawler chain. The conveying run of the orbitally moveable conveying belt is operable to convey material substantially throughout the entire longitudinal extent of the conveyor train either while the train is moving or is stationary.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
The present invention relates to conveyor systems, and more particularly, 
is directed to a self-propelled articulated conveyor system adapted to be 
driven along the mine surface by an elongated crawler chain and which 
conveyor system is capable of traversing curvilinear paths. 
2. Description of the Prior Art 
In mining operations, especially underground mining operations, such as, 
coal mining or the like, conveyors or series of conveyors are used to 
transport the mined ore from the mine. Normally, there is a main conveyor 
that moves the mined material along a fixed path. The main conveyor has a 
terminal end at a fixed location for receiving the material being mined. 
In the past, shuttle cars or other short distance haulage vehicles have 
been used to transport the mined material from the mining machine to the 
fixed terminal end of the main conveyor. The use of shuttle cars and other 
such haulage vehicles is intermittent, time consuming, and inefficient in 
not providing for the continuous transport of the mined materials from the 
mining machine to the fixed conveyor. Thus, in more recent years there 
have been several developments directed toward a mobile articulated 
conveyor that provides for continuous transport of the discharge of a 
continuous miner to the main conveyor as the miner advances into the mine 
face and changes the direction of its forward movement. Such mobile 
articulated conveyors are particularly adaptable to "room and pillar" type 
coal mining operations wherein the mobile conveyor follows the continuous 
miner and changes in direction as the machine penetrates into the mine 
face in one room and then is backed out and set to work in the mine face 
of another room while roof bolts are installed in the recently mined room. 
The mining machine is then backed out of this second room and set to work 
in either the recently roof-bolted room or it may go on to still another 
room. 
One of these more recently developed mobile articulated conveyors is shown 
in the Payne et al patent, U.S. Pat. No. 3,707,218, and sold under the 
trade designation "Serpentix". The Serpentix conveyor has an endless 
trough shaped, accordion-pleated belt supported on a vertebrae-like member 
which, in turn, is supported on the mine floor by stanchions. The 
stanchion supported conveyor was cumbersome and did not lend itself to 
frequent shifting of the conveyor path from room to room. Thus, Craggs, as 
shown in U.S. Pat. No. 3,920,115, suspended the Serpentix conveyor from an 
overhead monorail and thereby provided a flexible frame conveyor which 
could be attached to the surge car behind a mining machine. The conveyor 
could now follow the mining machine as it moved from one room to another 
in performing its mining operation. 
Another development in such mobile articulated conveyors is disclosed in 
McGinnis U.S. Pat. No. 3,701,411 which shows a conveyor comprised of an 
endless belt supported on a train of pivotally interconnected portable 
cars or carriages. Each of the carriages are supported on ground engaging 
wheels thereby providing mobility to the conveyor. A self-propelled 
tractor is connected to the conveyor train to move it from one location to 
another. Another development along the same lines can be found in U.S. 
Pat. No. 3,863,752. 
A later McGinnis patent, U.S. Pat. No. 4,061,223, discloses a mobile 
articulated conveyor suspended from an overhead monorail. Shown is a 
U-shaped conveyor belt carried by a plurality of individual carriage units 
suspended from the overhead monorail. The carriage units are fastened to 
one another by a resilient, flexible spline member which provides for 
positioning of the carriage units around vertical and horizontal curves. 
The conveyor belt is driven by a separate power belt and guided by guide 
rollers. 
The Assignee of Applicant's invention has obtained U.S. Pat. No. 4,339,031 
which discloses a mobile monorail suspended conveyor system. While this 
conveying system has shown promise in higher seams of coal and other 
mineral mining, there is a limit to the seam height in which one can 
utilize a conveyor system suspended from an overhead monorail. 
United Kingdom Pat. No. 1,373,170 discloses a self-propelled conveying 
system which can convey minerals and can move itself from one place to 
another after the conveying function is no longer required. As can be 
seen, an obvious draw back to this system is that the conveyor is not 
capable of continuously conveying material from the input end to the 
discharge end while the conveying system is being moved to another site. 
SUMMARY OF THE INVENTION 
The preferred embodiment of the conveyor system, as disclosed herein, 
includes various unique features for facilitating the transport of 
materials from a first location, such as an area where a continuous miner 
is working, to a second location, such as where the receiving end of a 
second conveyor is positioned, wherein the travel path defined between the 
first and second locations includes horizontal and/or vertical curves. 
While these unique features are particularly adapted for conveying 
materials along a curvilinear path, such as experienced in underground 
mining operations, it will be readily apparent that some of such features 
may be incorporated, either singularly or together, into above-ground 
conveying systems for conveying materials either along linear or 
curvilinear paths, as well as for conventional above and below ground 
flexible conveyors and thereby improve the same. 
It is, accordingly, the principal object of the present invention to 
provide a conveyor system with an articulated conveyor in which the 
aforementioned problems of the prior art have been overcome which is 
simple and inexpensive in structure, reliable in operation, and is so 
constructed to present a low-profile enabling the same to maneuver around 
pullers and through low-clearance passageways. 
More particularly, an object of the present invention is to provide an 
improved articulated conveyor which is supported by the floor of a mine 
and which is capable of traversing a curvilinear path while maintaining 
the conveyor run portion of an orbital conveying belt in an operative 
mode. 
More specifically, an object of the present invention is to provide an 
articulated conveyor which includes a train of framework members which 
support a crawler chain or crawler track in engagement with the mine 
surface and which cooperate with adjacent framework members to maintain 
the entire conveyor train in a predetermined disposition relative to an 
elongated path along a mine floor. 
Yet another object of the present invention is to support an orbitally 
moveable elastomeric conveyor belt within a relatively short distance of 
the mine floor to permit conveyance of mined material either while the 
entire conveying system is in motion or is stationary with respect to the 
mine floor. 
Still another object of the present invention is to provide a conveyor with 
an improved traction drive system for moving the mobile articulated 
conveying system along the mine floor either straight or along curvilinear 
paths while substantially eliminating any binding or other deleterious 
forces normally associated with or resulting from moving a rigid member 
through horizontal or vertical curved paths. 
Still another object of the invention is to provide a conveyor system 
having a flexible track drive system capable of bending around horizontal 
and/or vertical curves while delineating a fixed elongated path within a 
mine. 
Pursuant to these and other objects, the present invention sets forth a 
conveying system comprised of a plurality of tandemly disposed framework 
members that are connected to one another by an articulated joint so as to 
permit each framework member to move universally relative to adjacent 
framework members and to permit the train of framework members to be moved 
in unison along a curvilinear path. Each of the framework members defines 
an open extent extending longitudinally therethrough which includes a 
means for supporting an orbital conveyor belt which extends longitudinally 
within the open extent of the conveyor train and is located above the 
track or crawler chain system also mounted on the framework members. 
Mounted on the respective ends of adjacent framework members are portions 
that form the articulated joint which thereby connects adjacent framework 
members and permits universal movement of one framework member relative to 
its tandemly disposed adjacent framework member. In the preferred 
embodiment, the conveyor train is supported on the lower run of the 
crawler chain or track assembly which is capable of driving the conveyor 
train along the mine surface. 
Mounted on the ends of adjacent framework members are structures which 
cooperate with one another so as to selectively limit the longitudinal 
movement of adjacent framework members relative to one another during a 
longitudinal movement thereof. Other structures are utilized to limit 
horizontal, vertical and twisting movement of the framework members so as 
to maintain both the conveyor belt and the crawler chain assemblies in 
proper alignment. 
The articulated conveyor system is moved along the mine surface by traction 
drive means located in at least one of the framework members and capable 
of driving the track or crawler chain assembly. 
These and other advantages of the present invention will become more 
apparent upon reference to the following detailed specification and 
drawings.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
In the following description, it is to be understood that such terms as 
"forward", "rearward", "left", "right", "upward" and "downward", etc., are 
words of convenience and are not to be construed as limiting terms. 
IN GENERAL 
Referring now to the drawings, and particularly to FIGS. 1 and 7, there is 
shown a conveying system having a mobile articulated conveyor which is 
adapted to be mounted above an endless crawler chain and which conveyor 
and crawler chain are capable of traversing curvilinear paths. This 
conveyor system is indicated generally by the numeral 10 and comprises the 
preferred embodiment of the present invention. 
As is shown in FIGS. 1 and 7, the conveyor system 10 generally includes an 
articulated conveyor, generally denoted as 11, having an orbitally 
moveable conveying belt 12 supported by a train of framework members 14 
interconnected in series which support the conveying belt 12 throughout 
the longitudinal extent of the train. In the preferred embodiment the 
train has a discharge end 16 and a material receiving end 18 at an end 
opposite the discharge end. 
In the preferred embodiment, the receiving end 18 includes steering means, 
such as hydraulic cylinders 13, for directing the advancing conveyor train 
along an elongated path within the mine. Steering means may also be 
included at the discharge end 16 to steer the conveyor system 10 during 
retreat from the mine face. 
Each framework member 14 further supports an orbitally moveable crawler 
chain assembly 20 (FIG. 3) located generally vertically below the conveyor 
belt 12. 
As can be seen in FIG. 1, there is normally a stationary panel belt 22 
located within the mine for receiving material discharged by the discharge 
16 end of the conveyor system. Various methods and arrangements of the 
actual discharge of material from the conveyor belt 12 onto the panel belt 
22 will be discussed in detail hereinafter. 
For purposes of illustration only in the preferred embodiment the orbital 
conveying belt 12 is of the type originally disclosed in U.S. Pat. No. 
4,387,801 to Merrill Hoover entitled "Conveyor Belt". The Hoover belt is a 
pre-controlled stretchable belt formed of a stretchable elastic material 
having the ability to be pre-stretched or elongated by up to 10% as to 
maintain tension within the belt when going around curves. It is necessary 
to control and limit the elongation of the belt and various methods have 
been proposed to limit the stretch of the belt. Such methods are generally 
disclosed in U.S. Pat. No. 4,282,971 to Harry R. Becker entitled, 
"Conveyor Belt Chain and Method for its Use" and U.S. Pat. No. 4,474,289 
to Neal W. Densmore entitled, "Control Member for an Elongatable Conveyor 
Belt". The teachings of these patents are incorporated herein by 
reference. 
FRAMEWORK MEMBERS 
As discuseed above, a plurality of framework members 14 are connected in 
series to form the elongated conveyor system 10. As can be seen in FIGS. 
3, 4 and 5, each framework member 14 includes a bottom portion 30 which 
supports the crawler chain assembly 20 and, at predetermined intervals, 
the various drive components therefor. In addition, the bottom portion 30 
of the framework member 14 supports an upper portion 32 which contains the 
support elements for the orbitally moveable conveyor belt 12. 
In the preferred embodiment, the bottom portion 30 is composed of three 
sections. The two outer sections 34 and 36 serve to support the uppor 
portion 32. A central portion 38 is utilized to support and guide the 
upper and lower crawler pads 40 and the drive chain 44. The combination of 
the upper and lower crawler pads 40 and drive chain 44 make up the crawler 
chain assembly 20. 
In the preferred embodiment, the crawler chain 44 is formed in an endless 
loop with each crawler pad 40, attached to the chain in series along the 
entire length of the conveyor train. In the preferred embodiment, each 
crawler pad 40 is attached to the chain 44 by means of a U-shaped member 
43 welded to the under side of each pad. The links of chain 44 interact 
with the U-shaped member 43 when chain 44 is in tension to thereby move 
each crawler pad 40 along at the same speed as the drive chain 44. 
Each bottom portion 30 supports a pair of top runners 46 and a pair of 
bottom runners 48. As can be best seen in FIG. 4, the runners 46 and 48 
extend beyond the end portions 50 and 52 of the bottom portion 30. The 
runners 46 and 48 are supported by two pairs of stop plates 54 and 56. 
Each pair of stop plates 54 is welded to the end 50 of the bottom portion 
30 on opposite sides of the central portion 38. Each support plate 56 is 
fixedly attached to the end 52 of bottom portion 30 adjacent the central 
portion 38 thereof. In the preferred embodiment, the runners 46 and 48 
which are associated with end portions 50 and 52 are offset so that the 
upper and lower runners on adjacent framework members intermesh, thereby 
providing continuous support for the upper and lower crawler pads 40. 
In addition, in the preferred embodiment, the stop plates 54 and 56 are 
adapted to interact with the adjacent stop plate 54 or 56 of the adjacent 
framework member to limit the side-to-side motion therebetween. The 
limitation of horizontal angular movement between adjacent framework 
members 14 is provided by a pin-and-slot arrangement which can be best 
seen in FIGS. 4 and 5. A pin 60 is fixed to stop plate 54 and is 
positioned to engage a slot 62 in stop plate 56. In the preferred 
embodiment, the pin and slot are arranged approximately equal distance 
from the top and bottom of stop plates 54 and 56. 
In the preferred embodiment, when the framework members are aligned in a 
straight line, the pin 60 is centered within slot 62. When the conveyor 
train 10 negotiates a horizontal curve, the angular displacement in the 
horizontal plane between adjacent framework members 14 is limited, in 
either direction, by the pin 60 impinging on an end 64 of the slot 62. In 
the preferred embodiment, the permitted articulation between framework 
members 14 is approximately 5 degrees in either direction. 
The above described pin-and-slot arrangement also limits the roll (about a 
longitudinal axis) allowed between adjacent framework members 14. This 
limiting function is controlled by the width of slot 62 versus the 
diameter of pin 60. The difference between the width of slot 62 and the 
diameter of pin 60 permits approximately 2-1/2 degrees of roll between 
adjacent framework members. In the preferred embodiment, this means that 
the difference between the width of the slot and the diameter of the slot 
is approximately one inch. This roll limitation is necessitated by the 
normal condition of the mine floor which is generally very uneven. 
In the preferred embodiment, the central portion 38 of the bottom portion 
30 is provided with chain guides generally denoted as 70 for the upper 
chain guide and 72 for the lower chain guide. Each chain guide 70, 72 is 
composed of a pair of identical guide members 74 and 76. In the preferred 
embodiment, each chain guide member 74, 76 extends beyond the end plates 
50, 52 of the bottom portion 30 a sufficient distance to support the chain 
in the space between two adjacent framework members 14 and to act as a 
stop as described below. The preferred chain guides are of a cruciform 
shape so that alternate links of the chain 44 are maintained in parallel, 
but at right angles to the intermediately adjacent link. This structure 
positively entraps the chain keeping the links from either going upwards 
or sideways or twisting. 
The central portion 38 additionally supports a longitudinally extending 
force transmission member 78. In the preferred embodiment, the force 
transmission member 78 is a tube which passes through end-plate members 50 
and 52 and is fixedly supported thereby. As seen in FIGS. 3a and 3b, each 
end of tube 78 is provided with the necessary connection to form a 
universal type connection with each adjacent tubular member associated 
with an adjacent framework member 14. In the preferred embodiment, the 
tube 78 has a first end with a clevis-type arrangement 79 and a second end 
with a spherical ball joint arrangement 81. When the adjacent framework 
members 14 are interconnected as by pin 83, the opposite ends of the 
adjacent tube 78 are mated such that the clevis and ball joint are 
interconnected thereby forming a universal connection. This universal 
connection, of course, allows universal movement between adjacent 
framework members 14 and also transmits longitudinal forces (push and 
pull) between framework members. 
The tubular member 78 may be made of telescoping parts (not shown) which 
may be extended to take up slack in both the belt 12 and the chain 44 as 
wear of these parts occurs. A pin arrangement would be used to lock the 
telescoping parts of member 78 in an extended position. 
This movement is limited in the vertical direction by the chain guides 70 
and 72. In the preferred embodiment, the chain guides extend within a 
predetermined distance of one another to limit the vertical angular 
displacement between adjacent framework members 14 to approximately 6 
degrees. The 6-degree limit would determine the maximum angular 
displacement between framework members as the conveyor train moves up or 
down an inclined surface. As can easily be seen, the upper chain guide 70 
would determine the limit when the conveyor is progressing along an 
upwardly sloped incline and the lower chain guide 72 would provide the 
limit when the conveyor is progressing downwardly along an incline. 
In the preferred embodiment, the point of universal connection between ends 
80 and 82 of tube 78 are in line both vertically and longitudinally with 
the pins 60 located on each of plates 54. This arrangement allows the 
limits on both the twisting and horizontal movement of the conveyor, as 
discussed above, to be independent of the vertical inclination between 
adjacent framework members (i.e. as the leading framework member 14 starts 
going up an incline). 
As can be seen in FIGS. 3-5, each framework member 14 has an upper portion 
32 constructed as to define an opening extending generally longitudinally 
throughout the conveyor train. Within this opening, each framework member 
14 upper portion 32 includes mounting means for supporting an orbital belt 
within the open extent of the conveyor train. Since, as indicated above, 
all of the framework members 14 are identical, with the exception of the 
framework members which contain the drives for chain 44, only one will be 
discussed in detail. The chain drive system will be discussed in detail 
below. 
As can be seen in FIG. 3, the upper portion 32 of each framework member 14 
includes left and right conveyor belt support members 100 and 102. Support 
members 100 and 102 are bolted to the side portions 34 and 36 of the 
bottom portion 30. There exists a generally open area between member 100 
and 102 directly above bottom portion 30. 
A plurality of rollers comprise the means mounted on each framework member 
14 for moveably supporting the orbital conveying belt 12 within the open 
area of the carriage train. An upper series of roller are provided for 
supporting the upper conveying run portion 12a of the belt 12 and a lower 
series of rollers are provided for supporting the lower run portion 12b of 
the belt 12. 
Edge rollers 104 and 106 are mounted on brackets 108 and 109 respectively 
which are mounted across the bottom portion 30, thereby supporting edge 
rollers 104 and 106. The brackets 108, 109 are attached in any convenient 
manner to the end portions 34, 36 of bottom portion 30. In the preferred 
embodiment, a pair of belt support rollers 112 and 114 are also supported 
by and within brackets 108, 109. 
In the preferred embodiment, the upper conveying run portion 12a of the 
belt 12 is supported by respective left and right troughing idlers 116 and 
118 and a centrally-disposed dumbbell idler 120. As can be seen in FIG. 3, 
the troughing idlers 116 and 118 are disposed at a predetermined angle 
with respect to dumbbell idler 120 to give and maintain the upper 
conveying run 12a in a trough-shaped configuration. The troughing idlers 
116 and 118 are maintained at this predetermined angle by a pair of 
support brackets 122 and 124. 
For maintaining the upper conveying run portion 12a of the orbital belt 12 
in an operative position on the troughing idlers 116 and 118 and the 
dumbbell idler 120, each framework member 14 is provided with a respective 
left and right upper edge idler 126 and 128. The edge idler 126 is 
supported on bracket 122 and the edge idler 128 is supported by bracket 
124. As can be seen in FIG. 3, the left and right edge idlers 126, 128 
rotate about an axis oriented generally perpendicular to the axis of 
rotation of troughing rollers 116 and 118. This orientation of the edge 
rollers provides rolling support for the edge of the belt and minimizes 
scuffing. 
The dumbbell roller 120 is so formed to allow space for the stretch 
limiters (described in U.S. Pat. No. 4,474,289) that control the 
elongation of the belt. The edge rollers 104 and 106 perform the same 
function for the lower run of the belt 12b as do the edge rollers 126, 
128. 
In the preferred embodiment, the belt 12 is driven at each end of the 
elongated conveyor train by an electric motor and speed reducer (not 
shown). The details of this drive are taught in U.S. Pat. No. 4,339,031 in 
FIGS 21-23, and are incorporated herein by reference. It can be seen that 
there are any number of well-known methods for driving an orbital conveyor 
belt which could also be utilized in the present conveyor train. 
In the preferred embodiment, the conveyor train is normally between 200 and 
500 feet long, although any convenient length can be utilized as long as 
there is sufficient power to drive both the crawler chain and the conveyor 
belt. In the preferred embodiment, each framework member 14 has a length 
of approximately two feet, the length being in the direction of the 
longitudinal extent of the conveyor train and being measured between the 
centers of adjacent U-joint connections. 
In the preferred embodiment, the crawler chain is driven by a series of 
interspersed framework members 14a containing drive means, the spacing of 
which is determined by mine conditions. Generally, the drive framework 
members 14a are spaced about 40 feet apart. 
While there may be 10 or 12 drives in a 400 foot train, only one such drive 
containing framework member 14a will be described here. 
As was discussed above, the crawler chain 20 is made up of a plurality of 
crawler pads 40 attached to the chain 44. In a typical 400 ft. long 
conveyor, the chain would be approximately 800 ft. long. In the preferred 
embodiment, the spacings between the centers of adjacent crawler pads 40 
is approximately 12 inches with each crawler pad being a steel plate 
approximately 5-1/2 inches wide and 1/2 inch thick. The framework member 
14a containing the chain drive is structurally very similar to the 
framework members 14 described above so only the differences will be 
discussed. The main difference is that it contains a drive sprocket and 
the drive means necessary to drive the sprocket. 
As can be seen in FIG. 6, the bottom portion 30 of the framework member 14a 
which contains a drive sprocket includes a motor 150 and a planetary gear 
assembly 152 interconnected by an input shaft 154. The planetary gear box 
152 includes an output shaft 156 which drives a sprocket 158. While in the 
preferred embodiment the gear box 152 is a planetary drive assembly, any 
well-known gear speed-reducing assembly can be utilized to drive the 
sprocket. 
In the preferred embodiment, the motor 150 is an alternating current 
electric motor having a power output of approximately 10 horsepower, 
however, it can be seen that any convenient power source such as hydraulic 
or pneumatic can be utilized. 
As indicated above, the framework members 14a containing a drive unit are, 
in most respects, identical to the framework member 14 described above. It 
should be noted that the force transmission member 78 is removed and 
replaced by two plates 160 and 162. Plates 160 and 162 not only act as a 
force transmission member through the longitudinal axis extent of the 
framework member 14a, but also served to mount both the motor and gear 
reducer 150 and 152 respectively. 
The universal connection points 79 and 81, on the framework members 14a are 
welded directly on end plates 50 and 52 rather than being attached to the 
ends 80, 82 of the force transmission member 78 as is the case in the 
other framework members 14. It should be noted, that in the preferred 
embodiment, the drive elements described above fit within the standard 2 
ft. length utilized in the preferred framework members 14. However, the 
framework member 14a can be lengthened somewhat to accommodate different 
or larger drive elements. 
In the preferred embodiment as seen in FIG. 8, the chain 44 is an 
alternating pitch chain. This means that longer links 166 are 
interconnected with short links 168. Normally, the horizontally oriented 
links are the long links and the vertically oriented links are the short 
links. As can be seen in FIG. 6 and 8, the drive sprocket 158 fits in 
between the long links 166, but pushes against the edges of the vertical 
short links 168. As can be seen in FIG. 6, looking down on the sprocket 
158, each tooth of the sprocket contains a concave indentation 159 which 
matches the convex outer surface of the vertical chain link 168. In the 
preferred embodiment, the sprocket 158 has five upstanding teeth and 
simultaneously drives both the upper and lower runs of chain 44 in a 
tangential manner. By this it it meant that there is no significant wrap 
of the chain around the circumference of the sprocket 158. It should be 
noted that the teeth 170 of sprocket 158 are in constant engagement with 
both the top and bottom run of chain 44 in that before one tooth 
disengages from the chain, the adjacent tooth is beginning its engagement 
with the links 168 of chain 44. In order to insure proper mating of each 
tooth 170 with each link 168 throughout the period of engagement 
therebetween, it is necessary to generate the profile of the tooth 170 
from the incremental movement of the chain 44. 
It should be noted that not every framework member 14 need have support 
structures for the belt 12 and the crawler system chain assembly 20 as 
long as sufficient support is provided by the framework members 14 which 
do have these structures. For simplicity, every framework member of the 
preferred embodiment has such support members. 
It should also be noted that a take up system (as shown in FIG. 2 of U.S. 
Pat. No. 4,339,031) may be utilized at each end 16 and 18 of the conveyor 
system 10 to maintain proper tension in the elongatable belt 12. A similar 
tensioning system can be used to maintain proper tension in the chain 44 
as wear occurs between the links thereof. 
OPERATION 
FIG. 7 discloses a typical application of the conveying system 10 as taught 
herein. In the preferred embodiment, the input end 18 is capable of 
advancing around curvilinear paths within a room-and-pillar type coal 
mine. In the preferred embodiment, the curvilinear paths have radii of 
curvature of approximately 25 feet. This allows the use of 60 degree cross 
cuts which are typical in many mines. It is, of course, advantageous to 
minimize the radius of a curvature of the articulated conveyor system 10 
to permit tighter turns. 
It is envisioned that the conveying system 10 as taught herein will provide 
a mobile conveying system which can simultaneously convey material from 
the input end 18 to the discharge ends 16 while advancing on the crawler 
system as described above, through an elongated path in an underground 
mine. In general, it is envisioned that the input end 18 would be 
steerable in some fashion as by wheels, 19, shown in FIG. 1, to follow the 
output of a continuous mining machine 61, including a loading means 63 for 
gathering mined material off of a mine floor and means 65 for discharging 
material gathered by the loading means for example, or a mobile mineral 
feeder crusher car 67 or even a mineral loading machine 69. 
In order to facilitate loading the end 18 may be equipped with a 
hopper-like framework member 21 which would include the conveyor belt 12 
drive system. As can be seen from the above description, the conveying 
system can continuously convey the material received from any of these 
mining machines while at the same time advancing or retreating. 
For purposes of explanation only, the operation of the conveying system as 
it would occur following a continuous mining machine shall be described. 
A typical continuous mining machine has a discharge conveyor which is 
articulated and can be swung from side to side as it discharges material. 
In the preferred embodiment, the conveying system 10 would utilize a 
hopper 21 on the receiving end 18 of the conveyor. The continuous conveyor 
belt 12 would extend a predetermined distance within the hopper to insure 
gathering and transporting together all the material deposited by the 
continuous mining machine. 
As discussed above, discharge end 16 of the conveyor system 10 overlaps the 
mine panel belt 22. As can be seen, FIGS. 10, 11, 12 and 13 shows various 
methods or arrangements for this discharge and will be described below in 
more detail. 
In a typical mining situation, the conveyor system 10 would, as indicated 
above, extend for approximately 200-500 ft. with, at least initially, the 
majority of the conveying system positioned over the panel belt 22. As the 
continuous mining machine advances into the mine face, the crawler chain 
drive system would propel or advance the conveyor 10 along with the 
advance of the continuous mining machine so that the hopper 21 of input 
end 18 is always positioned to receive the discharge from the rear 
discharge conveyor of the mining machine. The path that the conveyor 
system 10 follows is that path delineated by the steerable input end 18. 
Should the continuous mining machine cut a corner to form a cross-cut, the 
conveyor system 10 would turn in a like manner to follow the continuous 
mining machine. The crawler system inherently maintains the position of 
the entire conveying system along the path delineated by the input end 18 
since only the upper pads of the crawler chain move with respect to the 
ground. The lower strand of crawler pads maintains the shape of the 
elongated path since these pads are substantially fixed as the conveying 
system 10 advances (at least up to the point where the discharge end 16 
and the last framework member 14 would engage the ground). However, during 
normal function of the conveyor train, this point of advance would never 
occur since the panel belt 22 would then have to be extended in order to 
insure the conveying of mined materials discharged from the conveyor 10. 
It can be seen, however, that if one were to tram the conveying system 
through the mine, such as when one would want to move the conveying system 
from one section of the mine to another, then the last framework member 14 
would represent the point where the last crawler pad would be picked up 
off the ground and the first framework member 14 adjacent end 18 would 
always represent the point where the crawler pad 40 is first laid on the 
mine surface. All the intermediate crawler pads in contact with the mine 
floor would remain substantially stationary while the conveyor train 
advances until the trailing end of the conveyor system picks up the pad 
40. Conversely, the conveyor pads 40 of the upper run are in continuous 
motion until they are laid down by the leading end of the conveyor. As can 
be seen, the path or track formed by the crawler chain is as fixed as if 
there were rails laid on the mine floor. The advantages of the mobile 
conveying system taught herein when compared to a mobile conveying system 
utilizing wheels should be obvious. When a conveyor system utilizing 
wheels is used, there is nothing to constrain the conveyor to a fixed path 
as it advances. This is especially so when a wheel conveying system goes 
around a curve. 
While the preferred crawler chain extends substantially throughout the 
longitudinal extent of the conveyor train it would of course be possible 
to utilize two or mroe closed loop or endless crawler chain assemblies 20 
in series to support the endless orbital conveyor belt 12. When two or 
more crawler chains are used over the 300 foot to 500 foot conveyor train 
length each would have the same structural design and exhibit the same 
flexibility and other characteristics as described in the single crawler 
chain assembly 20. 
DISCHARGE 
FIGS. 9-12 disclose various methods of supporting the conveying system 10 
of present invention over the standard panel belt 22 which is fixed with 
respect to the mine passageways in order to discharge material therefrom. 
As can be seen in FIGS. 2a and 2b, the conveying system 10 of the present 
invention is initially located so that a longer portion of the conveying 
system 10 is supported over the panel belt 22. In the preferred 
embodiment, there are guide means 23 such as welded angles, on either side 
of the crawler pads 40 which serve to keep the conveying system 10 aligned 
vertically above the panel belt 22. Note that the panel belt 22 is 
well-known in the mining art and can be of any suitable type conveyor and 
is not described herein in detail. 
In addition, any suitable guide means 23 can be utilized to insure that the 
discharge end 16 of the conveying system 10 is maintained in proper 
alignment over the panel belt 22. 
FIG. 10 discloses a discharge system very similar to that described above 
in FIG. 9 with the exception that the panel belt 22 and the discharge end 
16 of the conveyor system 10 are suspended by chains 25 from the mine 
roof. 
FIGS. 11 and 12 disclose alternate guiding means replacing the angled 
guiding means 23 for insuring that the discharge end 16 of the conveying 
system 10 is maintained directly over the panel belt 22. As can be seen in 
FIG. 11, a pair of channel members 27 form an overhead rail system 
suspended from the mine roof. Each framework member 14 is then equipped 
with a pair of rollers 29 which engage the channel members and maintain 
the path of the discharge end 16 during the portion of travel in which the 
conveyor system 10 is over the panel belt 22. 
FIG. 12 discloses a similar arrangement with the difference being that an 
I-beam 31 is suspended from the mine roof and the rollers 29 attached to 
each framework member 14 are centrally located above the elastomeric 
conveyor belt 12. 
It can be seen that a standard cutter or loading device can be integrally 
attached to the advancing end of the conveyor system 10 to be advanced 
toward the mine face by the operation of crawler chain or track assembly 
20. The conveying system then would become an elongated cutting and/or 
loading and conveying system.