US2068573A - Mining machine - Google Patents

Description

Jan. 19, 1937. L. E. SIMMONS MINING MACHINE Filed May 8, 1953 3 Sheets-Sheet l Jan. 19, 1937. L. E. SIMMONS 2,068,573

MINING MACHINE Filed May 8, 1953 3 Sheets-Sheet 2 AM 1 Wmdizz Patented Jan. 19, 1937 ll 5 TAT E S T OFFICE MINING MACmNE Massachusetts Application May 8, 1933, Serial No. 669,952

22 Claims.

This invention relates to mining machines, and more particularly to improvements in the feeding means of a coal mining machine of the flexibly fed, continuous cutter, bottom cutting type.

An object of this invention is to provide an improved coal mining machine. Another object is to provide an improved mining machine feeding means. A further object is to' provide an improved feeding means for a mining machine of the flexibly fed, continuous cutter, bottom cutting type. Still another object is to provide an improved feeding means for a room and pillar type mining machine whereby the machine may be fed and guided in an improved manner. A still further object is to provide an improved mining machine feeding mechanism wherein a plurality of feed operating and controlling or haulage drums are employed and having improved variable speed driving means therefor whereby the haulage drums may be driven at any desired low speed between zero and a predetermined maximum low speed. Yet another object is to provide in a feeding mechanism of the above character an improved drum driving means wherein the haulage drums may be driven at variable low speeds and at a predetermined high speed. These and other objects and advantages of the invention will, however, hereinaf er more fully appear.

In the accompanying drawings there are shown for purposes of illustration two forms which the invention may assume in practice.

In these drawings,

Fig. 1 is a plan View of a mining machine of the room and pillar type having embodied therein the preferred illustrative form of the improved feeding means.

Fig. 2 is an enlarged plan view of the feeding means shown in Fig. l, with the cover plate removed and parts shown in horizontal section to show structural details.

Fig. 3 is a central longitudinally extending vertical sectional View taken substantially on line 33 of Figs. 1 and 2.

Fig. 4 is a cross sectional view taken substantially on line l i of Figs. 1 and 2.

Fig. 5 is a detail sectional view taken on line 5--5i of Fig. 2.

Fig. 6 is a detail sectional view taken on line 66 of Fig. 2.

Fig. 7 a detail sectional view taken on line ?-'i of Fig. 2.

Fig. 8 is a View similar to Fig. 2 showing a modified form of feeding means.

Fig. 9 is a longitudinally extending vertical sectional view taken substantially on line 99 of Fig. 8.

Fig. 10 is a cross sectional View taken on line III-l9 of Fig. 8.

Fig. 11 is a detail sectional view taken on line HH of Fig. 8.

Fig. 12 is a detail sectional View taken on line l2-l2 of Fig. 8.

Fig. 13 is a detail sectional view taken on line [3-43 of Fig. 8.

As shown in Fig. 1 of the drawings, both forms of the improved feeding means are shown embodied in a mining machine of the room and pillar, continuous cutter, bottom cutting type generally designated I, comprising a casing 2 having a plane bottom surface 3 upon which the machine is adapted to rest and slide in any direction over the mine floor. Projecting forwardly from the machine casing is a cutter bar A having mounted on its margin for circulation thereabout an endless cutter chain 5. Formed longitudinally through the bottom portion of the machine casing is a passage 6 through which the cutter chain moves, the rapidly moving outter chain clearing the cuttings from the kerf and conveying them rearwardly through the bottom of the machine to discharge at the rear end of the machine in the manner usual in mining machines of the room and pillar type. Mounted on the machine casing at the forward end thereof above the cutter bar is a motor casing I housing a motor, herein preferably of the reversible electric type, having its power shaft 8 horizontally disposed and extending longitudinally of the machine. Mounted within the feed frame 9 at the rear of the motor casing is a plurality of feed operating and controlling members, herein in the form of feeding and controlling or haulage drums Ill and II, arranged in an improved manner on parallel vertical axes within the rear portion of the machine casing and respectively cooperating with feed operating and controlling elements, herein ropes or cables [2 and I3. Arranged at the opposite front corners of the machine casing are swing arms I4, l4 carrying usual guide sheaves I5, l5 for guiding the feed cable laterally from the opposite front corners of the machine during cutting in opposite directions. As shown in Fig. 1, the feeding and controlling cables are arranged to efiect feed of the machine from right to left. When it is desired to effect cutting in the opposite direction, the feeding and controlling cables are arranged in the opposite manner, the cutter bits turned in their respective links of the cutter chain and the driving motor reversed. As the room and pillar type of machine disclosed herein is generally of a standard design, and as the improved feeding means may be embodied in mining machines of various other types, further description thereof is deemed unnecessary.

Now referring to the preferred form of the improved feeding means and more particularly to the improved driving means for the feed operating and controlling drums, it will be noted that the power shaft 8 of the motor extends longitudinally of and is suitably journaled within the feed frame 9 and has keyed thereto at its rear end a spur pinion ll meshing with a spur gear l8 keyed, to the rear end of a longitudinally extending shaft l9 herein arranged parallel with and below the motor shaft 8 and likewise suitably journaled within the feed frame 9. Keyed to the forward end of the shaft I 9 is a bevel pinion 20 meshing with a bevel gear 2! having its hub keyed at 22 to a vertical shaft 23. The shaft 23 is journaled within bearing sleeves 24, 24 supported within the machine casing. Journaled on a bearing sleeve 25 supported on the hub of the bevel gear 2i is a chain sprocket 25 and this sprocket is connectible to the gear 2| for driving thereby by means of a pin clutch 27 operated by a shipper member 28 having a suitable controlling handle 29. The chain sprocket 23 engages and drives the cutter chain 5 in the usual manner. Formed on the upper end of the vertical shaft 23 is a bevel pinion 30 meshing with a bevel gear 3! journaled on a bearing sleeve 32 supported by a tubular shaft 33 rotatably mounted on the shaft 8. Keyed to the shaft l9 adjacent the gear 58 is a spur pinion 34 meshing with a spur gear 35 journaled on a tubular shaft 36 in turn rotatably mounted on the shaft 8. The gears 3i and 35 herein respectively constitute low and high speed terminal driving gears, and are connectible to the tubular shafts 33 and 36, by multiple disc clutches 3i and 38, respectively. The improved operating means for these clutches will later be described.

In this instance the shafts 33 and 36 are clutched at their inner ends to the opposite hubs of a worm 39 rotatably mounted on the shaft 8 and meshing, at its opposite sides, with worm wheels 40 and 4!. These worm wheels are suitably rotatably mounted on vertical shafts 32 and 43, respectively, herein arranged equidistantly from the longitudinal vertical center of the machine and. suitably journaled within the feed frame 9, as shown in Fig. 4. These worm wheels are connectible to the Vertical shafts 42 and 43 by multiple disc clutches 46 and 45, respectively, each having suitable operating means including a pressure plate 46 engaged by a shipper yoke 41 keyed to a longitudinally extending operating shaft 48. Secured to the outer ends of these shafts are suitable operating handles 49 and 50, respectively, whereby the clutches may be independently controlled. Keyed to the lower ends of these vertical shafts are the feed operating and controlling drums l0 and H herein arranged within horizontal chambers 5| and 52 formed in the feed frame directly above the cutter chain passage 6, these chambers opening outwardly through the sides of the feed frame to enable the feeding and controlling cables to be extended in various directions from their respective drums.

Now referring to the improved operating means for the speed controlling clutches 3i and 38, and more particularly to the improved operating means for the clutch 31 controlling the low speed terminal gear 3!, it will be noted that formed on the bevel gear 3! is a sleeve portion 53, in turn having formed on its rearward edge a cam surface 54 which is adapted to cooperate with a longitudinally reciprocable pin or plunger 55 slidably guided in a bore 56 in a bearing member 57. At its rearward end the pin 55 is pivotally connected at 58 with one end of a lever 58 whose opposite end. is pivotally connected at $9 to a threaded member 6! which receives the forward end of a threaded rod 32. The forward portion of this rod is provided with an enlargement 83 forming a shoulder 34, and a spring 65 is compressed between a nut 63 cooperating with the threaded rearward end of the rod 62 and a collar 6i slidably mounted on the rearward reduced end of the rod 62 and normally engaging the shoulder 34. The enlarged forward end 63 of the rod 82 passes through a trunnion device tit supported by a shipper member 69 pivotally mounted at it? within a support element H carried within the feed frame. This lever 69 carries between the trunnion device 68 and the lever pivot l'fl clutch applying elements l2, 72 which engage the rearward end surface of a clutch applying sleeve 73 slidably mounted on the tubular shaft 33, as shown in Fig. 3. It will be evident from the foregoing description that movement to the left of the rod 62 in Fig. 2 will result in the transmission of no pressure to the clutch shipper sleeve l3 until the sliding collar El engages the end of the trunnion device 68; but that further movement to the left, in this figure, of the rod 62 will thereafter impart a load to the shipper sleeve 13 which will be determined by the extent of the movement of the rod and the degree of compression of the spring 65. A movable fulcrum for the lever 5G is provided by an adjustable rod Hi pivotally connected at its forward end at 15 to the lever 59 between its pivotal connections 58 and 68, as shown in Fig. 2. This rod is guided within bearing members 16 and 77 within the feed frame and has threadedly connected at its rearward end a nut member 18 for an operating handle 79. This nut member is held against axial displacement by means of a groove 80 thereon engaged by a flange 88 on the feed frame. The rod 14 also carries a collar 82 engageable with a lever arm of a pivoted shipper member 83 for operating the pressure plate 84 of the high speed clutch 38. Rotation of the nut member '53 in a direction to effect movement of the rod M toward the left in Fig. 2 moves the fulcrum T5 of the lever 59 toward the left, and thereby moves the pin 55 into engagement with the cam surface 5 and upon movement of the fulcrum sufficiently far to the left the other end of the lever 59 will have suificient throw so that the shoulder 6 5 will pass inside the trunnion device 68 and permit the collar 61 to contact with the trunnion device and the spring 65 to load the low speed friction clutch 31. Obviously, when the spring 35 is under sufficient compression so that it will yield only when a pressure adequate to effect power transmission through the discs of the friction clutch 3'! is applied to the collar 67, the adjustment of the lever fulcrum will effect rotation of the worm 39 at a low speed by the bevel gear 3| for any desired part of each revolution of the latter. When the rod 14 is moved to the left so far that the collar 6'! continuously presses under the pressure of the spring against the trunnion device 68, continuous rota- 75 tion of the worm 39 will take place, the spring 65 will compress during each rotation of the bevel gear 3! an amount substantially equal to the full throw of the cam 54; but since the load of the spring is desirably above the minimum necessary to effect power transmission through the friction clutch discs, there will be no release even when the lowest point in the cam 54 is opposite the pin 55. However, by moving the fulcrum rod l9 graduated amounts toward the right in Fig. 2, the period of drive during each rotation of the bevel gears 3i may be progressively reduced until it is entirely discontinued. When the fulcrum rod M is moved a sufficient distance toward the right in Fig. 2, the low speed clutch 9? is entirely released, and upon engagement of the collar 82 on the rod with the lever arm of the clutch shipper 83 the latter may be swung rearwardly to effect application of the high speed clutch 3B, and as a result the worm 39 is driven at a continuous high speed. It is thereforeevident that by suitable adjustment of the fulcrum rod Hi the worm 39 may be driven at a continuous high speed, at a continuous low speed and intermittently driven at a number of different still lower mean speeds. As a result, the feed operating and controlling drums I0 and II may be separately or simultaneously driven in a direction to wind in their respective cables and under the control of the disc clutches 44 and 55 at variable low speeds between zero and a predetermined maximum low speed and at a relatively high predetermined speed.

In the form of the invention shown in Figs. 8 to 13, inclusive, there is shown keyed to the rear end of the motor power shaft 8, as shown in Fig. 9, a spur pinion 85 meshing with a spur gear 86 keyed to a longitudinally extending shaft 87 herein arranged parallel with and below the motor power shaft and suitably journaled Within the machine frame. Keyed to and driven by the shaft 81 is a bevel gear 88 meshing with a bevel gear 89 keyed to a vertical shaft 90 suitably journaled within the machine frame. Also keyed to the shaft 99 and driven thereby is a spur gear 9I meshing with a spur gear 92 having its hub keyed at 93 to a vertical shaft 94 likewise suitably journaled within the machine frame. J ournaled on the hub of the gear 92 by a bearing sleeve 95 is a chain sprocket 96 which engages and drives the cutter chain 5. The gear 92 is connectible to the chain sprocket 96 by a pin clutch 9'! similar to the clutch 21 heretofore described and having similar operating means. Keyed to the upper end of the shaft 94 is a bevel gear 98 meshing with a bevel gear 99, herein the high speed terminal gear. The hub of the gear 99 is keyed to the rear end of a longitudinally extending shaft I09 herein arranged with its axis parallel with and above the motor shaft axis and likewise suitably journaled within the machine frame. Keyed to the forward end of the shaft I 90 is a spur pinion Ilil meshing with a spur gear I92. keyed to a longitudinally extending shaft I93 suitably journaled within the feed frame 9. Keyed to the shaft I03 and driven thereby is a spur pinion I94 meshing with a spur gear I95, herein the low speed terminal gear, suitably rotatably mounted on the shaft I99. A so r0- tatably mounted on the shaft I99 is a tubular shaft I96, and the gears 99 and I95 constituting the high and low speed driving elements, respec tively, are connectible to this tubular shaft by multiple disc clutches I9! and I08. The operating means for these clutches will later be described. Formed on the shaft I96 is a worm I99 meshing at its opposite sides with worm wheels III] and III which are mounted and arranged to drive the feed operating and controlling drums in a manner disclosed in the preferred form of the invention, and as shown in Fig. 4. The manner of mounting the worm wheels and the controlling means for connecting the drums to their respective worm wheels are shown in Fig. 10, and, as above mentioned, as this drum driving structure is similar to that disclosed in the preferred form of the invention, further description thereof is thought unnecessary.

Now referring to the improved operating means for the high and low speed clutches I97, I98, respectively, and particularly to the improved operating means for the low speed clutch, it will be noted that formed on the forward face of the spur gear I05 is a cam H5 with which is adapted to engage a longitudinally reciprocable plunger or pin I I8 guided in a bore i ll formed in a bearing member H8. The forward end of this pluner is pivotally connected at I I9 with one end of a lever I20 whose opposite end is pivotally connected at I22 to a threaded member I23 which receives the forward and of a threaded rod I24. The rearward end of the rod is provided with an enlargement I25 forming a shoulder I26, and a spring 52'! is compressed between a nut I28 threaded on the rod and a collar I29 slidably mounted upon the rod and normally engaging the shoulder I26. The enlarged rearward end of the rod I24 passes through a trunnion device I39- supported by a shipper member I9I pivotally mounted at I32 within the machine frame. This shipper member carries at its opposite side from its pivots, clutch applying elements I33, I33 which engage a ball bearing shipper m r h lilt'. slidably mounted on the tubular shaft I96. It will be evident from the foregoing description that movement to the right of the rod I24 in Fig. 8 will result in the transmission of no pressure to the clutch shipper member I39 until the sliding collar I29 engages the end of the trunnion device I38; but that further movement to the right, in this figure, of the rod I24 will thereafter impart a load to the shipper member I34 which will be determined by the extent of the movement of the rod and the degree of compression of the spring I2'I. A movable fulcrum for the lever I20 is provided by a trunnion device I35 wh ch is held upon a longitudinally movable rod I36 between a shoulder I31 on the latter and a collar I38 pinned to the rod. The rearward end of the longitudinally movable rod I 35 s threadedly engaged at I39 within a boss I49 formed on the rear end wall of the feed frame. Fixed to the rear end of the screw threaded rod is an operat ing handle MI for rotating the screw to effect axial movement of the rod. Also fixed to the rod I36 is a collar I92 engageable with a trunnion device I43 surrounding the rod and pivotally mounted in the outer end of a shipper member I44. This shipper member is pivotally mounted at I 45 on the feed frame and carries clutch apply n elements 53 e11" '="able wih a ball hearing clutch applying member I4! mounted on the tubular shaft I06, for applying the high speed clutch I91. Through the means above described, rotation of the worm H19 may be effected at a continuous high speed or a continuous low speed, and intermittent rztation at a number of diiferent still slower mean speeds. Rotation of the handle MI in a direction to cause movement of the rod I36 toward the left in Fig. 8 results in loading of the high speed friction controlling clutch I91 and driving of the worm IIJQdirectly by the high speed terminal gear 99. Rotation of the handle Ii in a direction to efiect movement of the rod toward the right in Fig. 8 moves the fulcrum I35 of the lever I20 toward the right and thereby moves the pin I I6 into engagement with the cam I I5; and upon movement of the fulcrum sufficiently far to the right, the other end of the lever I29 will have sufiicient throw so that the shoulder I26 will pass inside the trunnion device I30 and permit the collar I29 to contact with the trunnion device and the spring I21 to 1oad the low speed friction controlling clutch I98. Obviously, when the spring I21 is under suficient compression so that it will yield only when a pressure adequate to effect power transmission through the discs of the friction clutch EH8 is applied to the trunnion I36, the adjustment of the fulcrum device I35 may effect rotation of the worm I09 at a low speed by the low speed terminal gear I95 for any desired part of each revolution of the latter. When the rod I36 is moved to the right so far that the collar I29 continuously presses, under the pressure of the spring, against the fulcrum device I25, continuous rotation of the worm IE9 will take place and the spring I2? will compress dur ng each rotation of the gear Hi5 an. amount substantially equal to the full throw of the cam H5; but since the load of the spring is desirably above the minimum necessary to effect power transmission through the friction clutch discs, there will be no release, even when the lowest point in the cam H5 is opposite the pin H6. However, by moving the rod I 36 graduated amounts toward the left in Fig. 8, the period of drive during each rotation of the gear I 95 may be progressively reduced until it is entirely discontinued. It will thus be evident that the feed operating and controlling drums I 0 and II may be driven in a direction to draw in their respective cables separately or simultaneously at variable low speeds and at a predetermined high speed under the control of the drum controlling clutches.

From the foregoing description the mode of operation of both forms of the improved feeding mechanism will be clearly apparent, and as the use of a room and pillar coal mining machine of the type disclosed is Well understood by those skilled in the art, a detail description of the general mode of operation of the machine is thought to be unnecessary. It will be noted, however, that the machine may be fed over the mine floor at a relatively high haulage speed by either drum under the control of the high speed friction. The machine may also be fed at any desired low speed from its maximum low speed down to zero by proper adjustment of the fulcrum. Overloading will be prevented in the illustrative embodiments shown in the drawings by the presence of the spring 65 in the preferred form and the spring I21 in the modification. The machine may be suinped in and fed transversely across the coal face in accordance with the room and pillar system of cutting, by means of the feed drum and under the control of the controlling drum.

As a result of this invention, it will be noted that an improved mining machine feeding mechanism is provided which is of a rugged and compact character and which is particularly adapted to use in coal mining machines of the room and pillar type wherein at times substantial variat ons the feeding speed are importance. It will further be noted that by arranging the fast and slow speed drive trains and arranging the drum controlling clutches in the manner disclosed, a very convenient and simple operating mechanism for all of the clutches used in the control of the feed of the machine is made possible. It will further be noted that a continuous low feed and an intermittent low feed are both available by the same mechanism, permitting a wide variation in the feeding speeds attained, thereby to suit different cutting conditions. Further advantages will be apparent to those skilled in the art.

While there are in this application specifically described two forms which the invention may assume in practice, it will be understood that these forms of the same are shown for purposes of illustration and that the invention may be modified and embodied in various other forms without departing from its spirit or the scope of the appended claims.

What I claim as new and desire to secure by Letters Patent is:

1. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, motor operated gearing for driving said element, and feeding means for the machine including a low speed gear train and a high speed gear train, said high and low speed gear trains driven through said gearing, said low speed gear train including a driving element coaxial with said kerf cutter driving element, and said low speed gear train including a friction clutch, and means driven by an element of said low speed gearing as distinct from said high speed gearing for intermittently applying and releasing said clutch at timed intervals.

2. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, motor operated gearing for driving said element, and feeding means for the machine including a low speed gear train and a high speed gear train, the drive for the low and high speed gear trains including a driving element coaxial with said kerf cutter driving element, and said low speed gear train including a friction clutch, and means driven by an element of said low speed gearing as distinct from said high speed gearing for intermittently applying and releasing said clutch at timed intervals.

3. In a mining machine, kerf cutting mechanism, motor operated driving means for said kerf cutting mechanism including a cutter drive element disposed on a vertical axis, and feeding means for the mechanism including high and low speed gear trains, said low speed gear train driven through said cutter drive element, a horizontal shaft driven through said low speed gear train, said low speed gear train including a friction clutch coaxial with said horizontal shaft, and means driven through said vertical drive element for intermittently applying and releasing said clutch at timed intervals.

4. In a mining machine, kerf cutting mechanism, motor operated driving means for said kerf cutting mechanism including a cutter drive element disposed on a vertical axis, and feeding means for the machine including high and low speed gear trains driven through said vertical drive element, a horizontal shaft driven through said low speed gear train, said low speed gear train including a clutch coaxial with said horizontal shaft, and means driven through said vertical drive element for intermittently applying and releasing said clutch at timed intervals.

5. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, a motor driven shaft for driving said cutter driving element, and feeding means for the machine including high and low speed gear trains driven by said motor driven shaft, said low speed gear train including a driving element coaxial with said kerf cutter driving element, a horizontal shaft driven through said low speed gear train, said high and low speed gear trains including elements coaxial with said horizontal shaft, said low speed gear train including a friction clutch coaxial with said horizontal shaft, and means driven by power from said motor driven shaft for intermittently applying and releasing said clutch at timed intervals.

6. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, a motor driven shaft for driving said cutter driving element, and feeding means for the machine including high and low speed gear trains driven by said motor driven shaft and including a driving element coaxial with said kerf cutter driving element, a horizontal shaft driven by said low speed gear train, said high and low speed gear trains including elements coaxial with said horizontal shaft, said low speed gear train including a friction clutch coaxial with said horizontal shaft, and means driven by power from said motor driven shaft for intermittently applying and releasing said clutch at timed intervals.

7. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, a motor driven shaft for driving said cutter driving element, and feeding means for the machine including high and low speed gear trains driven by said motor driven shaft, said low speed gear train including a driving element coaxial with said cutter driving element, a horizontal shaft driven by said low speed gear train, said high and low speed gear trains including elements coaxial with said horizontal shaft, said low speed gear train including a friction clutch coaxial with said horizontal shaft, and means driven by one of said elements coaxial with said horizontal shaft for intermittently applying and releasing said clutch at timed intervals.

8. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, a motor driven shaft for driving said cutter driving element, and feeding means for the machine including high and low speed gear trains driven by said motor driven shaft, said high and low speed gear trains including a driving element coaxial with said cutter driving element, a horizontal shaft driven by said low speed gear train, said high and low speed gear trains including elements coaxial with said horizontal shaft, said low speed gear train including a friction clutch coaxial with said horizontal shaft, and means driven by one of said elements coaxial with said horizontal shaft for intermittently applying and releasing said clutch at timed intervals.

9. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, a motor driven shaft for driving said cutter driving element, and feeding means for the machine including a low speed gear train driven by said motor driven shaft and including a driving element coaxial with said outter driving element, said low speed gear train including a friction clutch disposed on a horizontal axis, and means driven by said motor driven shaft for intermittently applying and releasing said clutch at timed intervals.

10. In a mining machine, kerf cutting mechanism including a kerf cutter driving element disposed on a vertical axis, a motor driven shaft for driving said cutter driving element, and feeding means for the machine including a low speed gear train driven by an element coaxial with said outter driving element, a horizontal shaft driven by said low speed gear train, said low speed gear train including a friction clutch coaxial with said horizontal shaft, and means driven by said motor driven shaft for intermittently applying and releasing saicl clutch at timed intervals.

11. In a mining machine, kerf cutting mechanism including a kerf cutter driving element, motor operated driving means for said kerf cutting mechanism including a shaft extending longitudinally of the machine and operatively connected to said kerf cutter driving element to drive the latter, and feeding means for the machine including a shaft arranged coaxially with said longitudinal shaft, a low speed gear train driven by said longitudinal shaft including a gear coaxial and rotatable with said kerf cutter driving element, a low speed clutch for connecting said shafts in driving relation through said gear train,

and mechanism operated by an element of said low speed gear train for intermittently applying and releasing said clutch at timed intervals.

12. In a mining machine, kerf cutting mechanism including a kerf cutter driving element, motor operated driving means for said kerf cutting mechanism including a shaft extending longitudinally of the machine and operatively connected to said kerf cutter driving element to drive the latter, and feeding means for the machine including a shaft arranged coaxially with said longitudinal shaft, a low speed gear train driven by said longitudinal shaft including a gear coaxial and rotatable with said kerf cutter driving element, a low speed clutch for connecting said shafts in driving relation through said gear train, mechanism operated by an element of said low speed gear train for intermittently applying and releasing said clutch at timed intervals, and a high speed gear train driven through said shaft extending longitudinally of the machine and operatively connected to said kerf cutter driving element.

13. In a mining machine, kerf cutting mechanism including a kerf cutter driving element, motor operated driving means for said kerf cutting mechanism including a shaft extending longitudinally of the machine and operatively connected to said kerf cutter driving element to drive the latter, and feeding means for the machine including a shaft arranged coaxially with said longitudinal shaft, a low speed gear train driven by said longitudinal shaft including a gear coaxial and rotatable with said kerf cutter driving element, a low speed clutch for connecting said shafts in driving relation through said gear train, mechanism operated by an element of said low speed gear train for intermittently applying and releasing said clutch at timed intervals, and a high speed gear train driven through said shaft extending longitudinally of the machine and operatively connected to said kerf cutter driving element and including a high speed gear coaxial with said longitudinal shaft.

14. In a mining machine, kerf cutting mechanism including a kerf cutter driving sprocket, motor operated driving means for said sprocket including a gear coaxial and rotatable with said sprocket, and feeding means for the machine including a high speed gear train and a low speed gear train, said gear trains respectively including high and low speed terminal gears arranged on axes extending longitudinally of the machine and said low speed gear train driven by said coaxial sprocket driving gear, a clutch controlling the drive by said low speed terminal gear, and means actuated by an element of said low speed gear train for automatically applying and releasing said clutch at timed intervals.

15. In a mining machine, kerf cutting mechanism including a kerf cutter driving sprocket, motor operated driving means for said sprocket including a gear coaxial and rotatable with said sprocket, and feeding means for the machine including a high speed gear train and a low speed gear train, said gears trains respectively including high and low speed terminal gears arranged on axes extending longitudinally of the machine and both gear trains driven by said coaxial sprocket driving gear. I

16. In a mining machine, kerf cutting mechanism including a kerf cutter driving sprocket, motor operated driving means for said sprocket including a gear coaxial with said sprocket, and feeding means for the machine including a low speed gear train, said gear train including a bevel gear coaxial with said sprocket driving gear and driven thereby, a bevel gear meshing with and driven by said coaxial bevel gear, a horizontal shaft arranged coaxially with and driven by said last mentioned bevel gear, a clutch for connecting said last mentioned bevel gear to said shaft, and

means actuated by an element of said low speed gear train for automatically applying and releasing said clutch at timed intervals.

17. In a mining machine, kerf cutting mechanism including a kerf cutter driving sprocket, motor operated driving means for said sprocket including a gear coaxial with said sprocket, and

feeding means for the machine including a high speed gear train and a low speed gear train, said low speed gear train including a bevel gear coaxial with said sprocket driving gear and driven thereby, a bevel gear meshing with and driven by said coaxial bevel gear, and a horizontal shaft arranged coaxially with and driven by said last mentioned bevel gear and saidlow speed gear train including a clutch for connecting said last mentioned bevel gear to said shaft, and means actuated by an element of said low speed gear train for automatically applying and releasing said clutch at timed intervals, said gear trains driving said horizontal shaft selectively at continuous high and intermittent low speeds.

18. In a mining machine, kerf cutting mechanism including a kerf cutter driving element, motor operated driving means for said kerf cutting mechanism including a shaft extending longitudinally of the machine, a parallel shaft operatively connected to said kerf cutter driving element and gearing connecting said shafts in driving relation, and feeding means for the machine including a driven shaft coaxial with and rotatable relative to said first mentioned longitudinal shaft, a low speed gear train including a gear coaxial and rotatable with said kerf cutter driving element, and a low speed terminal driving gear coaxial with said coaxial driven shaft, a clutch for connecting said low speed terminal gear to said coaxial driven shaft, and means actuated by said low speed terminal gear for intermittently applying and releasing said clutch at timed intervals.

19. In a mining machine, kerf cutting mechanism including a kerf cutter driving element, motor operated driving means for said kerf cutting mechanism including a shaft extending longitudinally of the machine, a parallel shaft operatively connected to said kerf cutter driving element and gearing connecting said shafts in driving relation, and feeding means for the machine including a driven shaft coaxial with and rotatable relative to said first mentioned longi-,

tudinal shaft, a low speed gear train including a gear coaxial and rotatable with said kerf cutter driving element and a low speed terminal driving gear coaxial with said coaxial driven shaft, a clutch for connecting said low speed terminal gear to said coaxial driven shaft, means actuated by said low speed terminal gear for intermittently applying and releasing said clutch at timed intervals, and a high speed gear train including a gear coaxial with and driven by said parallel shaft and a high speed terminal gear coaxial with said coaxial driven shaft, and a clutch for connecting said high speed terminal gear to said coaxial driven shaft.

20. In a mining machine, kerf cutting mechanism including a kerf cutter driving element, motor operated driving means for said kerf cutting mechanism including a gear coaxial with said kerf cutter driving element for driving the latter, and feeding means for the machine including a horizontal driven shaft extending longitudinally of the machine, a high speed gear train including a gear coaxial with and driven by said cutter driving element driving gear and a high speed terminal gear coaxial with said shaft, a clutch for connecting said high speed terminal gear to said shaft, a low speed gear train driven by said gear coaxial with said cutter driving element driving gear including a shaft coaxial with said longitudinal shaft, a low speed terminal gear coaxial with and driven by said coaxial shaft, a clutch for connecting said low speed terminal gear to said longitudinal driven shaft, and means actuated by an element of the low speed gear train for intermittently applying and releasing said low speed clutch at timed intervals.

21. In a mining machine, kerf cutting mechanism including a kerf cutter driving sprocket, motor operated driving means for said sprocket including a gear coaxial and rotatable with said sprocket, and feeding means for the machine including a high speed gear train and a low speed gear train, said low speed gear train driven by said coaxial sprocket driving gear and said gear trains including high and low speed clutches arranged in coaxial relation on horizontal axes, and means driven through said coaxial sprocket driving gear forintermittently applying and releasing said low speed clutch at timed intervals.

22. In a mining machine, kerf cutting mecha-- nism including a kerf cutter driving sprocket, motor operated driving means for said sprocket including a gear coaxial and rotatable with said sprocket, and feeding means for the machine including a high speed gear train and a low speed gear train, said gear trains both driven by said coaxial sprocket driving gear and including high and low speed clutches arranged in coaxial relation on horizontal axes, and means driven by said coaxial sprocket driving gear for intermittently applying and releasing said low speed clutch at timed intervals.

LEON E. SIMMONS.

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