US2353052A - Loading machine - Google Patents

Description

July 4, 1944. N. D. LEvlN LOADING MACHINE original Filed oci. 22, 1937 6 Sheets-Sheet l N i mmm/m VD. 2m mi M 6 Sheets-Shea?I 2 N. D. LEVIN LOADING MACHINE Original Filed Oct. 22, 1937 July 4, 1944.

N. D. LEVIN LOADING MACHINE July 4, 1944.

Original Filed Oct. 22, 1957 6 Sheets-Sheet 3 JAA/ENTOE N n 5 D. LEVI N) Original Filed Oct. 22, 1937 6 Sheets-Sheet 4 /NVENTO/ef NILS D. LEVIN,

july 4, 1944. N D EVlN LOADING MACHINE Original Filed Ocb. 22, 1957 6 Sheets-Sheet 5 /NVENTo/e! NILS D. I rivnmj [BY QL-lb" HTTY July 4, 1944. 2,353,052

N. D. LEVIN LOADING MACHINE Original Filed Oct. 22, 1937 6 Sheets-Sheet 6 ATT 'Y Passed July 4, 1944 UNITEDv STATES PATENT oFFicE LOADING MACHINE Nils D. Levin, Columbus, Ohio, assignor to The Jel'ey Manufacturing Company, a corporation of Ohio Original application October 22, 1937, Serial No.

Divided and this application February 18, 1941, Serial N0. 379,475

6 Claims. (Cl. 198-11) after having been shattered or dislodged from the solid of the mine vein by blasting charges.

A further object of the invention is the provision of an improved hydraulic control system particularly useful in loading machines.

Another object of the invention is .to provide improved means for iiexibly supporting gathering and discharge conveyors of a loading machine.

Still another object of the invention is to provide improved and eillcient means for replacing upon a mine track the front wheels of a wheeled truck of a loading machine.

More particularly it is the object of the present invention to provide improved hydraulic mechanism for adjusting the elevation of `a conveyor swingable on a horizontal axis and resiliently.

supporting such conveyor when in adjusted position.

Other objects of the invention will appear hereinafter, the novel features and combinations being set forth in the appended claims.

In the' accompanying drawings,

Fig. 1 is a plan view of thel loading machine embodying my improvements, with the swinging boom of the discharge conveyor cut short;

Figs. 2 and 3 placed end to end constitute a side elevational view of the loading machine shown in' plan in Fig. 1;

Fig. 4 is a vertical longitudinal sectional view of the rear end portion of the loading machine shown in Figs. 1 and 2;

Fig. 5 is a vertical longitudinal sectional View of the front portion of the loading machine shown in Figs. 1 and 2, with the extreme forward end of the gathering conveyor unit cut short;

Fig. 6 is a sectional view taken along the line 6--6 of Fig. 5 looking in the direction of the arrows;

Fig. 7 is a sectional plan view showing particularly the rear end portion of the truck and the truck propelling means;

Fig. 8 is a continuation of Fig. 7, showing thev forward end of the truck and the drive means for the gathering conveyor;

Fig. 9` is a piping diagram of the hydraulic system for the loading machine; and

Figs. l0, ll and l2 show details of the valve mechanism. 1

This application is a division of my co-pending application, serial No. 170,426, med october 22, 1937, for an improvement in a Loading machine. As illustrated generally in Figs. l, 2 and 3 of the drawings, the mining and loading machine A comprising my invention is primarily a frontal attack machine but provision is made whereby a gathering conveyor cannot become wedged into the material being loaded in that the attack is not coniined to a front attack but also includes a lateral attack at both sides of the forward end of the gathering conveyor.

The said loading machine comprises a track mounted truck 40 upon which is mounted a gathering conveyor 4I and a discharge conveyor 42, the former being adapted to dig into and gather loose or semi-compact coal and to convey it to the latter by which it is discharged into track mounted coal cars, one of which is illustrated at 43. (Figs. 2 and 3.)

Power means is provided to tram the loading machine along the mine tracks at a relatively fast speed, and to operate it along said tracks at a feeding or operating speed while at the same time operating the gathering and discharge conveyors to gather and load coal into coal cars 43.

As best seen by reference to Figs. 2, 4, 5, '7, and 8, the truck 4|! comprises a main frame formed by longitudinally extending side members 44 rigidly attached together at their forward ends by an arcuate front cross-piece formed by spaced members 45, preferably Welded to the side members 44 and rigidly attached at'their rear ends, as by welding, to an arcuate cross-piece 46 (Fig. 7) having removably attached thereto an arcuate bumper plate 41 held in place by nuts and bolts 48.

Adjacent its forward end, the main frame comprises a bed plate 49 (Fig. 5) rigidly attached to the tops of the side members 44 and front crosspieces 45, as by welding. TheV gathering conveyor 4| and the drive means therefor are supported from this bed plate 49, as will'be hereinafter explained in complete detail.

Adjacent its rear end the main frame is provided with a bed plate 50 (Figs. 4 and 7) which is rigidly attached to the bottoms of the side members 44 and the rear cross-piece 46. The bed plate 50 supports the single drive motor '224 which drives all of the apparatus on the loading machine, as hereinafter described in full detail, and supports most of the gear mechanism for controlling said loading machine.

As best seen in Figs. 4 and 5 of the drawings, the truckV 40 is mounted upon a pair of forward track 'engaging anged wheels 5I, 5| keyed on 2 2,ass,os2

axle 52 which is journaled in adjustable bearing boxes 53, 53 slidably supported upon guideways 54, 54. Gearing mechanism 55 is provided for adjusting the bearing boxes 53, 53 in unison longitrack engaging flanged wheels 55, 56 mountedV upon axle 51 journaled in bearing boxes 58, 58 (see Fig. 7) slidable longitudinally in guideways. Gearing mechanism 5| readily accessible from the side of the truck 48, as best seen in Fig. '7, is provided for adjusting the bearing boxes 58, 58 longitudinally in unison along guideways.

As clearly seen in Fig. '7 of the drawings, the gearing mechanism 6| includes a square headed shaft adapted to receive a crank, which square head may be locked in position by a latch slidable vertically in a guide and having a square notch at its lower end fitting over a squared portion of the shaft 5I. Similar latch mechanism may be associated with the operating shaft of the gearing mechanism 55.

The axles 52 and 51 are provided with sprockets which are connected together by a continuous chain 65 to insure their movement in unison. Axle 51 also carries a drive sprocket 59 by which it is driven, as hereinafter described in full detail. It is thus evident that driving power will be applied to all of the track engaging wheels 5|, 5| and 56, 56.

It is to be particularly noted, that the bearing boxes 58, 58 (Fig. 7) associated with axle 51 are positioned outside the wheels 56. As was previously mentioned, the bearing boxes 53, 53 associated with axle 52 are inside the wheels 5|, 5|. As a consequence, there is a modified three point suspension provided for the truck 48 which I have found allows all of the wheels 5I, 5| and 55, 58 to remain on the mine rails 88 though the latter may be very uneven. 'I'his tends to prevent derailment of the machine.

It will be evident that the gearing mechanisms 55 and 6| may be employed to shift the axles 52 and 51 (Figs. '1 and 8) forwardly or rearwardly either to tension the chain 65 or to tension the drive chain associated with the sprocket 59.

The construction of the gathering conveyor 4| is best seen by reference to Figs. l, 2, 4, 5, 7 and 8 of the drawings and comprises a turntable 88 formed by a bottom plate 69 provided at its rear end with a circular opening adapted to receive a journal bearing 18 (see Figs. 4 and 5) which is reinforced by a plate 1| and a. ring 12, all rigidly attached together, as by welding. The journal bearing 18 is journaled to a casing 13 which is removably attached to the front bed plate 49 by virtue of screws 14 which thread into a ring 15 welded to the bottom of said front bed plate 49. as clearly seen in Figs. 4 and 5 of the drawings. It is thus evident that the turntable 68 is journaled to the truck 48 about an upright axis provided by the casting 13 thereby providing for lateral swinging movement of the gathering conveyor 4|. l

It will be evident that the thrusts received by the gathering conveyor 4| will be translated to the truck 48 through the casting 13 and thus this casting and the journal bearing 18 associated therewith is made of very rugged construction.

As clearly illustrated in Figs. 4 and 5 of the drawings, the bottom plate 59 is removably attached to the casting 13 by a threaded ring 15 threaded to the top of said casting 13 and held locked by a set screw 11.

The turntable 68 also includes upright side plates 18 and intermediate front plates 19 which cooperate to support a top plate 88, which plates co-operate to provide a gearing' housing and support, as hereinafter explained in full detail.

As best seen in Figs. 1 and 2 of the drawings. side plates 18 of the turntable 58 carry side brackets 8l, 8| provided with pivot pins 82 upon which is pivoted the gathering boom 83 of the gathering conveyor 4| by means of brackets 84, 84 (Fig. 1) having apertures to receive the pins 82, which brackets 84, 84 are welded rigid with side members 85, 85 of said gathering boom 83. It will be evident that'the boom 83 is swingable with respect to the turntable 58 about a horizontal axis provided by the pivot pinsv 82. The gathering boom 83 comprises a bottom plate 88 welded to a cross I-beam |8I (Fig. 5) which said bottom plate 88 is welded rigid with the side members 85, 85 and, at its rear end, is substantially parallel with and forms an extension of the top plate 88 of turntable 58.

As clearly illustrated ln Fig. 2 of the drawings, the bottom plate 88 is provided with a flat working portion 81 adjacent its forward end which lies in a plane forming an angle with the plane of the major portion of said bottom plate 88, said two plates being connected by a smooth curve. In other words, the bottom plate 85 is smoothly curved to form a working portion 81 at its forward end which is substantially horizontal thereof when at the mine floor, slightly sloping upwardly and rearwardly when the boom 83 is in its lowered position with the working portion 81 sliding over the floor of the mine. 'I'his construction is particularly desirable to the end that the bottom plate 85 may work under all of the coal during the attack on the shot-down or senilcompact mass of coal.

As best illustrated in Fig. 1 oi the drawings, the bottom plate 85 carries a pair of gathering chain guides 88 and 89 each formed by an outer grooved track member 88 grooved at its outer surface to receive the side bars and retaining gibs of the gathering conveyor chains designated generally 9|, 9|. That is, the track members 98 are provided with grooves and retaining flanges to keep the gathering conveyor chains 9|, 9| in proper position. Cover plates 92, 92 extend between the opposite sides of each track member 98 to prevent any material accumulating therebetween. Reinforcing bars are provided inside each of the track members 98 and all of said members comprising bottom plate 88, track members 98, 98, cover plates 92 and reinforcing bars are rigidly attached together by appropriate rivets.

As clearly illustrated in Fig. 1 of the drawings, the track members 98 extend substantially the full length of the gathering conveyor 4| and thus the gathering conveyor chains operate substantially through the entire length of said gathering conveyor. As a consequence, there is only one re-handling of the gathered material from the time it is first gathered by the gathering conveyor to the time it is discharge into the mine cars and this is during the time it is discharged from the gathering conveyor to the discharge conveyor.

It is furthermore to be noted by particular reference to Fig. 1, that the inner portions of the track members` 98 are substantially parallel through the entire length. As a consequence,

assaone 3 there is no progressive squeezing action on the coal being loaded which can produce undesirable stresses and strains.

As was previously pointed out, the width of the bottom plate 86 is substantially constant throughout its entire length but at the front end attacking portion thereof it is curved rearwardly as seen at 94 (Fig. 1) to provide for a maximum amount of contact of the flights of the gathering conveyor chains duringloperation.

It is also to be particularly noted that during the rearward portion of the travel of the con-v veyor chains 9| in their progress toward Athe front end of the gathering conveyor, the flights are spaced inwardly of the sides of the bottom plate 86 and are within the connes of the side members 85 which are provided with appropriate cover plates 95, 95 (see Fig. 1) attached to inner side wall cover plates 95', 95' (see Figs. l and 5). However, adjacent the forward end of the gathering conveyor 4| the cover plates 95 and 95' and the side members 05 are removed and the track members 90 diverge progressively as the front end is approached. As a consequence, the

flights of the gathering conveyor chains 9| pro-v gressively move laterally beyond the edges of the bottom plate 86 adjacent the fiat Working portion 81 thereof. These flights also, in moving around the front lcurved ends of the guide members 90, extend beyond the front extremity of the curved portion 94 of the bottom plate 86 to dig into, break down and gather the coal either in shot-down condition or in a semi-compact mass. This operation is described in more complete detail hereinafter.

As clearly illustrated in Fig. 1 of the drawings, I also preferably provide a pair of electric lights 86, 96 on the gathering conveyor 4| to illuminate the material being worked.

Since the gathering boom 83 of the gathering conveyor 4I is pivoted about a horizontal axis 82 with respect to the turntable 68 of said gathering conveyor 4|, it is, of course, evident that the track members 90 must be broken at this pivot point. As illustrated in Fig. 5 of the drawings, an extension for the track members 90 is provided at 91 to guide the conveyor cha-in 9| in its movement over the turntable 68. The extensions 91, of which there will be one for each of the two gathering conveyor chains, provide guide paths on each side thereof leading both to and from drive sprockets 98 for which there will be one for each of the chains 9 I, 9|. The extensions 91 will, of course, terminate the guide track for the chains 9|, 9| adjacent the drive sprockets 98,98.

Each of said extensions 91, 91 is provided with a rounded nose 99 (Fig. 5) adapted to extend into a pocket in the frame of the boom 83 and slightly spaced therefrom. This, of course, permits limited movement of the boom 83 about the horizontal axis provided by the pins 82, 82. It is also to be noted that protecting cover plates |00 are provided adjacent and above the top plate 80 of the turntable 68, which cover plates |00 overlap the cover plates 95. (Fig. 5.)

To provide for the vertical swinging movement of the boom 83 about the axis of pivot pins 82 I provide a double acting type of hydraulic piston motor mechanism best seen in Figs. 5, 6 and 8 of the drawings and designated generally by the reference number |02. Said piston motor mechanism |02 comprises a bottom head casing |03 provided with trunnions |04 by which it is pivotally mounted upon a bracket formed by spaced plates |06, |05 rigidly but removably-attached to frame members |06, |06 of the turntable 68 by nuts and bolts |01, |01.

Clamped rigidly between the head casting |03 and a piston rod receiving cylindrical head |08 by a plurality of elongated clamp bolts |09,

cylinder head |08 provided with an appropriate 4 packing gland or vstufling box ||9. It will be evident that fluid under pressure may be admitted either above or below the piston to move it either upwardly or downwardly.

As hereinafter described in complete detail, the piston may also be sealed and locked in any adjusted position. The upper end of the piston rod ||5 is provided with an u'pset head |20 received flxedly but loosely in a channeled cross member |2I provided at its opposite ends with downwardly extending L-shaped hanger plates |22, |22 forming a yoke. The connection between the head |20 and thecross member |2| permits relative movement between them while insuring their attachment together.

The hanger plates |22, |22 have their horizontal portions provided with apertures through which extend rods |29, |23 pivotally attached at their tops by pins |25, |25 to a transversely extending bar |24 welded rigidly with the bottom plate 86 of the boom 83. Between the horizontal portions of said hanger plates |22, |22 and said bar |24 and surrounding the rods |23, |23, I provide compression coil springs |26, |26. The bottom ends of the rods |23, |23 are threaded and receive'adjusting and lock nuts |21, |21.

It will be evident, particularly by reference to Fig. 6 of the drawings, that the boom 83 is supported upon the coil springs |26, |26. When the loading machine, with the gathering convieyor 4| elevated, travels along the track about the same weight is carried on each of the axles 52 and 51. When at the face, the Afront end of the gathering conveyor 4| is lowered until it rests on the mine floor. This takes a gneat amount of weight off the front axle and, except for springs |26, |26, would throw the machine out of balance to such an extent that the front wheels 5|, 5| might raise. off the track and derail the machine. Also, sometimes the front end of the gathering conveyor 4| climbs up a roll in the mine bottom. The springs |26, |26 insure suiiicient load on front wheels 5|, 5| to keep them on the track rails vunder all normal conditions and prevent derailment.

By reference particularly to Figs. 5 and 8 of the drawings, it will be seen that adjacent the front end of the truck 40 and extending upwardly through the front bed plate 49 thereof, is a plurality of rollers |28 mounted upon stub shafts |29 carried by the spaced plates of the front cross-piece 45. These rollers |28 bear against an arcuate bearing plate |30 carried on the bottom plate 69 of the turntable 68 and thus provide an anti-friction support for the front end of the turntable 68 of said truck 40. In other words, the turntable 68 will be support- 49 and is rigidly attached to the bottom plate 69 of the turntable 58 by screws |32 threaded in an arcuate spacer |33.

To provide for the swinging of the gathering conveyor il about the vertical axis of casting 13 I provide a very simple and compact arrangement in the form of a hydraulic piston motor |84, best seen in Figs. 7 and 8 of the drawings, comprising a cylinder |35, pivotally attached at its rear end to a bracket |36 formed rigid with the main frame of the truck 40. and a piston carrying a rod |31 pivotally attached to a bracket |38 formed rigid with the turntable 68 of the gathering conveyor 4|. The piston motor l|34 is of the double acting type. That is, it maybe moved under power in reverse directions and with the system comprising my invention, may bs locked in any adjusted position, as hereinafter described. It is to be noted that this hydraulic piston motor is entirely within the confines of the loading machine truck 40 and thus does not increase the width of said machine. It is furthermore to be noted that it is highly protected and therefore cannot ,be easily damaged.

Attention is now directed particularly to Figs. l, 2 and 5, inclusive, and to the construction of the gathering conveyor chains 9| and the gathering flights which they carry. Each of said gathering chains 9| comprises a plurality of main links formed by spaced retaining gib carrying side bars interconnected with a plurality of connecting links formed in two parts which are pivotally connected about horizontal axes.- The main links and connecting links are pivotally attached together by pins. The' pins make a snug fit with the connecting parts whereby the chain will be relatively rigid except for movement about rectangularly disposed horizontal and upright axes provided by said pins. That is, each chain 9| will be free to pivot about a horizontal axis so the chain can travel over the irregular surface of the bottom plate 86, and also free to pivot about a vertical axis so the chain can travel around the continuous generally orbital path provided by the track members 90. For any other movement the chain will be relatively rigid which is particularly desired in carrying out the rather heavy work required of the gathering chains 9|. s

I pivotally attach to every sixth main Iink a gathering flight |43 interspersed with alternate gathering flights |44. The essential dierence between the gathering 'ilights |43 and |44 lies in the fact that the former carry removable bits or picks |45 which are particularly effective to dig into and break down a semi-compact mass of material while the gathering nights |44 are devoid of such bits or picks.

Attention is now directed particularly to the construction of the discharge conveyor 42 as illustrated in Figs. 1, 2, 3, and 4. Said discharge conveyor 42 comprises three articulated parts including a stationary hopper |55 supported upon the front bed plate 49 of the truck 40 by spaced side brackets. The hopper |55 comprises spaced side members |58 and a downwardly inclined rear chute |59 (Fig. 5) formed integral with said side plates |56. The chutev|58 is adapted to receive coal as it discharges from the rear end of the gathering conveyor 4| over the top plate 80. A guiding arcuate apron |66 is carried by the top plate in overlapping relation with the chute |59 to insure the proper reception oi' coal by said hopper |55 without any loss thereof. The chute |59 is of generally conical form thus permitting free rotation of the apron |65 with respect thereto.

It may also be pointed out that the side plates 18 of the turntable VSil have rearwardly extending deflector wings |6I, |6|' which extend over and partially into the arcuate chute |59 of the hopper |55 thus guiding the material discharged by the gathering conveyor 4| into the hopper |55. (Fis. 1.) The hopper |55 is provided with a chain guiding bottom plate |62 (see Figs. 4 and 5) fwhich is primarily adapted to guide the return flight of the conveyor chain associated with the discharge conveyor 42. A feed plate |62 is provided adjacent the forward endoi' the chute |59 inthe hopper |55 and feedsthe material onto a material supporting false bottom plate |64 of the hopper |55 over which bottom plate |64 the upper run of the flight carrying conveyor chain |65 of the discharge conveyor 42 travels to convey the coal rearwardly and discharge it into the cars 43.

Pivotally attached to the hopper |55 by means of spaced side brackets |66, |66 (Fig. 4) carried by side members |61, |61 and journaled on pins |68, |68 is a discharge boom |69. It is evident that the boom |69 is pivoted about a horizontal axis formed by pins |68 for vertical swinging movement with respect to the hopper |55 and the truck 40. The discharge boom v|69 is formed in two parts comprising the forward part |10 and the rearward part |1| which are pivotally attached about a vertical axis, the reaward part |1| being swingable horizontally about said vertical axis. The forward part |10 of the boom |69 comprises a bottom plate |12 (Fig.4) which acts somewhat as a continuation of the bottom plate |62 ofthe hopper |55 (Figs. 4, 5).

Positioned above the bottom plate |12 is a material supporting false bottom plate |13 which forms a continuation'of the material supporting false bottom plate |64 of the hopper |55. Extending successively along the false bottom plates |64 and |13 are a pair of spaced guiding and retaining angle members |14 and |15, respectively. As clearly illustrated in Figs. 1 and 4 of the drawings, these angle members |14 and |15 cooperate with retaining gibs on the conveyor chain |65 to retain it in place while permitting longitudinal movement thereof, at the same time guiding it properly along the center of the troughway formed by the false bottom and side plates of the discharge conveyor 42.

Extending downwardly from the false bottom plate |13 and in alignment with the angle members |14, |14, I provide angle .members |16 which form a guide and support for the return night of the chain |65 during its travel along the for- |19 above which is positioned a material sup-i porting false bottom plate |80 which is a continuation of the false bottom plate |13 and over which the conveyor chain |65 travels and conveys the material. The forward end of the rearward part |1| has attached to the false bottom plate |80 contacting plate means I8| which is pivotally attached by a pivot |82 to the rear end of the false bottom plate |13.

As clearly illustrated in Fig. 1 of the drawings,

having an upstanding guide rod 204 which extends into the coil spring 202 and into ,the guide cylinder 20 I, the coupling member 203 being pivotally attached to a bracket 205 formed integral with the rear bed plate 50 and the bumper plate 41 of the truck 40.

It is evident that the coil springs 202 will provide a flexible support for the discharge boom the rear end of the false bottom plate |13 and of the bottom plate |12 are formed on the arc of a circle, the centerof which is along the axis of the pivot |82. Likewise, the forward end of the bottom plate |18 and the false bottom plate |60 are formed on the arc of slightly larger circles than those of plates |12 and |13, respectively, whereby a continuous surface is provided in each case for any swinging position of the rearward part |1| of the discharge boom |69.

It is also to be noted by reference to Fig. 4 of the drawings, that angle members |83 are provided on the bottom of the plate member |8| to form a guide for the return strand of the chain |65 leading up to the pivot point provided by pivot |82.

Adjacent the break between the bottom plates |12 and |19 I provide a lower wear plate |84 on plate |19 and laterally spaced guide plates |85 on member |8I. These plates |84 and |85 serve to guide and direct the return strand of the chain |65 so that their gibs enter the guideways of the angle members |83.

Adjacent the rearward arcuate end of the bottom plate |12 I provide an arcuate bearing v plate |86 upon which rolls a pair of rollers 38|- (see Fig. 2) carried at opposite sides of the front end of the rearward part |1| of discharge boom |69 by brackets 382, which, with the pivot |82, support the rear part I1| of the discharge boom |69. Adjacent its rearmost end the rearward part |1| will be provided with a centrally positioned discharge sprocket mounted upon an adjustable shaft |81 (see Fig, 3) upon which sprocket the conveyor chain |65 :will ride. At the forward end of the discharge conveyor 42 (see Fig, 5) I provide Within the hopper a centrally disposed guide sprocket |88 for said chain |65.

To eect the driving. of thedischarge conveyor |65 I provide a drive sprocket 291 (Fig. 7) with an endless sprocket chain (not shown) and condrawings, the means for swinging the discharge boom |69 about the horizontal axis provided by the pins |88, comprises a single .acting hydraulic piston motor mechanism |94 comprising a bracket |95 rigidly attached to the bottom of the bottom plate |12 to which is pivotally attached a cylinder |96 having a head |91 provided with an appropriate inlet port |98 within which cylinder extends a cylindrical piston I 98 provided at its top with a clamped leather or compound sealing ring 200 which makes a leak-proof sliding t, within which cylindrical piston |99 is a guide cylinder 20| within which extends a coil spring 202 mounted upon a pivoted coupling member 203 |69 for any position of adjustment thereof, thus relieving any strain caused by a large lump of coal on the boom striking the top of the mine roof or for any other similar cause. `Th'e guire rod 204 provides a guide and retainingmeans for the coil spring 202.

It will be evident that by admitting fluid under pressure to the port |98 or discharging it by said port, the piston |99 may be adjusted in the cylinder |96 to expand or contract the hydraulic piston motor mechanism |94 thus swinging the discharge boom |69 about the horizontal axis provided by the pins |68. By locking the fluid in the cylinder |86, as hereinafter described, the boom |69 may be locked in any elevated position.

Attention is now directed particularly to the construction of the means for swinging the rearward part |1| of the discharge boom |69 with respect to the forward part |10 thereof. It may be mentioned that to provide continuous side walls for the discharge conveyor 42 for any position of adjustment of the rearward part |1| with respect to the forward part |10, each of the side plates |18 carries a pivoted arcuate extension side plate 206, (Figs. 1, 2) the free end of which is urged into contacting relation with the side plate |61 by a coil spring 201 coiled about an extensible rod 208 pivoted at one end to a bracket rigid with the plate 206 and extending through a bracket formed rigid with the side plate |18. As the rearward part |1| of the boom |69 swings about the axis of pin |82 (Fig. 4), the free end of the plate 206 Iwill move forwardly and rearwardly in contacting. relation with the side member |61 thus forming continuous sides for the discharge boom 42.

To cause swinging movement of the rearward part |1| of the boom |69, with respect to the forward part |10 thereof about the axis of pin |82, I provide a bracket 2I| formed rigid with the bottom plate |12. Pivotally attached to bracket 2| is a rod 2|2 the rear end of which is pivoted to a sliding head 2I3 of a hydraulic piston motor 222. Said hydraulic piston motor 222 comprises a'cylinder 2 |4 rigidly attached to a side plate |10 of rearward part |1| of discharge boom |69 within which is a piston attached to a piston rod 2 I4'.

It is evident that upon operation of the hydraulic piston motor 222 the rearward part |1.| of discharge boom |69 will swing about the axis of pin |82 (Figs. l, 2). I'he motor 222 may be locked in any desired position of adjustment to lock the rearward part |1.| of discharge boom |69 in position. In actual pratice this angle of swing is made approximately eighty degrees. It may also be mentioned that the angle of swing of the gathering conveyor 4| is also approximately eighty degrees.

This ability to swing the discharge boom by iluid pressure motor operated mechanism provides for the loading of cars on tracks adjacent the track which supports the loading machine and, in addition, provides for the loading of cars while the loading machine is on a curved track. It is also useful in traveling around curves while tramming the loading machine to an operating position.

Attention is now directed particularly to Figs. 4. 5, '1 and 8 and to the drive means for the various devices to be driven. At the outset it may be stated that only a single or common electric motor 224 is relied upon as the primary source of power to effect a driving of all of the devices of the loading machine. Said electric motor 224 is mounted upon the rear bed plate 58 of the truck 40 and compactly positioned below the discharge conveyor 42 which extends upwardly and rearwardly from the hopper |55. Due to this positioning of the electric motor 224 it is possible to provide a very large and powerful motor which is capable of effecting -any and all of the drives required at. any time while maintaining a machine of low height to permit its use in a relatively low head coal mine. Said electric motor 224 is provided with a forwardly extending armature shaft 225 (see Fig. 4) carrying a drive pinion 226 meshing with a bevel ring gear 221 which is rigidly attached to the housing 228 of a friction clutch mechanism 229 (see Fig. 4) The housing 228 is keyed to a vertical shaft 238 which is mounted at its top in a bracket 23| rigidly attached to the main frame of the truck 40, there being an anti-friction ball bearing 232 interposed between the bracket 23| and the shaft 238 which is held in place by a removable cap 233. The bottom of the shaft 238 is supported in a bracket formed rigid with the bottom plate 5|), said support being through an anti-friction ball bearing 235. Keyed to the lower end of the shaft 239 and above the bearing 235, is a bevel gear 238. It may thus be noted that the gear 221 and the gear 236 being both keyed to the shaft 239, will be driven together at all times from the motor 224.

Journaled loosely on the central portion of the shaft 230 is a clutch member 231 (Fig. 4). Splined on the interior of the housing 228 and on the exterior of the clutch member 231, which members 228 and 231 comprise cooperating clutch members, is a plurality of overlapping stacked friction plates, alternate ones of which are connected to the housing 228 and the clutch member 231, respectively. Adjacent its bottom the clutch member 231 is provided with an integral extended flange to which is pinned a gear 249. The flange, in addition to supporting the gear 249, also acts as one compression member for the friction clutch plates 238.

To effect a compression of the clutch plates 238 and thus to effect an engagement of the clutch elements 228 and 231, I provide a compression ring within the housing 228 having a flange which bears against said plates 238. Downward movement of the ring to effect the aforementioned compressing action is effected by a plurality of pins 242 which extend through apertures in the housing 228 and are carried by a ring operable through an anti-friction ball bearing operable by a trunnion collar which is controlled by a shipper 246 keyed on a shaft 241 (Fig. 4) which shaft 241 is Journaled at one end in an upwardly extending plate 248 (Fig. 7) rigidly attached to a false bottom plate which, in turn, is rigidly attached to the main frame of the truck 49, as clearly illustrated in Fig. 4 of the drawings.

Adjacent its other end the shaft 241 is supported in a pair of downwardly extending apertured plates 259, 258 (see Fig. 7) which are bolted to the bracket 23|.

It will be evident that rocking movement of the shaft 241 to urge the collar downward will Ves cause an application of the friction clutch 229 to lThe gear 249 meshes with idler gear 25| mounted upon an anti-friction supported shaft 252 journaled in a cup A253 rigidly and removably attached to front bed plate 49, which gear 26| in turn meshes with a large gear 254 carried by a shaft 256 on anti-friction bearings in the previously described casting 13. (Fig. 4.)

It is to .be particularly noted that since the vertical axis about which the gathering conveyor 4| swings is along the axis of the shaft 255, power can be transmitted to said gathering conveyor through the gear 254l while the gathering conveyor is in any desired position of adjustment. The large gear 254 meshes with one of a pair of interxneshing large gears 258, 256 (Figs. 5 and 8) which are journaled in the bottom plate 69 and top plate 88 of the turntable 68 and which drive the previously mentioned sprockets 98, 88 through shafts 251, 251. It is thus seen that the two drive sprockets 98 are driven in reverse directions and at the same speeds, thereby to drive the gathering chains 9|, 9| at the same speeds and in reverse directions, with the flights on one chain in xed relation to the flights on the other chain.

Attention is now directed particularly to Figs. 4 and 7 and to the gear train which is operative to drive the truck 48 either forwardly or reversely and at either a fast tramming or transportation speed or at a low feeding or sumping speed. This gear train includes the previously described gear 236 which, as above pointed out. is driven directly from the motor 224. Gear 238 meshes on opposite sides with bevel gears of reversing friction clutches.

The reverse ends of the shaft 282 are mounted in appropriate journal bearings 218 and 21| both formed rigid with the false bottom plate 248 (Figs. 4 and 7) Keyed to the shaft 262 is a drive pinion 212 which, as best seen in Fig. 7, drives a variable speed reduction mechanism comprising a gear 213 constantly in mesh therewith, which is keyed to a pinion 214 both of which are journaled loosely upon a countershaft 215. Pinion 214 meshes with a larger gear 218 keyed to a pinion 219 and mounted upon a shaft 288 (Fig. '1) journaled in bearings 28|, 28|. Pinion 219 meshes with a gear 282 which is also loosely journaled on countershaft 215.

The gears 213 and 282 are provided with clutch jaws 283 and 284 respectively, which cooperate with clutching elements 285 and 288, respectively. having appropriate cooperating jaws. A shipper 281 is provided for the clutching elements 285 and 286, which shipper ls adjustably mounted on a shiftable shaft 288 slidable at one end in a journal 289 carried by side plate 44 and at the other end pivoted to an operating lever.

In the position illustrated in Fig. 7 of the drawings, both of the clutching elements 285 and 286 are in clutch disengaging position and thus no drive whatever will be effected to the countershaft 215. If the shaft 288 is moved in one direction, clutching element 285 will be moved to engaged position which will effect a high speed connection between the drive shaft 262 and the countershaft 215. When the clutching el'ment 266 is moved into engaged position by moving the shaft 286 in the other direction, a low 'speed connection will be effected between the drive Ashaft 262 and the countershaft 215.

Keyed to the countershaft 215 is a drive sprocket 293 which drives the sprocket 59 (see drum 336 and the countershaft 215, the former is provided with jaws adapted to cooperate with the jaws of a sliding clutch member 331-which is feathered to the end of the shaft 215 and Fig. 7) 'through a drive chain 293. As was previously pointed out, the drive sprocket 59 drives the axle 51 and the wheels 56, 56 of the truck 40, which axle 51 in turn drives the axle 52 through the chain 55 to drive the wheels 5|, 5| of the truck 40 (Fig. 8). It is thus manifest that the loading machine may be driven through the traction wheels 5| and 56, 56 from the motor 224 either forwardly or reversely. at either a high As clearly disclosed in Figs. 1, 2 and 7 of they drawings, I provide a power driven electrical cable drum 325 which is pivotally mounted upon the rear bed plate 50 by a shaft journaled in a bearing 326 (see Fig. 7) mounted. on an arm pivoted to a bracket 321 carried on the top of an oil reservoir 328 of the hydraulic control system which is described in full detail hereinafter. The drum 325 carries a flexible electrical cable 329 which supplies electrical power to the electric motor 224.

Rigidly attached to the cable drum 325 is a drive sheave 330 'driven by a chain 33| from a sheave 332. The ratio of the sheaves 338 and 332 is so selected that the speed of rotation of the drum 325 will be sufficient to pick up the cable 329 to prevent an accumulation of slak thereon even when substantially .all of the cable 329 has been paid out and thus the effective diameter of the drum 325 is at a minimum. It will,of course, be evident that the drum 325 will have to rotate at different speeds relative to the speed of travel of the loading machine during the hauling in of the cable 329 due to the effective diameter of said drum 325. To provide for this, it is to be noted that the sheaves 330 and 332 have smooth surfaces and that the chain 33| can slip with respect thereto. Thus, if the drum 325 tends to rotate at a speed too fast for that required to take up the slack in the cable 329, there will be slippage between the chain 33| and one or both of the sheaves 330 and 332.

Furthermore, the sheave 332 is a one-way power driven sheave so that when the mining machine is operating to pay out the cable 329 the tension on said cable 329 is relied upon to rotate it, the cable being hauled in, of course, under power. To provide this one-way drive, the sheave 332 is journaled loosely on a cup sleeve provided with ratchet teeth. The sheave 332 carries a spring pressed pawl which is ei'ective in any position thereof to provide a one-way drive between the cup sleeve and said sheave 332. It is to be noted that the cup sleeve is keyed to the countershaft 215. Also loosely mounted on a portion of the cup sleeve is a haulage or towing' cable drum 336 (Fig. '1) with which there is associated a flexible steel cable, not shown, to aid the sumping of the loading machine, when necessary, or to aid it in climbing a hill. In general, it is not necessary to use this flexible steel cable but sometimes severe conditions are encountered wherein it is desired.

To eect a driving connection between the operated by a'shipper 338 carried on a longitudinally movable shaft '339 having an operating handle. It will' be evident that such handle may be operated to effect a driving or nondriving relation between the countershaft 215 and the drum 336.

-As clearly illustrated in Fig. 7 of the drawings, a guide pulley 342 is carried on a bracket 343 supported by a plate 58 directly to the rear of the d rum 336 to act as a guide for the abovementioned steel cable. As clearly illustrated in Fig. '1 of .the drawings, a pair of guide pulleys 344 and 345 is provided adjacent the rear end 0f the frame-40 to guide said mentioned flexible steel cable from the rear of the main frame of the truck y4|'| to extend either rearwardly or forwardly. When the steel cable extends rearwardly it will pass directly from the pulley 342 to the pulley 344 and when it is directed to the front end of the loader it will, in addition, be reeved about the pulley 345 extending forwardly along the side of the truck 40.

It is also to be noted by reference to Fig. '1 of the drawings, that the rear cross-piece 46 of the main framegof. the truck 40 carries a guide member 35| having top, bottom and side antifriction roliersj" As was vpr'iously pointed out, the electrical cable'drum ,825 was mounted upon the pivoted bearing 326 which bearing was attached to an arm pivoted to bracket 321. This provides for shifting of the drum 325 forwardly or rearwardly to tension or loosen the -drive chain 33|. To

effect the shifting of said drum-325 to tension or loosen said chain 33|, I provide an operating handle 352 pivoted to a bracket 353 mounted on the .oil reservoir 328, which handle 352 is provided with an eccentric crank pin 354 to which is attached a rod 355 extending through an aperture in the bearing 326 and provided with a compression spring 356. When the handle 352 is in its lowered position it will pass over dead center and the spring 356 will urge the bearing 326 to the left, as 'viewed in Fig. '1, to tension the chain 33|.4 When the handle 352 is lifted the bearing 326.will be moved to the right to release the tension on the chain 33| thereby to permit free rotation of the drum 325.` The former trated in Fig. '7, and drives a hydraulic pump 351, preferably an oil pump, through a chain and sprocket drive mechanism 358. The pump 3511s preferably a relatively high pressure pump capable of producing pressure up to one thousand pounds yper square inch and is vmounted upon the oil reservoir 328.- It will thus be seen that the pump l351 is continuously driven whenever the motor 224 is operated.

It may also be mentioned that the pump 351 is of such a construction that regardless of its direction of rotation it will always supply pressure at the same port. This is useful to maintain full control of the machine in case the motor 224 is driven in reverse for any reason. y

By means of a system of piping and connections including the suction pipe 358 andthe supply pipe 366 (Fig. '7), the various double acting hydraulic motors 222, |34 and |62 and the single acting hydraulic motor |94 (Fig. 4), may be operated under the control of the valves connected to the actuating levers 31|, 314, 316 and 318 at the operator's station (Fig. 2). Under normal conditions the pump 351 will be operating at rio-load but upon operation of any of the control valves in either direction the no-load bypass will be closed automatically and pressure will be available at any selected hydraulic motor. When any hydraulic motor reaches the limit of its stroke the pressure will be relieved by the by-pass and when the respective valves are each closed its particular hydraulic motor will be locked in adjusted position.

As was previously pointed out, the conveyor chain |65 for the discharge conveyor 42 is not only controllable from a main central control station, Where all of the controls are located, but is also controllable by a trip rider by handle 324 (Fig. 2) located adjacent the rear of the truck frame 44. It is also desirable to provide the trip rider with controls for the hydraulic piston motor |94 and the hydraulic mtor 222 whereby said trip rider may control the swinging of the discharge boom |68 and the elevation thereof. The trip rider will thus have full control over the discharge conveyor 42. To this end I provide operating handles 423' and 424 (see Fig. 2) adjacent the rear end of the truck 46 and near the handle 324, which are connected to levers- 425 and 426, respectively. Thus the control valves 315 and 318 which control the hydraulic motors 222 and |94, respectively, associated with the discharge conveyor to swing it laterally or vertically, are controllable both at the central station and at the station adjacent the rear of the truck 40.

Reversal of the truck propelling mechanism in order to advance and retract the gathering conveyor in the loading operations, is controlled by the lever 44| which when moved in one direction will effect the application of the clutch259 and when moved in the opposite direction will effect the application of the clutch 266 (Fig. '1). Movement of the lever 44| in either direction actuates the intermeshing bevel gears 442, 443 to move the rods 43| and 269 axially to slide the latter axially of the shaft 262 and thus operate either the clutch 259 or the clutch 266 to effect transmission of power from the motor 224 to the shaft 262 and from the latter-to the shaft 215. speed reducing gearing driven by the pinion 212 (Fig. '1) eects rotation of the shaft 215 at two different speeds and therefore the machine may be advanced at a slow feeding or sumping speed or at a fast or transportation speed. In a similar manner the machine maybe moved rearwardly at slow or fast speeds underthe control of the clutches 285, 286 shown in Fig. 1. It should be understood that the shafts 262 and 215 always rotate in opposite directions whether the truck is driven at slow speed or fast speed and that reversal of the truck propelling mechanism depends upon the alternate applications of the clutches 259, 266.

The electric motor 224 should be constantly Thel extending bores 381.

vides a circumferential oil chamber 388 providdriven in the same direction so as not to reverse the directions of travel of the conveyor chains on the gathering and discharge units. However, without reversing the motor 224, the clutches 266, 266 may effect reversal of the truck propelling mechanism;

Attention is now directed particularly to Fig. 9

of the drawings, which illustrates diagrammatically the hydraulic system for controlling the several iiuid pressure motors. The in-put to the pump 351 is fed from the reservoir 328 by a suction pipe 359. A by-pass pipe 36|, including a high pressure relief valve 362, connects the pressure pipe 366 to the reservoir 328. The pressure pipe 366 leads to a no-load by-pass valve 363, hereinafter described in full detail, which, in turn, directs the oil underpressure to a common pressure chamber 364 (see Fig. 11) of a control valve manifold 365. The by-pass valve 363 when in by-pass opening position, directs fluid from the pipe 366 to a by-pass return pipe 366 leading to the oil reservoir 328. The manifold 365 is also provided with a return now oil chamber 361 (see Fig. l0) which is connected to thereturn pipe 366 by a pipe 368 (see Fig. 9).

Leading from the manifold 365 to the ports ||1 and I8 of the double acting piston motor |62 for elevating the gathering conveyor 4|, are pipes 368 and 316, respectively, controlled by valve 31|, which is similar to valve 316 hereinafter described in full detail. Also leading from said manifold 365 to the opposite ends of the piston motor |34 for swinging the gathering conveyor 4|, are pipes 312 and 313 controlled by a valve 314 which is similar in construction to valve 315. Valve 315 (see Fig. 10) is provided on manifold 365 and controls pipes 316 and 311 leading to the motor 222 for swinging the boom of the discharge conveyor 42. Another valve 318 is provided on manifold 365 which is similar to valve 315 except that only one of the pressure ports is employed, the other being plugged up, said one pressure port leading to pipe 318 connected to motor |94 for elevating the boom |68 of the discharge conveyor 42. Interposed between the pipe 319 and the return pipe 366 is a high pressure relief valve 386 which is effective to relieve the pressure on the boom |68 of the discharge conveyor 42 in case an overload is placed on said boom. It may be pointed out that the construction of the valves 31|, 314, 315 and 318 is such that fluid in the pipes 368, 31o, m, su, 31s, 311 and 319 may be kicked against movement in either direction. As a consequence, the movable elements of all the hydraulic motors |62, |34 and 222 may be locked in position. It is furthermore to be noted that each of said motors may be moved positively in reverse directions.

Attention is now directed particularly to Figs. 10 and 1l and to the construction of the by-pass valve 363, the manifold 365, and the operating valve 315 as representative of the four valves 31|, 314, 315 and 318. The by-pass valve 363 comprises a body casting 383 having a horizontally extending cylinder 384 within which moves a hollow piston 385 having a longitudinally extending bore 386 and communicating transversely 'Ihe casting 383 also proing communication between an inlet port 386 and an outlet port 38| of the casting 383. Within the piston 385 in the position illustrated in Fig. 11, oil from the pressure line 366 will 'ow, from the chamber 388 to the return pipe A366 which is connected to the casting 383 by a. fitting 382 by way of bores 386 and 381. It is thus obvious that in this position the by-pass valve 363 provides a substantially no-,load by-pass for the pump 351. This is the normal condtion of the by-pass valve 363 and is realized when none of the control valves 31|, 314, 315 or 318 is operated. Should any of the mentioned control valves be operated the piston 385 will move to the right, as viewed in Fig. 11, regardless of the direction of movement of the operating handle of the control valve, as hereinafter described in full detail, to close the `by-pass by shutting ol communication between the oil chamber 383 and thebores 381..

The piston'385 is provided with a plurality of spaced piston rings 333, there being groups of three on each side of the bores 381, to prevent valves 314, 31| and 318 may be operated to control and lock the motors 134 and |02 and to control motor |34. It may be mentioned, however, that the valve chamber similar to chamber 408 associated with the pipe 313 is merely plugged up instead of provided with a conduit, such as conduit 316 of valve 315.

It is to be noted that the manifold 365 is sup- I ported upon spaced brackets 403 and 410 (Fig.

leakage into the return pipe 366 when said piston 385 is in by-pass closing position. The piston 385 is provided with an operating rod 334 with which is associated a packing gland 335 to prevent any leakage of fluid from the by-pass valve 363. When the by-pass valve 363 is in by-pass -closing condition, as above described, fluid in the chamber 383 will be communicated to the pressure chamber 364 of the manifold 365 by way of the hollow coupling 336 which supports the casting 383 from the manifold 365. The pressure chamber 364 runs longitudinally of the manifold 365 to provide oil under pressure to all of the control valves 311, 314, 315 and 313.

vThe construction of the valve 315 is illustrated in detail in. Fig. l0, and, as abover mentioned, is representative of the valves 311, 314, 315 and 318. The by-pass valve 363 and the operating mechanism therefor are important features of my invention and are hereinafter described in full detail. It may be stated briey that the valve 315 comprises an operating handle 331 pivted upon a bifurcated bracket 333 and held in a normal upright position by spring means 333 and cooperating stop pins 400 and 431 carried respectively by the bracket 338 and the handle 331..

The handle 331 is pivotally attached to an operating shaft 432 formed integral with a. pair of control pistons 403 and 404 by a link 405.

It may be stated that when the handle 331 is moved to the right, as viewed in Fig. 10, the pistons 4113 and 404 will be moved to the right to eiect a communication between the pressure chamber 364 and the individual valve chamber 406 thereby to direct fluid under pressure to the pipe 316, which will be effective to operate the hydraulic piston motor 222 and4 thereby swing the rear part 111 of the discharge boom 169 in one direction about its pivot 182, the return path from the motor 222 being provided over pipe 311 by way of valve chamber 431 to oil return chamber 488 which is in constant communication with the general oil return chamber 361, Fig. 10. When the handle is moved to the left, as viewed in Fig. 10, oil under pressure in the pressure chamber 364 is communicated by valve chamber 401 to pipe 311 to operate the piston hydraulic motor 222 in the reverse direction, the return path for the oil. being provided by pipe 315, valve chamber 406 to return chamber 403 which is also in communication with the general oil communication chamber 361. It is, of course, evident by referring to Fig. 10 of the drawings, that when the lever 331 is in its normal, neutral position the pistons 403 and 404 lock the pipes 315 and 311 full of oil and thus lock the hydraulic motor 222 thereby holding the boom 163- in any predetermined horizontal position.

It will be evident that in a similar manner the 2) supported respectively from the bed plate 43 and the side member 153 of hopper 155. The brackets similar to the bracket 338 of valve 315 are removably attached to a cross-piece 41 1 which extends between'the brackets 403' and 413.

To' provide for the operation of the piston 385 of the by-pass valve 363 in the same direction to by-pass closing position, whenever any of the operating handles of the valves 314, 311, 315 and 318 are operated thereby to insure pressure in the pressure chamber 364 only when one of said control valves is operated, I provide mechanism now to be described. Said mechanism comprises a longitudinally extending shaft 412 having four operating levers associated with the valves 311, 314, 315 and 313, the lever associated with the valve 315 being seen at 413, which lever 413 is attached by a set screw 4151 to rotate the shaft 412. All of the levers corresponding to the lever 413 are likewise attached to rotate with the shaft 413. Lever 413 is provided with two adjustable stops 415 and 316 of which stop 415 contacts the operating lever or handle 391 and stop 416 contacts an integral extension of said lever 331 which is below the pivot point thereof provided by pin 411. upon the operation of the lever 331 in either a clockwise or a counter-clockwise direction the lever 413 will be operated in a counter-clockwise direction. (Fig. 10.)

Also rigidly attached to the shaft 412 by a set screw 413 (see Fig. 11) is a crank 413 attached by a link 423 to the center of a pivoted lever 421, the free end of which is attached to the operating rod 334 of the piston 385. It will thus be seen that upon the movement of the handle 331 in either direction, the piston 335 is operated in the same direction and to the left, as viewed in Fig. l1, to eect a closure of the by-pass, as previously described.

By reference td Fig. l2 of the drawings, it wili be seen that the lever 413 is urged in a clockwise direction by a spring 422 coiled about the shaft 413, one end of which is attached to a short lever 423 rigidly attached thereto by a. set screw 424, the other end of which is attached to the bracket similar to bracket 338 associated with valve 318. As previously mentioned, operation of the control handles of any of the valves 311, 314, 315 or 318 will be effective to rock the shaft 412 in the same direction thereby to close the by-pass valve 363. It is thus evident that under normal conditions the pump 351 will be operating at no-load but that upon the operation of any of the control valves in either direction the by-pass valve will be closed automatically and pressure will be available into the desired work.

In the operation of the loader comprising my invention, it may be trammed along a trackway in a mine to the place where the loading operation is to take place. During this tramming operation the drive Wheels of the truck will be driven at their fast speed and the electric cable will be paid out freely. The gathering conveyor will be elevated with its front end above the It is thus manifest that tracks by means of the hydraulic motor |02 and both the gathering and the discharge conveyors may be controlled by the operator who rides on a small platform on the truck 40 adjacent the above described controls, to swing said gathering and discharge conveyors, as required by the travel of the loader along a curved track.

Should a very steep incline be encountered it may be necessary to employ the iexible steel cable or rope associated with the drum 336 and reeve it about the two pulleys 344, 345 (Fig. 7) with the free end attached to a mine jack.v This arrangement is particularly desirable when traction feed tends to cause the truck wheels to slip on the mine track.

When the loading machine has reached the place where the coal is to be loaded, which coal has been previously cut and shot, with part thereof formed as loose coal and part formed as a semi-compact mass, the driving gears will be changed to drive it at a slow or sumping speed. The operator will then adjust the gathering conveyor 4| and the discharge conveyor 42, the former by lowering it in contacting relation with the mine tracks or, if the first operation is to take place adjacent the side of the mine tracks, to lower it into contact with the mine floor with the discharge conveyor 4| positioned to discharge into a mine car 43.

With the conveyor mechanisms of the discharge and gathering conveyors set into operation, and with the front end of the gathering unit resting on the mine floor in advance of the mine track, the entire machine may be fed forwardly providing'a frontal attack of the gathering conveyor 4| on the coal at the bottom of the mass of material to be loaded. The flights |43 and |44 will dig into the loose or semi-compact coal and feed it to the gathering conveyor 4|.

One special feature of operation of my device lies in the fact that the gathering flights |43 and |44 of the gathering conveyor 4| attacks the coal at the same time and in opposite directions to secure a balancing effect, thereby reducing to a minimum any tendency for the loader to jump off the tracks during the operation of the gathering mechanism.

A further very important feature of the operation of the fiights |43 and |44 also lies in the wedging action which they have due to the inclined serrated rib or comb |46. Due to this construction the flights tend to wedge under the coal, particularly when in a semi-compact mass, thereby breaking it down and at the same time providing a minimum of degradation due to the lack of a striking action comparable with a hammer blow.

It may also be mentioned that a low degradation is realized with my loader due to the fact that there is only a single rehandling of the coal by the loader, namely, at the hopper |55. This, of course, is realized by virtue of the fact that the gathering conveyor unit comprises continuous gathering mechanisms which operate through substantially the entire length thereof.

It is also to be noted that due to the fact that nights |43 and |44 extend laterally over the opposite edges of the fiat working portion 81 (Fig. 2) of the bottom plate 86 there is no tendency for the gathering conveyor to become wedged in the pile of coal, particularly when it is in the form of a semi-compact mass. Furthermore, a swinging or side attack on the coal may be carried out due to this particular construction. This is particularly useful in a final clean-up for, in general,

I prefer to operate the device as a frontal attack loading machine.

Another important feature of my invention lies in the fact that the double acting hydraulic piston motor |02 may be relied upon to suspend the front end of the truck fromthe gathering conveyor frame when the front wheels 5|, 5| are oil the mine track and located beyond the front end thereof while the front end of the gathering conveyor is supported on the mine bottom at its working portion 81. In such event the hanger plates |22 (Fig. 6) rest on the nuts |21 and the locked hydraulic motor |02 supports the front end of the turntable 66 and the latter in turn by means of the arcuate lifting plate |3| supports the front end of the truck 40 with -the front wheels off the mine track and spaced above the mine bottom beyond the front end of the mine track. It will thus be seen that the reach forward of the gathering conveyor may be extended without lengthening the mine track, it being necessary to retain only the rear wheels 56 on the mine track during the extended loading operations.

Furthermore, the double acting piston motor |02 is particularly useful to place the truck 40 back on the rails 66 if for any reason it is derailed. It is, of course, evident that the front wheels may be elevated and swung back over the rails by means of the reciprocating hydraulic motor |34 and then lowered to the rails by means of the motor |02. The rear wheels 56 may be elevated by placing a. jack between the front portion of the bottom plate 86 and the mine roof and expanding the piston motor |02, in which case the rear end of the truck 40 will be elevated about a pivot formed by the front wheels 5| and the axle 52; then by operating the piston motor |34 while the front end of the gathering conveyor remains anchored between the floor and the roof, the rear end of the truck may be swung into position so the wheels 56 are aligned with the track rails 66, after which the motor |02 is again operated to lower` the rear wheels 56 onto the mine track rails.

During normal operation, the conveyor boom 83 rests on the springs |26, |26, while the front wheels are on the mine track. When the gathering conveyor is adjusted in elevation the hydraulic motor |02 acts through the springs |26, |26 on the bottom plate 86 of the boom 83 but when the upward movement of the gathering conveyor is resisted by dislodged coal fallen from the semi-compact mass onto the receiving end of the gathering unit 4|, the springs |26, |26 may be compressed until the channeled crossmember |2| (Fig. 6) engages the transversely extending bar |24 to effect a direct, powerful and positive lifting of the receiving end of the gathering unit from the mass of dislodged coal. At the same time the truck propelling mechanism may be reversed to effect withdrawal of the gathering unit from such mass of dislodged coal.

It is also to be pointed out that all of the control levers for the mining machine are positioned at a single control station where they may be readily operated by the principal operator. Furthermore, due to the hydraulic control provided for swinging both the gathering and the discharge conveyors, the amount of work required by the operator is reduced to a minimum, being only that necessary to operate the control levers.

Furthermore, the complete control of the discharge conveyor 42 is extended to a position at the rear of the truck 40 where it may be operated by the trip rider. In this connectionit will, of course, be evident that the main operators attention will be required largely by the gathering conveyor and the trip rider will control the discharge conveyor, 1

It is also to be minted out that a single electric motor is provided for operating the entire loading machine including the providing of fluid pressure for the hydraulic control system. No auxiliary electric motor of any kind is required on the loading machine comprising my invention.

A general review of the construction and operation of the mining and loading machine shown in the accompanying drawings will show more clearly the flexibility of adjustments to obtain `the most efllcient operation in mining and loading coal by attacking a semi-compact mass oi coal shot down from the face o a coal vein. Under control of the valve 318 shown in Fig. 2 the rear end of the discharge conveyor |69 may be adjusted in elevation to the full line and dotted line positions shown in Fig. 3, by means of the vertical reciprocating hydraulic motor iSd. By means of the valve @1i shown in Fig. 2 the upright reciprocating hydraulic motor EQ2 may be operated to adjust the front end of the gathering conveyor to its full line or dotted line positions shown in Fig. 2. When the gathering conveyor is in the full line position shown in Fig. 2, the whole machine may be transported along the mine track under the control of the forward operator who may start or stop the electric motor 22d of Fig. i by means of motor controlling mechanism. By means of a reversing switch the operator may reverse the electric motor 22d and thereby control the direction of travel of any of the conveyor chains should they become stalled.

The truck propelling means comprises power transmission mechanism between the electric motor 22d and all of the wheels 5i and 56 of the truck, as shown in Figs. 4 and 3. This power transmission mechanism is under the control of the clutch 229 in Fig. e. The operator may apply or release the clutch 22S 'by rocking the shaft 251 (Fig. 4). The truck propelling power transmission mechanism also includes reversing clutches 259 and 2t@ shown in Fig. 7, either of which may be applied by the operator actuating the lever 4M in one direction or the other and consequently the loading machine during operation may be moved along the mine track in either direction without reversing the electric motor 221i.

When the shaft 262 of Fig. 4 is rotated in one direction or the other,. the pinion 212 thereon drives the reduction gearing shown in Fig. 7, which is under the control of the clutches 286 and 25 for the purpose of securing relatively low speed and relatively high speed of transmission to the transverse shaft 215.

A sprocket chain drive comprising the sprocket 293 on the shaft 215, connects the shaft 215 withv the axle '51 shown in Fig. 7. It will thus be seen that the electric motor 224 may be continuously operated in the same direction while by means of the clutches 25S and 26B in Fig. 7, the gathering mechanism may be moved forwardly or rearwardly under the control of the operator, and such forward or rearward movement may be at relatively fast speed or at relatively slow speed under the -control of the clutches 285 and 285 of Fig. 7. A slow powerful surnping movement into the semi-compact mass of shot down coal may thus be effected, and whenever desired a slow, powerful withdrawal movement of the gathering mechanism may also be effected.

The power transmission mechanism connected between the motor 224 and the pair of endless conveyor chains on the gathering device 4|. comprises the gear 240 on the vertical shaft 230 of Fig. d. The gear 240 meshes with the gear 25| which in turn meshes with the gear 254, and the latter is in mesh with one of the gears 255 as" shown in Fig. 8. Since the gears 25'6 mesh with each other, the nights of the gathering conveyor are in such xed relation to each other that they travel in pairs, in opposite directions, as illustrated in Fig. l. The starting and stopping of the pair of endless chains of the gathering conveyor are controlled by the clutch 229 shown in Fig. 4. During normal operation of the gathering conveyor the nights move in pairs towards the discharge conveyor lli and therefore the motor 224 should be continuously operated in the same direction. Should a lump of coal get caught between the rear end portion of the gathering conveyor and the roof of the mine chamber, the crowding and wedging action will be downward against the upwardly extending serrations of the nights |63, |44 (Fig. l) and against the points of the cutter bits |55, thereby eiecting a crushing of the unusually large lump of vcoal so that delivery of the coal to the discharge conveyor need not be interrupted. If there is an overload on the gathering conveyor chain 5| due to contact between nights E53l or Idil and solid or irremovable coal, the friction clutch 22d will slip, whereupon the proper clutch 255 or 25@ may be operated to cause the machine to move rearwardly thereby causing the conveyor flights It@ and idd to release the contacted coal and relieve the overload.

Under the control of the lever 31d shown in Fig. 2, the operator may control the swinging of the gathering conveyor laterally on its vertical pivotal connection at 255 (Figs. e, 5) to the truck frame M, and during such lateral swinging movement of the gathering conveyor its frame 68 rests at its forward end on the rollers |28, as shown in Fig. 5. A single reciprocating hydraulic motor i3d, pivotally connected at its ends to the truck frame and the gathering conveyor frame, is relied on to swing the forward end of the gathering conveyor laterally to various angular positions relative to the mine track. The gathering conveyor may be locked by means of the motor |36 in its angular. adjusted position when the loading machine is to be sumped or withdrawn rectilinearly parallel to the mine track, but it should be understood that the reciprocating hydraulic motor |34 is sufficiently powerful to swing the forward portion of the gathering conveyor in either direction for lateral attack on a semi-compact mass of shot-down coal, and at various elevations illustrated in full and dotted lines in Fig. 2.

After a mine vein has been undercut and shot down it may remain standing for several feet back from the face in a semi-compact mass termed a standing shot. Some of this may 'be tight at various elevations but the frontal attack of the gathering unit may be relied on to eect a V-shaped kerf in. such semi-compact standing mass at the mine bottom or at Various elevations to complete the dislodgment of the coal `and its falling onto the receiving end of the gathering unit. l

The discharge -conveyor comprises two sections |10 and |16 (Fig. 4), with the rear section |1| movable laterally on the upright pivot |82. Hydraulically operated mechanism comprising the hydraulic motor 222 is controlled by the valve 315 (Fig. 2) to effect power swinging of the rear section of the discharge conveyor. By. means oi' the mechanism shown in Fig. 1 the continuity of the sides of the conveyor trough I1| is maintained notwithstanding the fact that the discharge conveyor comprises a single endless chain |65 having links pivotally connected on vertical and horizontal axes, this chain being similar in construction to the chain 9 I, as shown in Fig. 5.

The cable reel 325 (Fig. 1) may be operated by power to wind up the cable 323 which contains the insulated wires connecting the motor 224 to the distant source of electric power supply. The pawl and ratchet mechanism permits paying out of the cable 329 as the machine moves forward.

By applying the clutch 331 and rotating the shaft 215 in a clockwise direction, as viewed from the right-hand side of the machine, the rope drum 336 may be rotated to move the whole machine along the mine track either for moving up a steep grade, or for moving the gathering mechanism into a compact mass of s-hot-down coal, particularly when the wheels tend to slip with traction feed. In such event one end of the feed rope is connected to and wound on the drum 336, and the free end anchored extraneously to the loading machine and at such a position that the machine will be pulled forwardly when the drum 336 is rotated.

When the clutch 331 is applied the rope drum 336 is connected directly to the shaft 215. Consequently by rotating the shaft 215 in either direction the drum 336 may be rotated in the same direction to eiect winding of the cable on the cable reel 336.

It is preferred that a main operator should be in a position to operate all of the controlling levers and that another operator should be able by means of extended actuating connections, to control adjustments of the discharge conveyor independently of the operation of the gathering conveyor. As the mine cars are brought up, loaded, and replaced by empty cars, a rear operator may start and stop the discharge conveyor and adlust the elevation of the rear end thereof as well as its lateral position. The main operator will know when the discharge conveyor stops without looking backward and thus stop the gathering conveyor to prevent overflow from hopper |55.

Whenever the electric motor 224 is operating, the pump 351 by means of mechanism shown at the left-hand end of Fig. 7 is being continuously operated so that at all times the hydraulic system is in readiness for performing the various adjustments by means of the hydraulic reciprocating motors |02, |34, |94 and 222. The controlling valves 31|, 314, 315 and 318 when released, automatically move to their neutral positions where the hydraulic motors are locked, thus rigidly holding the various parts in adjusted positions. It is important to note that whenever a controlling valve is manually released it is returned automatically to neutral position and at the same time the by-pass valve 363 is automatically moved to no-load position. rI'he high pressure Valve 352 opens only when the maximum output of pressure is exceeded but when the valve is opened, a very free passageway is provided for by-passing the liquid continuously pumped by the pump 351 while the main motor 224 is continuously operating.

It should be understood that when the gathering conveyor unit is swung laterally the hopper |55 of the discharge conveyor apparatus remains stationary. The rearwardly extending wings IBI, I6 I shown in Figs. 1 and 5 have their lower edges in overlapping relation to the upper semi-circular edge of the semi-funnel shaped chute |59. Such wings IBI, I 6|' move bodily with the gathering conveyor unit. As the flights leave the rear edges of the plate they move away from each other and any material thrown laterally will be deflected by the wings ISI, IBI into the hopper |55. Furthermore, such wings extend upwardly from the lateral edges of the chute |53 to cooperate with the latter to deepen the hopper |55.

Obviously those skilled in the art may make various changes in the details and arrangement of parts without departing from the spirit and scope of the invention as dened by the claims hereto appended, and I therefore wish not to be restricted to the precise construction herein disclosed.

Having thus described and shown an embodiment of my invention, what I desire to secure by Letters Patent of the United States is:

1. A loading machine comprising the combination with a wheeled truck adapted to travel on a mine track, of a conveyor apparatus including a forwardly extending gathering unit pivoted to the wheeled truck at its rear end portion on horizontal and vertical axes with the forward end of said gathering unit resting on the ground in advance of said wheeled truck, and fluid pressure motor mechanism connected to said gathering unit to depend therefrom and adapted to lift the wheeled truck when derailed for replacement on the track while the forward end of said gathering unit rests on the ground as aforesaid.

2. A loading machine comprising the comblnation with a wheeled truck adapted to travel on a mine track, said truck having two pairs of wheels, of a gathering unit mounted on said ltruck, a turntable on said truck, a pivotal connection between said gathering unit and said turntable on a horizontal axis, means comprising a hydraulic motor for rotating said turntable to swing said gathering unit on the upright axis of the turntable, means comprising an additional hydraulic motor between said gathering unit and said turntable for swinging the gathering unit on said horizontal axis to adjust the elevation of the forward end of said gathering unit, and means for controlling said hydraulic motors while the forward end of the gathering unit rests on the ground to effect lifting and turning of the trunk in either direction 4when derailed and thereby replace the Wheels of the truck back onto the track.

3. In a track mounted loading machine, the combination with a wheeled truck adapted to travel along a mine track and comprising a truck frame having a forwardly projecting plate, of a supplemental frame mounted on said truck frame, a connection between said supplemental frame and the said forwardly projecting plate, a gathering conveyor mounted on said supplemental frame in position for its outer end to rest on the surface from which the material is to be gathered in advance of the mine track, a fluid pressure motor, and means for connecting said motor between said supplemental frame and said gathering conveyor in position toenable such motor to adjust the elevation of said gathering conveyor relative to such surface when the truck is on the mine track and to lift by means of the aforesaid connection the forward end of the truck relatively to the track when the truck is derailed.

4. In a loading machine, the combination with a wheeled truck adapted to travel on a mine track and comprising a truck frame having a forwardly extending arcuate plate, of a supplemental frame mounted on said truck for-arcuate adjustment relative thereto on an upright axis, a gathering conveyor pivotally connected to said supplemental frame on a horizontal axis with the forward end of said gathering conveyor adapted to rest on the surface from which the material is to be loaded in advance of the mine track, an arcuate support on said supplemental frame in position to extend under said forwardly extending arcuate plate. means for swinging said gathering conveyor on said upright axis relatively to said truck when the latter is on the mine track, and means for adjusting said gathering conveyor on said horizontal axis relative to said supplementall frame so connected between the latter and said gathering conveyor that when the forward wheels of said truck are derailed said swinging means shall be capable in co-operation with said adjusting means in replacing said front wheels on the mine track while the forward end of said gathering conveyor is held against swinging laterally.

5. A loading machine comprising the combination with a truck having front wheels and rear wheels adapted to travel on a mine track, of a gathering unit mounted on said truck for adjustment relative thereto on a horizontal axis, said gathering unit projecting forward from said truck with its front end adapted to rest on and slide along the mine bottom in advance of the mine track, means comprising a double acting hydraulic motor depending from the gathering unit and connected to the front end of the truck, means for moving the loading machine along the mine track to enable said gathering unit to gather a load of loose material from the mine bottom-in advance of the mine track, and means for controlling said hydraulic motor to elevate the receiving end of the gathering unit above the mine bottom while the front wheels of the truck are on the mine track or to lock the motor while the front end of the gathering unit rests on the mine bottom to enable such motor to suspend the front end of the truck with the said front wheels up ofi' the mine bottom while ot l the track and in advance thereof to extend the gathering operations in advance of the mine track.

6. In a machine of the class described, the combination with a supporting frame, of a. gathering conveyor mounted thereon, a hydraulic piston motor comprising a cylinder. a piston and a piston rod, a yoke connected to the piston rod, spring means attached to the legs of said yoke and to said gathering conveyor and so constructed and arranged that said gathering conveyor is supported by said piston rod through said spring means, means connecting said cylinder to the forward portion of said frame, and means for adjusting and locking said piston in said cylinder.

N115 D. LEVIN.

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