US2334770A - Mining machine - Google Patents

Description

Nov. 23, 1943. R. K. JEFFREY MIN'ING MACHINE 4 Sheets-Sheet 1 Original Filed July 6, 1934 .5 w R T mw fihpfi mm W, E m

Nov. 23, 1943; K, EFFRE 2,334,770

MINING MACHINE Original Filed Ju 1y 6, 1934 4 Sheets-Sheet 2 l/vvzs/v TOR: R BERT KJEFF R EY,

Nov. 23, 1943. R. K. JEFFREY MINING MACHINE Original Filed July 6, 1934 4 Sheets-Sheet s A TT'X f/VVENTOR r ROBERTIKJEFFREY,

Nov. 23, 1943'. R. K. JEVFFREY MINING MACHINE Original Filed July 6, 1954 4 Sheets-Sheet 4 f/VVE/VTOR ROBERT KJEFFRE A TT'Y Patented Nov. 23, 1943 UNITED "STATES TENT QFFI-CE MINING MACHINE ration of Ohio Original-application July 6, 1934, Serial No.

733,999, now Patent No. 2,263,701, dated November 25, 1941.

Divided and this application November 18, 1938, Serial No. 241,239. In Great Britain July 28, 1933 2 Claims.

My invention relates to a mining machine of the universal type, and one of its objects is the provision of improved and efllcient apparatus for controlling the operation of a mining machine by hydraulic means, particularly for feeding the mining machine and swinging the cutter mechanism thereof, both during cutting of a kerf and during transportation or cramming.

Another object of the invention is to provide improved slow speed feeding and high speed tramming mechanism for a mining machine, including a hydraulic system.

Still another objector the invention is to provide a new and improved hydraulic system of control particularly adapted for mining machines.

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

In the accompanying drawings,

Figs. 1. and 2 placed end to end combine to make a plan view of the machine shown of my invention;

Fig. 3 is a sectional elevational view of the two speed reduction gearing for the truck drive;

Fig. i is a sectional view taken along the line 4-4 of Fig; 3 looking in the direction of the arrows;

Fig. 5 is a sectional view taken along the line 5-5 of Fig. 3 looking in the direction of the arrows;

Fig. 6 is a sectional view taken along the line 56 of Fig. 1 looking in the direction of the arrows;

7 is a piping diagram of the hydraulic system;

Fig. 8 is a sectional View of the control'valve for the turntable hydraulic motors;

Fig. 9 is a plan view of the reduction gearing control valve;

10 is a sectional plan view of the valve of Fig. 9; and

11 is a sectional view of a hydraulic motor control valve,

This application comprises a'division of my application for a Mining machine, Serial No. 733,999, filed July 6, 1934, now Patent No. 2,263,701, dated Nov. 25, 1941.

Referring to Figs. 1 and 2 of the drawings, it will be seen that the mining machine comprises a base frame 29, which is supported on a pair of track engaging rear wheels one of which is seen at 2!, and a pair of track engaging front wheels 22, the former being mounted on an axle 23 iournalled in bushings in an appropriate housing. The frame 29 is mounted on said housing 'by (ill. 262-28) trunnions providing pivotal movement of said frame 29 relative to said housing and to said rear wheels 2!, 2| along the central longitudinal axis of said machine. The front wheels 22, 22 are supported on an axle 25 carried within an appropriate axle housing which is attached to the base frame 20 by a pair of pivoted arms, one on each side of said machine, the pivotal attachment between the arms and the frame 29 being provided by appropriate knuckles.

Adjacent their forward ends the arms are provided with piston rods 28, 23 (see Fig. 7), which are connected to pistons 29, 29 which extend into cylinders of hydraulic piston motors so, 39 (see Figs. 2 and '7).

By controlling the hydraulic motors 30, 35, the wheels 22, 22 -may be individually adjusted in elevation relative to the frame 20, thereby adjusting the slope of said frame 29 relative to a horizontal plane. This is useful to level the frame 20 when the machine is mounted on an uneven track and is useful to tilt the frame 2i! about either a transverse or a longitudinal axis.

Mounted upon the frame 20 for pivotal movement about an upright axis positioned substantially midway between the rear wheels 2 I, 2| and the front wheels 22, 22, and supported by antifriction rollers is a turntable 32. The turntable 32 has on its lower face a track adapted to take the wear between said rollers and said turntable. On the lower face of the turntable there is provided a downwardly extending drum which is provided with an external gear (not shown) with which cooperate racks formed on the ends of apair of spaced piston rods 35, 35 (Figs. 1 and '7), which piston rods are associated with pistons of the two piston motors 36, 38. It will thus be evident that by controlling said motors 36, 36 the turntable 32 may be adjusted about its upright axis to any desired position and by locking said motors in any adjusted position the turntable will be held in said position against rotation.

Rigidly mounted upon the upper face of the turntable 32 there is provided a pair of side castings 37, 31, the rear ends of which are provided with journalled bearings 38, 3d. Extending between the journalled bearings 33, 38 and loosely journalled therein, is a rock shaft 39. At each side of the bearings 38, 38 there is a bearing 39, 49, which bearings tit form the ends of a plurality of forwardly extending arms H, M, of which there are four, two at each side of the turntable. Said arms 6!, ll ar provided with bearings d2, 62 at their forward ends which are rigidly attached to a transversely extending shaft 43. t may also be pointed out that the bearings 4|), 40 are keyed to the shaft 39. The shaft 43 extends into journalled bearings in the housing of an electric motor 44, whereby said motor 44 may rotate on said shaft 43.

Trunnioned between each of the pairs of arms 4|, 4! at each side of the turntable and approximately midway between the shafts 35 and 43 isa,

hydraulic piston motor 45. Each of the piston motors 45 is provided with a piston rod 46 which is pivoted to the adjacent casting 31. It Will-be evident that by adjusting the piston motors 45, the arms 4|, 4| may be pivoted about the rock shaft 39 and thus the forward portion of the electric motor 44 may be adjusted in elevation. At its rear end the motor 44 is provided with a bracket 41, to which is trunnioned a piston motor 43 having a piston rod 49 pivoted to the rear end of the turntable 32. It will be evident that the piston motor 48 may beoperated to pivot the motor 44 about the axis of shaft 43. It may be mentioned that the motor 44 rests between the inner pair of side arms 4|, thus maintaining the over-all height of the machine as determined by the top of the motor 44, at a minimum.

Rigidly attached to the housing of motor 44 is a gear housing 58, within which are appropriate gears which are part of a train which effects a driving connection between the motor 44 and the cutter chain, as will be hereinafter described in more detail. The gear housing 50 has adjacent its forward end a downwardly sloping neck, not

visible in the drawings, upon which is journalled a turn-over head A, formed by a casting 5|, which casting 5| is journalled on said neck for rotation about a longitudinally extending and downwardly sloping axis when the machine is in the position illustrated in Figs. 1 and 2. The forward end of the casting 5| terminates in a drum-shaped portion 52.

To provide for turning over said turn-over head A on th aforementioned axis, the rear portion of said casting 5| has attached thereto a worm gear within housing 49 which is adapted to be driven by a rotating type of hydraulic motor 53. It will be evident that by controlling the rotating motor55. the turn-over head A may be adjusted to any desired position about the axis of said aforementioned neck.

Extending transversely of the drum-shaped portion 52 along the central axis thereof, is a transverse shaft upon which is mounted for rotation a pair of side plates 55, 55 which cover the open ends of said drum-shaped portion 52. Adjust ment of said side plates 55, 55 about the axis of said transverse shaft is provided by a hydraulic piston motor 56 mounted upon the casting 5| and connected to brackets 51, 5'! carried by said side plates 55, 55 by appropriate connecting links 56, 58. Adjacent their bottoms, the side plates 55. 55 cooperate to provide a circular supporting track which supports the rear plate 59 of a cutter bar 66, upon which rides endless hit carrying cutter chain 54, whereby said cutter bar 66 may be pivoted with respect to said turn-over head A about an upright axis with respect to the plane of cutter bar 66. It will be evident that this axis may be adjusted to and from a vertical position by adjustment of the side plates 55 as directed by piston motor 56.

To swing the cutter bar 66 about said upright axis, I provide a pair of hydraulic piston motors 6|, 6|, which are trunnioned to brackets 62, 62 carried by side plates 55, 55. Piston rods 63, 63 of said motors 6|, 6| are pivotally attached to opposite sides of the plate 59 by brackets 62'. It will thus be evident that by adjusting the piston motors 6|, 6|, the cutter bar 60 may be swung about an axis permanently at right angles to itself, which axis is at right angles to the transverse axis and intersects both the latter axis and the axis of the turn-over head.

It is also to be noted that the cutter bar 66 may be swung in a horizontal plane about the axis of the turntable 52 by controlling the hydraulic piston motors 35. 36. It is thus possible to cut a relatively horizontal kerf in a plane which has a slight slope to the horizontal by swinging the cutter bar 66 about the axis of the turntable 32 as aforesaid, such slope being predetermined by adjusting the hydraulic piston motors 36, 35 in a manner previously described. Cutting of a kerf at a slope to th horizontal about the axis of the turn-over head A will, of course, be provided by adjusting the casting 5| by motor 55.

It will be evident that due to the numerous adjustmentspreviously described, substantially horizontal kerfs can be out from a position below the mine tracks to a very great height or along any plane intermediate the two extremes. It is also possible to cut kerfs at any desired slope between the horizontal and vertical position. Furthermore, vertical kerfs may be out along parallel planes of an appreciable Width in a mine room.

Extending rearwardly from the base fram 28 and forming a portion thereof, I provide a supporting platform 64. Upon said platform 64 is mounted a reversible electric motor 65, adapted to be controlled by a control box 66 operable by handle 61. Motor 65 is provided with a shaft 68, which extends laterally from each side thereof, and at one side drives a pump 69 which may be of any desired structure. The shaft 68 carries a pinion 10 adjacent its other end, which pinion meshes with a gear 1|. The gear drives a two speed hydraulically controlled planetary clutch and reduction gear mechanism 12 hereinafter described in full detail, which drives a pinion 16 at a relatively fast or relatively slow speed, depending upon how it is operated. The pinion 6 drives a master gear 11 which is keyed to a shaft 18 (Fig. 6). Loosely journalled on said shaft 1-8 is a sprocket 19 which is connected to a sprocket on one of the rear wheels 2| by a chain 8|. Also loosely journalled on the shaft 18 is a gear 82 which meshes with a gear 83 formed integral with a winding drum 84 about which is wrapped a flexible cable adapted to be anchored in the mine extraneous to the machine to effect slow feeding thereof.

Clutches 85 and 88 are interconnected by rod and are operable from a handle 81, and when operated in a position to engage the clutch to effect a driving connection between the shaft 18 and the wheel 2|, rod 80 insures that the drum 84 is not in driving relation with said shaft '18. When the clutch 88 is in operating relation to connect the drum 84 to the shaft 18, it insures that the wheel 2| is disconnected from said shaft 18 thus preventing operation of the drum 84 and sprocket 19 at the same time.

It will thus be seen that by actuating the clutch 85 to effect a driving connection between the shaft '18 and a wheel 2|, the mining machine may be propelled through the mine by the motor 65 at a relatively slow feeding speed, or at a relatively fast tramming speed, as hereinafter explained more in detail. The machine may move in either direction at either the fast or slow speed -by'reversing the direction of rotation of the motor "65 Itmay" be pointed out that the 'rear wheels 2| :are both keyed to the drive shaft, andthus both of. said wheels are driving wheels. Furthermore, a

which drives chain and sprocket drive mecha- I nism I4 controlled by'clutch'92. It.may be noted that the clutch 92 has helical teeth to allow the cable from reel J90 to pay out'freely, or to reel in the cable by power as the mining machine is being. moved under power, or it may be paid out or'reeled in while the mining machine is standing still, as the clutch-i2 is entirely independent inits operation.

.Also mounted upon the platform 64 is a control box 93 for controlling the electric motor 44. Appropriate electric cables, not shown, connect the control box 93 and the motor 44.

In addition to those elements previously described, it may be noted that there is carried on the platform 64 a distributing valve 94, the function ofwhich will be described more in detail hereinafter, and three operating valves having handles 95, -96 and 91 for controlling various hydraulic motors, as hereinafter described in more detail. It may be additionally mentioned that mounted upon the turntable 32 are five valves, having handles 98, 99, I60, IOI and I02, which will also be described more in detail hereinafter.

Before describing in detail the particular hydraulic system comprising my invention, attention is directed to Figs. 3, 4 and 5, and to the structure of the hydraulically controlled planetary clutch and reductiongear mechanism 12. The gear II is keyed to and drives a shaft :53 one end of which is'journalled in the housing of motor 65 and the other end of which is journalled in a shaft I04 which drives gear It which is keyed thereto. Keyed to the shaft IE3 is a spider not which carries a pair of diametrically positioned shafts I26, the outer ends of which are rigidly attached together by a bracket Iill. The shafts I06 are provided with appropriate journal bearings I08 upon which are journalled, integrally formed or connected planetary gears Hi9 and II!) which have an unequal number of teeth. As 11 lustrated in the drawings, gears I89 have sixteen teeth and gears I I B have fifteen teeth, though these numbersare not critical.

Journalled loosely upon the shaft 33 is a sun gear ill which meshes with both of the gears I09. Sun 'gear IN is keyed to a friction drum H2 provided with a peripheral groove I I3 adapted to receive a friction brake band I M provided with friction brake band'lining material I I5. By reference particularly to Fig. 3 of the drawings, it will be seen that the brake'band Il l is pro- Vided with a central attaching lug H6 having an oval shaped aperture II'i therein through which a supporting rod H8 extends, which rod is supported by an extending arm H9 formed integral with a bracket I26 which provides a journal bearing I 2I for previously mentioned shaft lad. The freeends of the brake band IM are connected together-byhydraulic piston motor mechanism I22 (see Fig.1), similarin struc- 169. E39 adapted to receive a brake band I 3| proturetoithehereinafter described mechanism I 34, 'andfed bypipe or conduit I25.

Formed integral with the shaft I04 is a ong :shaped member I26 provided with an integral internal ring gear I2! which continuously meshes with the two planetary gears I Iii. J ournalled to rotate freely on the exterior of the cup shaped -member 126 is a drum I28 which is provided with an integral internal ring gear I29 which continuously meshes with the planetary gears The drum I28 is provided with a groove vid'ed with friction brake band lining material 32. The brake band I3! is provided with an attaching lug I33 similar in structure and function to the lug H6 and is provided with a hydraulic piston motor mechanism I34 comprising apair of brackets 123 one attached to each of thefree ends of the brake band I3I between which extend a helical spring I24 urging the two :halves of the brakeband i3I into a non-braking position. The two brackets I23 are adapted to be forcibly drawn together by a cylinder and piston form of hydraulic piston motor of a type commonly employed with the brakes of an automobile which is supplied with hydraulic fluid by way of a'pipe or conduit I35.

It'may be stated that the number of teeth on the ringgears I21 and I29 is the same, but this condition is not absolutely essential.

The hydraulically controlled planetary clutch and reduction gear mechanism '52 is operative to effect a two-speed drive between the shaft Hi3 and the shaft I04. It may be stated generally that whenever hydraulic piston motor mechanism i 22 is operating to apply its associated braking mechanism a relatively high speed drive will be effected between said shafts I03 and IE4 to increase the speed of shaft Hi4 over that of shaft I63, and in the instant case the ratio will be 1 to 1.285. On the other hand, when the hydraulic piston motor mechanism I34 is applied, the speed ratio between the shafts I03 and We is substantially reduced in the ratio of 16 to 1.

The high speed drive with the hydraulic piston motor mechanism I22 applied operates as follows. Upon the operation of said hydraulic piston motor mechanism 622 the friction drum II2 will'be stopped gradually by a well understood clutching and braking action common with planetary gearing, whereupon sun gear III will be stationary. Spider H15 being in rotation, will cause the planetary gears I09, I29 to walk around the stationary 'sunlgear Hi. Gears I 09, being rigid with 'gears Hi3, which also walk around with spider IE5 and drive the cup shaped member I26 due to their meshing with ring gear I 2?. Cup shaped member E26 is, of course, integral with shaft I64 and effects a driving action thereof.

As was above mentioned, the ratio of the drive between shafts m3 and N14 is 1 to 1.285. This particular ratio is due to the number of teeth on the gears I69, IN MI and I21, there being fifteen teeth on' gears H6, sixteen teeth on gears I89, fourteen teeth on gear III and forty-six teeth on gear I27. noted that gear I29 has forty-six teeth also.

In analyzing this high speed power transfer between shafts I63 and I65 it may be observed that as spider IUZi rotates, gear I21 would rotate at the same speed if gears Iii; and I21 had no relative rotation. This alone would provides one to one ratio between shafts I93 and I'M.

In passing, it may also be 'However, since gear I II isstationary, there is in unison with them.

relative rotation between gears Ilfl'and I21 and for each rotation of the spider I95 the additional rotation of shaft I94 over that of shaft I93 is equal to the number of teeth on gear I21 T (46), divided into the number of teeth on gears H9 (15), multiplied by the ratio between the number of teeth on gear I II (14) to the number of teeth on gears I99 (16). In this latter connection it is evident that a clockwise rotation of the spider I95, as indicated by the arrow in Fig. of the drawings, will cause gears I99 to rotate about its own axis W of a revolution for each revolution of said spider I95.

In effecting the low speed drive the hydraulic piston motor mechanism I34 is energized to apply the brake band I 3| which progressively stops rotation of drum I28 and integral ring gear I29. Therefore, a spider I95 rotates, gears I99 walk around gear I29 and, of course, rotate gears Hi! When the spider I95 has rotated through an angle suflicient to rotate gears I 99 one complete revolution, or through sixteen teeth, gear I21 which meshes with gears H9 will only have rotated through fifteen teeth because gears H9 only have fifteen teeth. As a consequence, during this complete rotation of gears I99 and H9 there will be relative movement between drum I28 and the cup shaped member I26 equal to one tooth. The speed reduction ratio will therefore be sixteen to one since there are sixteen teeth on gears I99.

It is, of course, evident that brake mechanisms I22 and 34 should not be applied together and the hydraulic control system includes a particular type of control valve for controlling these hydraulic control mechanisms I22 and I34 which precludes their operation at the same time.

Referring particularly to Fig. 7 of the drawings, there is seen a complete hydraulic system comprising my invention and referring to Figs. 8, 9, and 11 there is illustrated in more detail certain of the valve mechanisms shown diagrammatically in Fig. 7.

Leading from a hydraulic fluid reservoir I35 is a feed pipe I31 for feeding reversible pump 99, having its output connected to pressure pipe or line S. Four interconnected check valves I38, I39, I49 and I4I so interconnect pipes I31 and S that regardless of the direction of rotation of pump 99, pipe S is always the pressure pipe. Interconnecting pressure pipe S and return pipe E is a high pressure relief valve I42 and a hand operated by-pass valve I43, the latter of which is normally closed but which may be open to relieve the load on pump 59 if it is rotating while doing no useful work.

Referring particularly to Fig. 7 it is to be noted that the supply or pressure line S is common to a plurality of control valves having operating handles numbered 95 to I92 inclusive. The structure of each of these valves is substantially the same and thus a description of one will suffice for all. One such device is disclosed in detail in Fig. 11 and will now be described. Said valve comprises a casing I44 provided with three chambers I45, I46 and I41. The supply line S leads to the central chamber I45 and two branches of the exhaust or return line E lead to the outside chambers I45 and I41. Between the chainbers I45 and I46 is a small outlet chamber I48 leading to an outlet conduit I49, and between the chambers I46 and I41 is a small outlet chamber I59, leading to a conduit I5I.

Extending into the casing I44 for controlling the flow of the fluid pressure medium or hydraulic fluid to and from the conduits I49, I5I is a pair of valve pistons I52 and I53 carried on a shaft I54. An operating handle 95 is provided for operating the shaft I54, said handle being biased to a neutral position at which pistons I52 and I53 close the chambers leading toconduits I49 and I5I respectively, said bias being provided by a spring I56.

hi the neutral position of the valve, the pistons I52 and I53 completely close off the small chambers I48 and I59 respectively and thus seal the conduits I49 and I5I. Any hydraulic piston motor which is connected to these conduits will thus be locked in adjusted position. If the handle 95 is moved to the left as illustrated in Fig. 11, the hydraulic pressure from the supply or pressure line S will be directed through chambers I46 and I48 to the conduit I49, and the conduit I5I will be connected to the exhaust or return line E, through chambers I59 and I41. If the handle 95 is operated to the position illustrated in dotted lines, Fig. 11, the pistons I52 and I53 will be moved to the right, under which conditions conduit I5I will be connected to the supply or pressure line S through chambers I45 and I59, while conduit I49 will be connected to the exhaust or return line E through chambers I48 and Returning to a consideration of the complete system as disclosed in Fig. '7, it will be evident that by controlling the handle I92, the rotating hydraulic motor 53 may be caused to rotate in either direction, depending upon which direction the handle I92 is moved from its neutral position. Said motor 53 is connected to its control valve through conduits M911 and I5Ia. The motor 53, of course, controls the turning over of the head A of the mining machine as was previously described. Handle I9I through its control valve controls the two motors 9|, 6| which are always operated in unison and in re-- verse directions through the conduits I49bwand I5Ib. Said motors 6|, 6|, of course, control the swinging of the cutter bar 69, as previously described. The valve provided with handle I99 controls the hydraulic piston motor 56 through conduits I490 and I 5I0, said motor 56 being operative to adjust the cutter bar 99 about the axis of the transverse shaft extending transversely along the axis of the drum-shaped portion 52 as was previously described.

Associated with the hydraulic piston motor 59 I also provide a valve I51 which may be open to connect the conduits I490 and I5Ic to allow free movement of the piston rod of said motor 55, even though the valve associated with the handle I99 is in a closed position. This is useful when the mining machine is employed to cut a vertical kerf while moving along a curved track, under which conditions the cutter bar 99 is allowed to swing freely on the axis of the previously mentioned transverse shaft. It will be obvious, of course, that by closing the valve I51, the motor 59 is under the direct control of the valve associated with handle I99.

Motors 45, 45 which control the tilting of the cutter bar and the electric motor 44 about the axis of shaft 39, are controlled by the valve with handle 99 through conduits I49d and I5Id. These two motors operate in parallel and in the same direction for obvious reasons.

The hydraulic piston motor 48 which controls the tilting of the cutter bar 69 and the electric motor 44 about the axis of shaft 43 is controlled from the control valvehaving handle 98 through conduits I49e and IIe.

It will, of course, be obviousthat, due to the fact that there is a conduit connected to each end of the motor cylinders 53, 6|, El, 56,. 45, 45 and it, said motors are reversible and also will be locked in any position to which they are, adjusted when their respective control valves are in neutral positions. This also, applies .to the motors 36, 3E) and 36, 36.

Said motors to, 36 which control the tilting of the turntable 32 are provided with separate control valves havin handles 9'5 and 96 respectively and are connected to their respective controlvalves by conduits his) and I 5i) and I49g I58 to IN, inclusive, may be closed to insure that the motors 39, 66 will be locked in position. It

is, of course, evident that individual control of the motors 36, 30 is desired so that the turntable 32 may be tilted relative to the horizontal plane along either a transverse or a longitudinal axis of the machine.

The control valve provided with handle 95 controls the two hydraulic piston motors 36, 36 which adjust the turntable 32 about its upright axis, but this control is made variable by the inter-position in the control system of the. dis

tributor 94 shown in detail in Fig. 8.

The description of the operation of said motors 36, 36 under the control of valve having handle 95 and distributor 9!! will best be understood by reference to Figs. 7 and 8. Assuming thatthe distributor 9& is in the position illustrated in Fig. 8 and the control valve is in the position illustrated in Fig. 11, fluid under pressure will be supplied from the line S to conduit I49 bythe control valve handle 95 being moved to its full line position shown in Fig. 11. Hydraulic fluid under pressure in said conduit I 69 will be divided by ports I62 and I63 of distributor 94 to conduits I62 and I63. Conduit I62 leads-to the piston rod end of left hand motor 36 as viewed in Fig. "7, and conduit I53 leads to the head end of the right hand piston motor 36. It is thus evident that pressure will be applied to the opposite ends of the two motors 36, which will tend to operate them in opposite directions.

The head end of the left hand motor 36 is con-- nected by conduit E64 to conduit I5I through port I65 of the distributor 94 and the piston rod end of right hand motor 36 is connected to conduit I-5I through conduit I66 and port I61 of distributor 94 It will thus be evident that under these conditions the two hydraulic piston motors 36 are connected in parallel, and thus the fluid delivered by conduit I49 will be divided between 1 them, whereby they will rotate the turntable :32 at a relatively slow speed, but with great power.

This is desirable where the turntable is rotated I branches of the exhaust and return line E are 3 connected to each end thereof, thus insuring against unequal pressure on the two ends of said piston I68. 7

Said piston I68 is also provided with: three ports I'll HI and I12 which are operative when the piston IE8 is rotated by handle I13 to a position,90 from that positionillustrated in Fig. 8,- to provide. direct communication between con-1 duits I49 and. 32, between conduits IE5 and IE3, and between: conduits i66-and ltl. Under these circumstances fluid under pressure supplied to the line I lcwill not be divided between the conduits I62 and I63, but will all be: directed to conduit 52 and to the piston rod endofleft hand motor The piston head end of left hand motor 35 will then be connected through conduitv ltd, port HI and conduit I63: to. the head end of righthand piston motor 36. The piston rod end or right'hand motor 36 will then be connected through conduit I66, port I10 and conduit fii to the exhaust or return line B via chamber Ml of Fig. 11. Under these circumstances the two piston motors 36, 36 will be connectedinseries and thus. will travel at. afaster rate thanwhen connected in parallel; This control isparticularly desirable when it is necessary to adjust the turntable as the machine is being transported or trammed through the min and' around curves, under which condition, of course, the cutting mechanism is not performing a kerf cutting operation and a greater speed ofoperation, requiring less power, is desired.

It'will, of course, be evident that by operatingthe handle in reverse directions, the direction of rotation of the turntable 32 may be reversed,

and by operating the distributor 94, the speedof rotation of said turntable may be determined.

In order to permit the turntable 32 to float, which may be desirable when cutting a vertical kerf while-the machine is on a curved track as aforesaid,-I provide a-valve I14 between the conduits I49 and I 5! which, when open, willof course, permit free movement of the motors 36, 36;

In addition to the hydraulic control motors previously described as part of my system, there conduit I26 leading from valveI'I'I to mechanism- I22, and conduit I35 leading from valve'll'l to mechanism I38.

Referring particularly to Figs. 9 and 10, it isto be noted that the valve Ill comprises a cas- Y ing I86 having ports NH and I8Z-therein, connected respectively to the exhaust or return line E and the-supply or pressure lines. A chamber I83- connects the ports NH and I62 through valve openings I84 and I85, respectively,

which are controlled by pistons 'I86-and' I811, respectively, which extend outside the casing I86:-

tively are further pistons I88 and' I89, respectively, which control ports E96 and I 9-I,res'pe'ctively, leading to conduits I25 and I35, respectively. The ports E96 andISI alsocommunicate with a discharge chamber I92 connected to a branch of the exhaust or return line E.- Com munication between the. ports IQUa'nd-Itl and:

the chamber I62 is. provided by openingsifimand I94, respectively, which are. cOntrQIIed by-Said" pistons. I88 and :I 89, respectively.

Rigidly attached to pistons I86 and 48-1 respec A control mechanism is provided for the contral valve I11 which permits pressure to be applied to only one of the conduits I25 or I35 at a time. To this end I provide a single operating handle I95 which is carried on a shaft I96 and which carries an elongated aperture I91.

The pistons I89, I81 carry transversely extending pins I98 and I99, respectively, adapted to slide in elongated slots 209 and ZIJI, respectively, in a bracket 292 upon which shaft I96 is journalled for free longitudinal and rotary motion. The aperture I91 of handle I95 is adapted to cooperate with the pins I98, I99 selectively upon sliding of the shaft I99 along its longitudinal axis whereby one or the other of said pistons I86, I81 may be actuated. It is to be particularly noted that the bracket 292 carries a central partition 293 which requires that the pistons I85, I81 be moved to their extreme lefthand position as viewed in Figs. 9 and 10, before the handle I95 can be shifted laterally from actuating connection with one of said pistons to actuating connection with the other. It is also evident that only one of said pistons can be actuated at one time.

With the handle I95 actuated as illustrated in Fig. 10, the piston motor controlling mechanism I22 will be operated. This will be due to the fact that pressure from the supply or pressure line S flows through port I82, chamber I83, port I99and conduit I25 to mechanism I22 to operate the brake band II4 controlled thereby. Under these conditions it will also be noted that the conduit I35 will be connected to the chamber I92 whereby the fluid in mechanism I 34 may be freely discharged to the exhaust or return line E.

If the handle I95 is operated to the dotted line position of the valve as illustrated in Fig. 9, it will be evident that fluid pressure in the chamber I83 will be cut off from the conduit I25 by the piston I83, and that said conduit I25 will be in communication with chamber I92 whereby fluid in the mechanism I22 may be freely discharged 7 to the exhaust or return line E. If then the.

handle I95 is moved laterally so that aperture I91 receives pin I99 and piston I81 is then moved to the'right as viewed in Figs. 9 and 10, pressure from the pressure line S will be communicated to the conduit I35 and to the mechanism I34 through port I9I as controlled by piston I99. It is thus obvious that the control valve I11 may operate either of the hydraulic piston motor mechanisms I22 and I34 to obtain high speed tramming or low speed feeding of the mining machine, or may leave both in a non-operating condition, but it is impossible to operate both of said mechanisms at the same time.

From the above description of the mining machine and the hydraulic control system therefor,

The electric motor 44 andthe power transmission mechanism between the same and the endless chain cutter may be relied on to drive the Furthermore, either vertical or inclined cutter chain 54 during kerf cutting feeding move ments either on the pivotal axis of the cutter bar or on the axis of the turntable, or rectilinearly parallel to the mine track forwardly and rearwardly. All such feeding movements are effected by the truck propelling motor 65 which operates not only the pump 69 but also the truck propelling mechanism as shown in Figs. 3, 4 and 5.

It will thus be seen that the feeding movements of the kerf cutter are independent of the driving of the chain kerf cutter. By reason of this independence of the operation, the speed of feed will regulate itself automatically in accordance with the hardness of the material being cut,

the feed being faster when relatively soft mate-- rial is being cut, and will be automatically slowed down when relatively hard material is encoun-v tered. When unusually hard material is encountered in the mine vein, the speed of feed may be automatically slowed down with safety because the hydraulic pressure responsive valve I42 will then act to reduce the pressure in the supply line S and in the feeding hydraulic motors. This is particularly true with respect to the hydraulic motors 6|, for effecting swinging feeding move- Rectilinear nected to the motor 65 which is operated in one direction for the forward sumping feeding movement, and in the opposite direction for the Withdrawal feeding movement. However, Whether the motor 55 is operated in one direction or the reverse, the hydraulic connections including the check valves associated with the pump as shown in Fig. '7, will enable the pump to be fully effective for maintaining full pressure to mechanisms I22 and I34 for controlling the planetary gear power transmission mechanism I2 of the truck propelling means connected to the motor 65 as shown in Fig. 1.

Quick, accurate and efiicient control of the feeding movements parallel to the mine track will thus be obtained as well as quick, accurate and emcient swinging feeding movements of the kerf cutter on the pivot of the cutter bar along the upright axis of the turntable. Such quickness, accuracy and efficiency of control also applies to the hydraulic motors 39, 39 for tilting the mining machine on the longitudinal axis I shown in Fig. l, to the motors 45, 45, 48 for tilting the kerf cutter on the transverse axes 39 and 43, and to the motor 56 for adjusting the kerf cutter transversely of its plane. 7

During transportation of the machine in the mine from one place to another, the electric motor 65 of Fig. 1 is relied on to operate the rear wheels of the truck. For such purpose the. multiple valve 94 is moved by means of the handle I13 to connect the cylinders 36, 35 in,

The operation of the pump 69 willthen cause the total volume of flow from the pump to i series.

enter the first cylinder 35, thereby eifecting relative rapid swinging movement of the cutter bar on the turntable axis. As hereinbefore explained, when the cutter bar is swung on the turntable axis for feeding movements, the cylinders 36, 38 are connected in parallel which will effect a slower but more powerful swinging movement for feeding purposes because the volume flow from the pump is divided between the two cylinders 36, 36.

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 defined 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. In a mining machine, the combination with a base frame, of a turntable mounted thereon, a supplemental frame carried by said turntable and mounted to extend forwardly of said base.

frame, traction means for supporting and propelling said base frame, a platform extending rearwardlyfrom said base frame, an electric motor mounted on said platform, hydraulic motor means to swing said turntable so said supplemental frame can avoid mine posts while traveling around curves in a mine during transportation thereof, a hydraulic system including a pump driven by said electric motor and also including connections to said hydraulic motor means, and mechanism for effecting a driving connection between said electric motor and said traction means to propel said mining machine at a transportation speed while said turntable is operable as aforesaid, said mechanism being operable by said hydraulic system.

2. In a mining machine, the combination with a base frame, of a turntable mounted thereon, a supplemental frame carried by said turntable and mounted to extend forwardly of said base frame, traction means for supporting and propelling said base frame, a platform extending rearwardly from said base frame, an electric motor mounted on said platform, hydraulic motor means to swing said turntable so said supplemental frame can avoid mine posts while traveling around curves in a mine during transportation thereof, a hydraulic system including a pump driven by said electric motor and also including connections to said hydraulic motor means, and mechanism for effecting a driving connection between said electric motor and said traction means to propel said mining machine, said mechanism being operable by said hydraulic system.

, ROBERT K. JEFFREY.

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