US2322481A - Loading device - Google Patents

Description

June 22, 1943. w, w, SLOANE 2,322,481

LOADING DEVICE Filed Feb. 26, 1942 12 Sheets-Sheet 1 INVENTOR.

Wm M 510a) BY W 814K June 22, 1943. w, w, sLo N 2,322,481

LOADING DEVICE Filed Feb. 26, 1942 12 Sheets-Sheet 2 ATTORNEY Ju ne 22, 1943. w. w. SLOANE 2,322,481

LOADING DEVICE Filed Feb. 26, 1942 12 Sheets-Sheet 3 INVENTOR,

Ma -4 5 K ATI'ORNCY June 22, 1943. w. w. SLOANE 2,322,481

LOADING DEVICE Filed Feb. 26, 1942 l2 Sheets-Sheet 4 INVENTOR.

ATTORNEY June 22,1943. 2 w. w. SLOANE 2,322,481

LOADING DEVICE Filed Feb. 26, 1942 12 Sheets-Sheet 6 A'I'TO R N BY June 22, 1943. w. w. SLOANE 2,322,431

' LOADING DEVICE Filed Feb, 26, 1942 12 Sheets-Sheet 7 90 g as INVENTOR. 9 Wi/liarn W 510m a v g ATTQ;

w. w. SLOANE 2,322,481

LOADING DEVICE '12 Sheets-Sheet s June 22, 1943.

Filed Feb. 26, 1942 June 22, 1943. w, w, SLOANE I 2,322,481 I LOADING DEVICE Filed Feb. 26, 1942 12 Sheets-Sheet 9 1&7

ZOO

IN VEN TOR.

Wig (2am W 5/00/7142 MV.M

A TTORNEY June 22; 1943. w. w. SLOANE LOADING DEVICE Filed Feb. 26, 1942 12 Sheets-Sheet 10 A -\L-\ '25 L 47 ATTORNEY Julie 22, 1943. w. w. SLOANE 2,322,481

LOADING DEVICE Filed Feb. 26, 1942 12 Sheets-Sheet 12 IN V EN TOR.

A TTOENEY Patented June 22, 1943 LOADING DEVICE William W. Sloane, Chicago, 111., assignor to Goodman Manufacturing Company, Chicago, 111., a corporation of Illinois Application February 26, 1942, Serial No. 432,436

(Cl. l98-14) 27 Claims.

This invention relates to improvements in loading devices and more particularly relates to a loading device adapted to pick up and load material onto the inby end of a shaker conveyor.

The principal objects of my invention are to provide a new and improved loading device of the class described, particularly adapted for use in mines underground and arranged with a view towards compactness, especially in vertical height and length, and towards ease and efiiciency in operation and control.

A further object of my invention is to provide a new and improved loading device consisting of a reciprocating trough section having a shovel on its forward end, for picking up loose material from'the ground and loading it onto the inby end of a shaker conveyer through line and having a novel form of reciprocably driven propelling device driven in timed relation with respect to the reciprocating trough section, for positively feeding the shovel into the material it is desired to load and aiding and'accelerating the gathering action of said shovel.

A more specific object of my invention is to provide a novel form of feeding and propelling means for a shaker conveyor loading device which consists in a propelling weight reciprocably driven along the base of the loading device in timed relation with a reciprocating pick-up member of the loading device, together with means for reciprocably driving the propelling weight in various directions in a plane substantially parallel with. the ground, and for controlling reciprocation of said propelling weight and the point at which it exerts its greatest propelling force, to cause said propelling weight to move the loading device along the ground in various desired directions.

A still further object of my invention is to provide a reciprocably driven weight for transmitting a propelling force to a stationary object, together with a novel form of drive and control means for the propelling weight arranged to control the direction of reciprocable movement of the weight and vary the points at which its greatest propelling force occurs, to change and reverse the direction of the propelling force transmitted by said weight.

Other objects of my invention will appear from time to time as the following specification proceeds and with reference to the accompanying drawings wherein:

Figure l is a diagrammatic plan view of a section of a mine, showing a loading device constructed in accordance with my invention in peel-- tion to pick up material from a breakthrough which is being cut to connect two adjoining rooms of the mine;

Figure 2 is an enlarged plan view of the loading device shown in Figure 1;

Figure 3 is an enlarged fragmentary plan view of the loading device shown in Figure 1, with parts of the reciprocating trough section broken away and other parts removed and shown in horizontal section, in order to more clearly illustrate certain details of my invention;

Figure 4 is an enlarged fragmentary longitudinal sectional view taken substantially along line 44 of Figure 2; t

Figure 5 is an enlarged view in side elevation of the forward end of the loading device, with certain parts broken away and certain other parts shown in longitudinal section in order to show certain details of the support and drive means for the reciprocating trough section and shovel;

Figure 6 is a view somewhat similar to Figure 5, with the reciprocating trough and shovel shown at the opposite end of the stroke than in Figure 5;

Figure 7 is an enlarged fragmentary transverse sectional view taken substantially along line 1-1 of Figure 3;

Figure 8 is an enlarged detail view showing certain details of the support and drive connection for the means for counteracting the reciprocating action of the reciprocating trough section and shovel;

Figure 9 is an enlarged partial fragmentary sectional view taken substantially along line 5-9 of Figure 6;

Figure 10 is a detail view in side elevation, showing certain details of the supporting means for the reciprocating trough section;

Figure 11 is an enlarged detail view in side elevation showing certain details of the support for the means for counteracting the reciprocating movement of the reciprocating trough section and shovel;

Figure 12 is a detail fragmentary sectional view taken substantially along line l2-I2 of Figure 11, and showing certain details of the guiding means for the reciprocating trough section;

Figure 13 is an enlarged fragmentary detail sectional view taken through the reciprocating trough section and showing certain details of the support for the means for counteracting the reciprocating action of said reciprocating trough section;

Figure 14 is a transverse sectional view taken substantially along line I-i-M of Figure 3;

Figure 15 is a transverse sectional view taken substantially along line I5i5 of Figure 3;

Figure 16 is an enlarged fragmentary detail sectional view taken substantially along line Iii-I6 of Figure 3;

Figure 17 is an enlarged longitudinal sectional view taken substantially along line I*II'I of Figure 3;

Figure 18 is an enlarged fragmentary sectional view taken substantially along line IB-IB of Figure 3;

Figure 19 is an enlarged detail partial fragmentary longitudinal sectional view, showing certain details of the positioning means for the links which reciprocably move the weight along the base of the loading device;

Figure 20 is an enlarged detail view, showing certain details of the connection of the stroke control means to the propelling weight;

Figure 21 is an enlarged fragmentary sectional View taken substantially along line 2 I2I of Figure 17;

Figure 22 is a diagrammatic View showing certain details of the remote electrical control and the fluid control, for controlling the operative positions of the drive links for the propelling weight;

Figure 23 is a partial fragmentary transverse sectional View taken through the valve-manifold illustrated in Figure 22; v

Figure 24 is a sectional view taken substantially along line 2424 of Figure 23; and

Figures '25, 26, 27, 28, 29 and 30 are diagrammatic views illustrating certain positions of the linkage connections to the propelling weight, for causing the propelling weight to move in the proper directions and phase relationship to propel the loading device in various desired tions along the ground.

Referring now in particular to the embodiment of my invention illustrated in the drawings, a loading device indicated generally by reference character 9 is shown in Figure 1 as being in position for loading from a breakthrough connecting two parallel working places or rooms of the mine. An extensible and swiveled trough section I I.) may be pivotally connected to the rear end of the loading device,,for receiving material discharged from the rear end of a reciprocating trough section Ii of the loading device and for transferring it to the inby end of a shaker conveyer trough line generally indicated by reference character I2.

The extensible and swiveled trough section It is so arranged as to be automatically extended as the loading device movestowards and from the trough line and is not herein shown or described in detail since it is no part of my present invention and is clearly illustrated and described in a companion application Serial No. 432,786, filed by J H. Holstein on February 28, 1942.

The shaker conveyer trough line may be of a usual construction, driven from suitable conveyer drive mechanism (not shown). Said drive mechanism is preferably located in the mine entry adjacent the room neck, in cases where the conveyer is extended into a mine room, and is arranged to reciprocably drive the conveyer trough line in such a manner as to move material away from the working face of the room, to the entry.

The loading device 9 includes enerally a base frame I3 mounted for slidable movement along the ground on its bottom and having a weighted direc- Cir propelling member I5 extending generally longitudinally thereof and slidably mounted thereon for reciprocable movement with respect thereto in various desired directions and at various intensities, for moving said base frame along the ground and for feeding a shovel I6 on the forward end of the reciprocating trough section II into the material it is desired to load.

A motor I I is provided for driving said reciprocating trough section and for reciprocably moving said propelling weight along said base. Said motor extends along one side of said base and, as herein shown, is mounted on a cover portion I8 of said base which is spaced upwardly from the bottom thereof.

With reference now to the mounting of the reciprocating trough section II on th base I3, a pair of laterally spaced upright supports I9, [9a project upwardly from the cover portion I8 of said base and are positioned adjacent the rear end of said base, to form pivotal mountings at their upper end for the rear ends of side frame members 2! 29. Said side frame members have said reciprocating trough section guided thereon, for reciprocable movement with respect thereto, and extend longitudinally forwardly from said supports beyond the forward end of said base, in parallel relation with respect to each other (see Figures 4, 5, 6 and 14) The side frame members 20, 20 are adjustably supported adjacent the forward end of said base on the upper ends of piston rods 15, I5 slidable in fluid cylinders 13, 13 and extending upwardly from pistons I6, 76, in said cylinders (see Figures 4 and 7). Each of said fluid cylinders is mounted on a transverse pivotal pin 14, extending through a depending portion 'II of said cylinder and through a pair of parallel spaced lugs I2, 72, pro jecting upwardly from said base and extending along opposite sides of said depending portion. The upper ends of said piston rods are transversely pivoted to brackets 11, I1 projecting laterally outwardly from said side frame members 20, 23. Fluid under pressure is admitted to the head end of said cylinders, to elevate said side frame members and the trough section II and shovel I6 about the axes of connection of said side frame members to the brackets I 9, I911 by means of suitable fiuid control valves and piping connections in a manner which will hereinafter be more clearly described as this specification proceeds.

Each side frame member 29, as herein shown, is provided with a pair of parallel longitudinally spaced inclined guide members 2 I, 2Ia, extending angularly forwardly and downwardly therefrom and disposed adjacent the rear end thereof, and with another pair of similar parallel longitudinally spaced guide members 22, 22a disposed adjacent the forward end of said side frame member.

The guide member 2I and the guide member 22a of each side frame member 20 form guide tracks for the reciprocating trough section I I, to guide said trough section to reciprocably move in a forwardly and downwardly inclined direction upon the forward stroke of the conveyer and in a rearwardly and upwardly inclined direction upon the return stroke of the conveyer.

The guide member 2| a and the guide member 22 of each side frame member 20 form guide tracks for a reciprocably movable counterweight 23, which is provided to neutralize the tendency of the shaking action of the trough section II to move the base I3.

The guiding support for the conveyer trough section I I on each side frame member includes a pair of bracket members 25, disposed adjacent the rear end of said trough section and projecting laterally from opposite sides thereof and extending along the insides of the guide members 2| 2| and outwardly along opposite sides thereof (see Figure 9). A retaining plate 25a is secured to th outside of each bracket member and extends along the outside of said guide member. A pair of longitudinally and vertically spaced rollers 26, 26 are journaled in each bracket and plate, for rotation about transverse axes. Said rollers, as herein shown, have substantially V- shaped faces engaging corresponding V-shaped recesses formed in opposite sides of said rear guide member.

A pair of bracket members and retaining plates indicated generally by reference characters 21, 2!? and similar to the bracket members 25 and retaining plates 25c, 25c, project laterally from opposite sides of the forward portion of said trough section. Said bracket members have longitudinally and vertically spaced rollers 28, 28 transversely journaled therein, which are adapt-- ed to ride in V-shaped grooves formed in opposite sides of the forward guide members 22a, 22a.

Downward and forward movement of the reciprocating trough section it along the guides 2 I, 2 I, 22a, 2201. is limited by the shovel l6, transversely pivoted to the forward end of said reciprocating trough ection and overlapping the receiving end of said trough section at its discharge end. Pivotal movement of said shovel is limited by a pair of spaced yleldable controlling members 24, is, pivotally connected to and yieldably movable with respect to the forward ends of the side frame members 261, ill.

Each counterweight 2% is provided with a pair of longitudinally spaced forward and rear reportions 52, i2 inclined in the same direction as the guide members Slla and 22. Each of said recessed portions has a pair of longitudinally and vertically spaced rollers 43. 43 mounted therein (see Figures and 1.3). A retaining plate ti t is secured to the outside of saidcounterweight and closes the outer open portion. of rear opening @2. Said rear retaining plate forms a support for the outer ends of the shafts on which said rollers are mounted and has a rearwardly projected portion 45 to which the drive mechanism for reciprocably driving said counterweight, is pivotally connected. A retaining plate 38 closes said forward recessed portion and forms a support for the outer ends for the shafts on which the forward rollers 43, 43 are mounted. The guide members 2m and 22 fit within said recessed portions and are engaged by the V- shaped rollers 43, ts and form a supporting guide for said counterweight on said side frame members.

The pivotal supporting connection between the reciprocating trough section ii and the shovel i6 includes a pair of laterally spaced cars 29, 29, projecting re rwardly from opposite sides of said shovel and pivotaily connected with bracket members Si], 30 by means of pivotal pins 3|, 3!. Said bracket members project laterally and forwardly from opposite sides of the forward end of said reciprocating trough section and also form a connection for the means for reciprocably driving said reciprocating trough section from the motor IT.

The controlling members 2Q, 24 for the shovel l6 depend from and are transversely pivoted at their upper ends to brackets 34, 34, projecting forwardly from the forward ends of the side frame members 20, 2t. Said control members each have a downwardly inclined slotted portion 35, opening towards the ground and closed by a retaining member 36. A block 31 is slidably mounted in each slot 35 and is pivotaliy connected to an outer side of the shovel Iii by a pivotal pin 38. An arm 3% projects rearwardly from the upper portion of each of said control members just beneath the bracket 34 and forms a seat for the upper end of a compression spring 46, supported at its lower end in a forwardly projecting portion ll of said side frame member. Said springs are adapted to yield upon the forward strokes of the conveyor as said blocks 31, 31 slidably move along the slots 35, 35 to permit said shovel to yieldably pivot about the axes of the pins Si, Si and to yieldably engage the forward end of said shovel with the ground. Pivotal movement of said shovel in an opposite direction is limited by engagement of the arms 3b with the under sides of the brackets 34. 34.

The mechanism for reciprocably driving the trough section H and shovel l6 along the guide members 2i, 2!, 22c, 22c; and for reciprocably moving the counterweights 23, 23 along the guide members 2m, Bid, 22, 22 in opposite phase relationship with respect to said reciprocating trough section and shovel includes a pair of rocking members 5i, il, mounted adjacent opposite ends of a transverse rock shaft 39 (see Figures 5, 6 and 7). An arm 59 depends from each rocking member 5?. Each of said arms has a drive link 5i pivotally conn cted thereto and extending angularly upwardly and rearwardly therefrom. Said arms are connected at their rear ends to the projecting portions 45, 45 of the retaining plates es. it, secured to the outer portion of said countervveights.

An arm 52 projects upwardly from. each rockinember ll in a diametrically opposite direction from the arm 58, and has pivotal connection with the rear end of a link 53, pivotaily connected to the forward end of the reciprocating trough section ii. A plunger 5% is slidabiy mounted in the forward end said link and is encircled by a preloaded compression spring 55 (see Figure 3). Said spring is loaded by means of a pair of vertically spaced parallel rods 54a. S lo. which are threaded in a collar 28. adjacent the forward end of said plunger, and which are slidabiy mounted in a flanged portion of said link. which abuts the rear end of said spring. An eye 5% is formed on the forward end of said plunger and is transversely pivoted to a forked portion of a connecting link 57. Said connecting link in turn has vertical pivotal connection with an car 59 projecting rearwardly from the bracket member 39, thus forming a universal connection between the end of said link and said trough section. The compression springs 55, 55 are loaded to such an extent and their strength is such that said plungers normally act as solid members and there is no movement of said plunger with respect to said links. said springs being adapted to yield only when the forward end of the shovel 55 engages a solid obstruction, to prevent damage to said shovel and the drive mechanism therefor.

The transverse rock shaft 45% is oscillatively driven from the motor H by means of a worm and worm gear drive indicated generally by ref erence character 60 and driven from the forward end of said motor by means of a suitable coupling 6| and a shaft 62, extending longitudinally forwardly from said coupling (see-Figure 4). A crank 53 is driven from the worm gear of said worm and worm gear drive and has a link 64 journaled thereon. The end of said link opposite from said crank has pivotal connection with an arm 55 of a rocking member 56, which is journaled on a transversely extending shaft 57'. Said rocking member has a depending rocking arm 63, which has a. link 69 pivotally connected thereto. The end of said link opposite from said rocking arm has pivotal connection with a rocking arm l6 secured to the transverse rock shaft 49, for rocking said rock shaft.

The arrangement of said crank, links, and rocking arms is such as to rock the rocking shaft 49 and reciprocably drive the trough section I I in such a manner as to cause material to move from the forward to rear end of said trough section by reciprocable movement of said trough section, and to reciprocably move the counterweights 23. 23along the guide tracks Zia, 22 in opposite phase relationship with respect to said trough section, to counteract the effect of the reciprocable action of said trough section to move the base I3 along the ground.

Referring now in particular to the means for reciprocably moving the weighted propelling member I in various desired directions along the base I 3 and for controlling the stroke of movement thereof, a crank 80 is rotatably journaled at its lower end on the bottom of the base frame I3 on a bearing BI, and adjacent its upper end on a bearing 82 mounted in a bearing support member 83 secured to the cover portion I8 of said base frame (see Figure Said crank has a splined portion 84 which projects upwardly from the bearing 82 and engages a splined hub of a worm gear 85. Said worm gear is driven from a longitudinally extending worm 86,, which in turn is driven from the rear end of the motor I'I' by means of a suitable coupling 81 (see Figure 4);

A connecting link 88 is journaled on the crank 80 on ball bearings 89, 89. The free end of said connecting link has pivotal connection with a horizontally extending rocking arm 95 of a rocking member 9I. Said rocking member is secured to a vertical shaft 93, which is suitably journaled at its ends and intermediate its ends in the base frame I3 (see Figure 16). A lower horizontally extending arm 94 of said rocking member has a link 95 pivotally connected thereto, which has pivotal connection at its end opposite from said arm with an arm 51 projecting horizontally from the lower end of a rocking member 99 (see Figures 3 and 15). Said rocking member is mounted on a vertical shaft I00 suitably journaled in the base frame I3. An arm IEH projects horizontally from the upper end of said rocking member and has a link I02 pivotally connected thereto by means of a pivotal pin N33. The end of said link opposite from said arm is pivotally connected with and drives an oscillatively movable drive member I05.

The oscillating drive member I05 is best shown in Figures 3, 14, and 17 and extends vertically from the bottom of the base frame I3 to a position just beneath the cover I8. Said drive member is provided with a lower inwardly projecting portion IO'I journaled on the bottom of the base E3 on a bearing I08. Said drive member is likewise provided with an upper inwardly projecting portion I09, spaced vertically from said lower portion and journaled on a bearing support member III! on a bearing III.

The means for reciprocably driving the propelling weight I5 along the base I3 in various directions with respect thereto in a plane parallel with said base, includes three vertically spaced slotted drive portions H3, H4 and H5 projecting inwardly from said drive member and disposed intermediate the portions I01 and I09 and forming a drive means for driving three vertically spaced linkage connections H6, H1 and H8 respectively. Said linkage connections are connected with the propelling member I5 at different points, and are selectively operable to drive said propelling member in diiferent desired directions and in dilferent phase relationships with respect to the base I 3, for causing said base to move along the ground in the desired direction.

The upper linkage connection II8 has drive connection with one side of the weight I5, adjacent the rear end thereof, for reciprocably moving said weight in a sidewise direction, and includes a link II9 connected at one of its ends to a rocking arm I20 of a rocking member I 2I. The opposite end of said link extends along opposite sides of the drive portion II5 of the drive member I55 and along the upper and lower sides of a guide block I23 and is connected therewith by means of a vertical pin I22, journaled in said block (see Figure 20). Said block is slidably movable in a guide slot I24, which forms the slotted portion of said upper drive portion H5.

The guide slot I24, as herein shown, is formed from a pair of parallel spaced members I25, I25, secured to and extending inwardly from opposite sides of the drive portion H5 and connected together at their free ends by means of a re taining member i25. Said slot I24 is intersected by the axis of rocking movement of said drive member I55, and is so arranged that the block I23 may be so positioned in said driving slot that the vertical axis of the pin I22 will be coaxial with the axis of rocking movement of said drive member. When said block is in this position there will be no reciprocable movement of said linkage connection, and said linkage connection will have no driving effect on said propelling weight. When said block is on one side of the pivotal axis of said drive member, said weight will be driven to impart a moving force in one direction, and when said block is on the opposite side of the pivotal axis of said drive member, said weight will be driven to impart a moving force in an opposite'direction. Also, the farther said block is positioned from the pivotal axis of said drive member, the more violent will be the reciprocating action of said propelling weight and the greater will be the propelling force thereof.

The position of the block I23 in the slot I2 is controlled by means of a pair of stroke control links I21, I21, pivotally connected to opposite ends of the pin I22 and extending forwardly therefrom. Said stroke control links are connected at their forward ends to a slidably movable guide member I28, by a vertical pin I29. Said guide member is slidably guided at its outer ends in a pair of parallel spaced longitudinally extending guide rods I39, I36, which are mounted at their ends in a pair of longitudinally spaced support members I3I I3I, secured to and projecting vertically from the base I3 (see Figures 3, 17, 18 and 21).

The means for moving said guide member and stroke control links or for holding said guide member and stroke control links in a fixed position, includes a pair of aligned opposed cylinders I32, I32, extending longitudinally of the base I3. Each of said cylinders has a piston I33 movable therein, from which extends a piston rod I34. The adjacent ends of said piston rods are herein shown as being threaded in and projecting in opposite directions from the guide member I28.

A compression spring I35 encircles each piston rod I34 and is adapted to be engaged by the guide member I23 when the piston I33, connected to the opposite piston rod I34, has traveled substantially half its stroke, to counteract the tendency of said piston to travel its entire stroke without stopping and to aid in initially returning said piston to the opposite end of its cylinder.

Fluid under pressure may be admitted to either one of said cylinders or held therein under pressure by a suitable system of piping and valves, the details of which will be more fully described as this specification proceeds.

Movement of the guide member I28 along the guide rods I30, I30 will thus slidably move the block I23 along the driving slot I24, to position the upper linkage connection I It! to reciprocably drive the propelling member I in one direction at varying intensities, depending upon the disstance of said block from the pivotal axis of the drive member I5, and to shift the point of maximum velocity of said Weighted member 180 degrees, to cause said weighted member to reverse the direction of movement of the base I3 along the ground. It is understood that reversal of the direction of movement of said base is effected by shifting the block I23 to one side or the other of the axis of rocking movement of said drive memher.

The linkage connection from the link I I9 and rocking member I2I to the propelling member I5 includes an outwardly projecting arm I43 of the rocking member I2I, having a link I4I pivotally connected thereto. Said link extends longitudinally forwardly from said rocking arm and has pivotal connection with'a rocking member I44 on a vertical shaft I45. A rocking arm I41 extends in a forward direction from said shaft and has a drive link I49 pivotally connected to its free end and extending inwardly therefrom and having pivotal connection at its inner end with said propelling weight.

The end of the drive link I43 opposite from the rocking arm I41 extends within a longitudinally slotted portion I50 of the propelling weight I5. Said end of said drive link is slidably guided in said slotted portion so-said link will reciprocably move said propelling weight transversely of said base, but will permit longitudinal movement of said weight with respect to said link. The guiding connection between said link and said slotted portion includes a pair of bearing blocks I53, I53 abutting the top and bottom sides of said link and pivotally connected thereto by a pivotal pin I52. Said bearing blocks are slidably mounted in facing longitudinally extending channelled bearing members I54, I54, mounted in and extending along said slotted portion, to permit longitudinal movement of said propelling weight with respect to said link.

A control arm I55 is provided to prevent movement of said drive link in a direction longitudinally of said base during reciprocable movement of said weight in longitudinal or transverse directions. Said control arm is pivotally mounted on the base frame I3 on a pivotal pin I53 and has pivotal connection at its free end with the drive link I49, at a point spaced'a slight distance inwardly from the rocking arm I 41.

The intermediate linkage connection H1 is adapted to reciprocably move the propelling weight I5 longitudinally of the base frame I3 and includes a transversely extending link I59 pivotally connected at its inner end to an arm I of a rocking member I51. Said rocking member is rockingly mounted on. the base frame i3 on a vertical shaft I53 and has connection with the propelling weight I05, for reciprocably moving said propelling weight longitudinally of said base. The end of said link opposite from said rocking arm is of a bifurcated formation and is connected to opposite sides of a guide block I54, guided in a guide slot I55 formed inthe drive portion H4 in a manner similar to which the driving slot I24 is formed in the drive portion I I5.

A pair of stroke control links I55, I55 are pivotally connected to the outer sides of thebifuroated portion of said link I59 and extend longitudinally forwardly therefrom and are pivotally connected attheir forward ends to opposite sides of a guide member I31 by means of a vertical pin I59.' Said guide member is constructed in a manner similar to the guide member I28 and is supported and guided in a pair of-parallel spaced guide rods I10, I19, mounted at their ends in the support members I3I, I3I.

Two aligned piston rods I'1I, III are threaded in and project in opposite directions from said guide member and, as herein shown, have pistons I12, I12 at their outer ends, which are slidably mounted in fluid cylinders I13, I13, for mov ing said guide member longitudinally along the guide rods I10, I19 and moving the block I54 and link I59 to various desired positions with respect to the drive member I65. Compression springs E14, E14 encircle said piston rods and are adapted to counteract the tendency of saidpistons to travel their full stroke and'to initially aidsaid pistons in moving the guide member I61 and stroke control links I66, I56. It should here be noted that the cylinders I13, I13 and' pistonsl12, I12 are of a larger diameter than the cylinders I32, I32 and pistons I33, I33. The reason for this is that two linkage connections are provided to move the propelling weight I5 transversely of the base while only one linkage connection is provided to move said weight'longitudinally of the base. The reaction against the stroke control links I63, I66 is thus twice as great as the reaction against the control links which control the strokes of the linkage connections H6 and H8.

The connections from the rocking member IGI to the propelling weight I5 includes an inwardly and forwardly projecting rocking arm I15 having pivotal connection with a generally longitudinally extending drive link I16. A control arm I11, rockingly mounted on the base frame I3 on a vertical shaft I18, is pivotally connected at its free end to the rear end of the drive link I16 by a pivotal pin I19, to prevent transverse movement of said link during reciprocable movement of said propelling weight.

The forward end of the drive link I16 extends within a transversely slotted portion I331 of the rear end wall of the propelling weight I5, and has bearing blocks I84, I84 pivotally connected to opposite sides thereof by means of a pivotal pin I85. Said bearing blocks are guided in facing channelled bearing members I86, I85 mounted in the slot I83 and extending transversely thereof, beyond opposite sides of said propelling weight so said propelling weight may move transversely of rocking member (see Figures 4 and 14:).

the base I3 while said drive link is held from transverse movement by the control link I11.

Thus when the block IE4 is to one side or the other of the axis of rocking movement of. the drive member I05, the intermediate linkage connection II1 will reciprocably move the propelling weight I5 longitudinally of the base I3, to cause said base to move in a forward or rearward direction with respect to the working face at varying rates of speed, depending upon the position of said guide block with respect to the pivotal axis of said drive member; Movement of said linkage connection is so synchronized with reciprocable movement of the shovel I5 that when said propelling weight is moving the shovel I6 into the material it is desired to load, the maximum velocity of said propelling weight will be reached upon its forward strokes at the same time the trough section II and shovel It reach their maximum velocity upon their forward strokes. a

The lower linkage connection I I6 is provided to reciprocably drive the forward end of the propelling weight I5 transversely of the base frame I3. l Said linkage connection includes a link I38 pivotally connected at one of its ends to a rocking arm I89 of a rocking member I96, herein shown as being disposed beneath the rocking member I2I and mounted coaxially with. said The end of said link opposite from said rockin arm is bifurcated and extends along opposite sides of a guide block I9I and is pivotally connected thereto. Said guide block is slidably movable in a slot I94 formed in the driving portion II3 of the drive member I 05 in the same manner the slot I24 is formed in the driving portion H5 of said drive member.

A pair of stroke control links I95, I95 are pivotally connected to opposite sides of the bifurcated portion of the link I88 in the same manner the stroke control links I21, I 21 are pivotally connected to opposite sides of the link I I9. Said 7 stroke control links I95 extend longitudinally forwardly of the link I38 and are pivotally connected at their forward ends to opposite sides of a guide member I96 by means of a pivotal pin I91. Said guide member is slidably guided in guiderods I99, I99 mounted at their ends in the support members I3I, I3I. A pair of oppositely extending piston rods 200, 298 are herein shown as beingthreaded in opposite ends of said guide member. Each of said piston rods has a piston 20I on the free. end thereof Which is movable in a fluid cylinder 292. Compression springs 203, 203 encircle said piston rods and serve the same purpose as the compression springs I35, I35 and I14, I14.

The rocking member I90 has a rocking arm 2M disposed beneath and extending in the same general direction as the arm I40 of the rocking member I2I (see Figure 4). A link 205 is pivotally connected to the free end of said rocking arm and extends longitudinally forwardly therefrom. The forward end of said link has pivotal connection with an arm 2% of a rocking member 201. An arm 208 of said rocking member extends longitudinally forward therefrom and has the outer end of a drive link 2B9 pivotally connected thereto. A control link 2111 is pivotally mounted on the base frame I3 on a vertical pin 2 and has pivotal connection with the drive link 209 a slight distance inwardly of the point of connection of said drive link to the rockmg member 201, for preventing longitudinal movement of said drive link with respect to said propelling weight. The inner end of said drive link extends within the slotted portion r55 of the propelling weight I5 and ha a pair of vertically spaced bearing blocks 2i 2, 2:2, abutting opposite sides thereof and pivotally connected thereto by means of a pivotal pin 2I3. Said bearing blocks extend along the top and bottom sides of the inner end of said control link and are slidably guided in the channelled bearing members I54, I5 1.

Referring now in particular to Figures 1 and 22 to 24 and the means for controlling the flow of fluid to the cylinders I32, I32, I13, 13 and 292, 202 and controlling movement of the propelling weight I5, when being reciprocably moved in various angular directions, a remote push button control generally indicated by reference character 254 is provided. Said push button control is adapted to be placed remote from the machine and connected thereto by means of an electric cable 2I5 (see Figure 1). Said control is diagrammatically illustrated in Figure 22 and may consist of a plurality of push buttons 2K5, 211, 238, H9, 220, 22I, 222, and 223, each of which push buttons is adapted to control certain operations of the device. A plurality of solenoid operated valves 224, 225, 226 and 221, herein shown as being in a valve manifold 229, are mounted on one side of the machine and the solenoids of said valves are operatively connected with said push buttons.

The valves 224 to 221 inclusive are of a well known balanced type of piston valve, so will not herein be described in detail, and are of a similar construction so the same part numberswill be applied to the same operating parts of each of saidrvalves. Each of said'valves is operated by two aligned solenoids 23!, 232, so arranged that the solenoid 23I will move a piston 233 of one valve in one direction and the other solenoid 232 will move said piston in an opposite direction.

The valve 224 is operative by the push buttons 2I6 and 2I1 and has connection withthe head ends of the cylinders 13, 13, for admitting fluid under pressure thereto and holding pressure therein or permitting fluid to be released therefrom. The piston 233 of said valve is normally in a position to close the pressure ports thereof, when the push button switche 21s and 2I1 are open. When pressure is applied to the push button ZIB, to close the circuit to the solenoid 231 of said valve 224, the piston 233 of said valve will move in a direction towards said solenoid to open a pressure port leading to a pipe 234, connected with the head ends of the cylinders 13, 13 to permit fluid under pressure to flow from said cylinders to a storage reservoir 235 through a pipe 236 and to permit lowering of the trough section II and shovel I6. When the push button switch 2I1 is closed and th push button switch 2I6 is open, the piston 233 will be moved in an opposite direction to admit fluid under pressure to the pipe 234 and the cylinders 13, 13 and elevate said reciprocating trough section and shovel. When both push buttons are open, the piston 233 will return to a position to close the port leading t c; tllize pipe 234 and hold pressure in the cylinders I When the push button 2I8, controlling opera tion of the valve 225, is closed, fluid under pressure will be admitted to the right-hand cylinder I32 through a pipe 231, and will be exhausted from the left-hand cylinder through a pipe 258,

2I9 is closed, fluid under pressure will be admitted to the left-hand cylinder I32 through the pipe 238, the port leading to the pipe 23'! being open at this time, to permit the return of fluid from the right-hand cylinder I 32 to the fluid storage tank 235. The instant, however, both push buttons 2I8 and Eli? are open, the ports leading from the pipes 231 and 233 wiil be closed, to hold pressure in said pipes and to hold the pistons I33, I33 in the desired position in their cylinders, thus holding the block I23 in the desired position in the slot IN, to provide the desired driving effect of linkage arrangement H8.

Similarly, closing of the push button 22!) will cause the pistons IlZ, I12 to move from right to left and closing of the push button 22I will cause said pistons to move in the opposite direction. The pistons 2M, 28! are controlled by the valve 22! and push buttons 222 and 223 in the same manner that the pistons II'Z, I12 and I33, I33 are controlled by their respective valves 225 and 226.

Pressure is eifected in the system by means of a pump 239 connected with the storage tank 235 by means of a pipe 235. Said pump may be of any type but is herein diagrammatically shown as being of a well known type of gear pump. The pressure side of said pump is connected with a relief valve generally indicated by reference character MI by means of a pipe 242. A high pressure pipe 243 leads from said relief valve to a high pressure line 244, connected with the valve manifold 229, for supplying fluid under pressure thereto. A pipe 245 connects said valve with the return pipe 236 leading to the fluid storage tank 235, to relieve pressure from the system upon overload thereof in an obvious manner. The pressure pipe 244 has a branch 2% leading to an accumulator 247, for building up pressure and supplying fluid under pressure to the manifold 229 when the pump 23% is not in operation. Said accumulator, as herein shown, is built into and is a part of the storage reservoir 235, and is of a type well known to those skilled in the art so is not herein shown or described in detail.

Referring now in particular to Figures 25 to 30 inclusive, diagrammatically illustrating various positions of the linkage connections for moving the propelling weight It in various directions with respect to the base I3, in Figure 25 the linkage connections lit and H8 are shown as being so positioned in their respective drive slots in the drive member H35 that said linkage connections will act together and reciprocably move the propelling weight I5 transversely of the base frame I3. As shown in this figure, the axes of connection of the linkages H6 and H8 to the driving member I95 are coaxial and are in an extreme forward end position with respect to said driving member. The axis of connection of the linkage connection Ill to said driving member IE5 is shown as being coaxial with the pivotal axis of said driving member. Said last mentioned linkage connection is thus inoperative to reciprocably move said propelling weight. When the linkage connections are in the position shown in this figure, the maximum velocity of said propelling weight will be at the time when said weight is moving from the left to the right-hand side of the base and will be shortly before said weight reverses its direction of travel along said base and starts to move to the left hand side of said base. Said propelling weight will thus shift said base along the ground in a direction from left to right.

In Figure 26, the axes of connection of the linkages H6 and H8 have been shifted to the opposite side of the pivotal axis of the drive member I05 from that shown in Figure 25. When said links are in this position, the maximum velocity of said weight will be reached as it is moving transversely across the base from right to left, just before said weight reverses its direction of movement along said base. The base will thus be moved towards the left-hand corner of the Working place.

In Figure 27, the linkage connections H8 and H5 are shown in the same relative positions on the drive member I55 as in Figure 25, but the axis of pivotal connection of the linkage Ill to said drive member has been moved to a position at the opposite end of said drive member from the axes of pivotal connection of the linkage connections H6 and H8 to said drive memher, This will cause the linkage connection Ill to reciprocably move the propelling weight I5 in a longitudinal direction with respect to the base I3 at the same time it is moved transversely of said base by the linkage connections HE and H8. In this position of the linkage connections IIB, Ill and II8 on said drive member, the propelling weight will reach its maximum velocity upon its rearward or return stroke. This will cause said propelling weight to move the base 53 in an angularly rearward direction away from the working face from the left to right-hand side thereof.

In Figure 28, the axes of connection of the respective linkage connections H8 and Iiii are coaxial with the axis of rocking movement of said drive member. Said linkage connections will thus be inoperative and will perform no driving action on the propelling weight I5.

The axis of connection of the linkage connection III to said propelling'weight, however, is shown as being moved to an extreme forward position. Said linkage connection will thus reciprocably move the propelling weight I5 along the base in a longitudinal direction, said weight being guided for such movement by means of the drive links I49 and 269 of the respective linkage connections H8 and H6, slidably guided in the longitudinal slot I59. The arrangement of said linkage connection Ill is such that the maximum velocity of the weight I5 will be reached at its forward stroke, just before it reverses its direction of travel. This will cause said weight to move with the base I3 towards the working face, to feed the shovel IE into the material it is desired to load, the maximum velocity of theforward strokes of said weight occurring at the same time the trough section I I and shovel I6 reach their maximum velocity upon their forward strokes. Thus said weight reciprocably moving along said base in the same phase relation with respect to the reciprocable movement of the trough section II and shovel I5, will feed said shovel into the material it is desired to load with sufiicient intensity to not only feed the shovel I6 into broken down material, but also to feed said shovel into material which is tightly wedged between the mine bot tom and roof with suflicient force to cause said shovel to break down this tight coal.

When it is desired to move the loadin device away from the workingface, the linkage connection I I I is so positioned with respect to the drive member I05 that its axis of pivotal connection to said drive member is on the opposite side of the axis of rocking movement of said drive member from that position shown in Figure 25.

In Figure 29 the linkage connection III! is shown as being in a neutral position and the linkage connections l [6 and I I8 are shown as being so positioned that their pivotal axes are on opposite sides of the axis of rocking movement of the drive member I05. Said linkage connection will thus reciprocably move the propelling weight l in an angular direction about its rear end as is shown in this figure. This will cause said propelling weight to move the base in an angular direction from right to left.

In Figure 23 the positions of the linkage connections Hi3 and H8 have been reversed from that shown in Figure 26 to reciprocably move the propelling weight l5 in an opposite angular direction from that shown in Figure 26 and to cause the base to pivot from left to right.

As has been mentioned before, the intensity of the propelling action of the propelling weight may be increased or decreased by varying the distances of the axes of pivotal connection of the linkage connections to the drive member [5, from the pivotal axis of said drive member 35, it being understood that the farther away the points of connection of said linkage connections are from the pivotal axis of said drive member, the longer will be the strok and the more intense will be the propelling action of said drive member. It should beunderstood, however, that as the propelling effect of said propelling Weight is increased, that upon the return stroke of said propelling weight, the tendency of the base l3 to slip backwardly along the ground will correspondingly increase, the amount of backslip being determined by the frictional resistance between the bottom of said base and the ground. Accordingly, during operation of the device, the intensity of the conveying operation must be regulated by the stroke control links and cylinders in the hereinbefore described manner to such a degree that there is little or no backslip. It has been found that in certain cases where the frictional resistance between the bottom of the base and the ground is relatively low, that a soft stroke of the propelling weight, with a relatively low maximum velocity on the propelling stroke, will move the apparatus at a higher rate of speed than a hard stroke with a high maximum velocity, due to the fact that with the soft stroke there is little or no backslip of the base along the ground. Where the frictional resistance between the base and the ground is relatively high, the backslip will be decreased and it has been found that a harder propelling stroke can be utilized.

It may be seen from the foregoing that a new and improved loading device has been provided having a novel and improved form of mechanism for feeding a gathering shovel into the material it is desired to load, at varying intensities under the control of the operator, and for moving the device across and into or away from the working face. It may likewise be seen that the device may be readily controlled in a simplified.

manner from a point remote from the machine proper, thus enabling the operator to be close to the face when desired, or to be at a distance remote from the machine in cases where the machine is being fed into a tight place with a maximum intensity of the propelling weight l5, or where roof or other conditions might be bad close to the face. i V 7 While I have herein shown and described one form in which my invention may be embodied, it will be understood that the construction thereof and the arrangement of the various parts may be altered without departing from the spirit and scope thereof. Furthermore, I do not wish to be construed as limiting my invention to the specific embodiment illustrated, excepting as it may be limited in the appended claims.

I claim as my invention:

1. In a loading device of the class described, a base, a trough section mounted on said base for reciprocable movement with respect thereto, a shovel on the forward end of said reciprocating trough section for picking up loose material from the ground, and means for moving said base along the ground and for feeding said shovel into the material it is desired to load comprising a propelling weight on said base and means for reciprocably moving said propelling Weight along said base in a transverse or longitudinal direction with respect thereto and in a definite phase relation with respect to said reciprocating trough section and shovel.

2. In a loading device of the class described, a base, a trough section mounted on said base for reciprocable movement with respect thereto, a shovel on the forward end of s id trough section for picking up loose material from the ground, means for moving said base along the ground and for feeding said shovel into the material it is desired to load comprising a propelling weight on said base, means for reciprocably moving said propelling weight along said base in a definite phase relation with respect to said reciprocating trough section and shovel, and means for controlling movement of said propelling weight with respect to said base, to vary the point of maximum velocity of said propelling weight and cause said propelling weight to move said base in various directions along the ground.

3. In a loading device of the class described, a base, a trough section mounted on said base for reciprocable movement with respect thereto,

a shovel on the forward end of said trough section for picking up loose material from the ground, and means for moving said base along the ground and for feeding'said shovel into the material it is desired to load comprising a propelling weight on said base, means for reciprocably moving said propelling weight along said base including a crank and a linkage connection between said crank and said weight, and other means for controlling movement of said linkage connection and varying the point of maximum velocity of said propelling weight, to cause said propelling weight to move said base in a forward or return direction along th ground.

4. In a loading device of the class described, a base, a trough section mounted on said base for reciprocable movement with respect thereto, a shovel on the forward end of said trough section for pickingup loose material from the ground, and means for moving said base along the ground and for feeding said shovel into the material it is desired to load comprising a propelling weight on said base, means for reciprocably moving said propelling weight longitudinally of said base including a crank, a member reciprocably driven thereby, a linkage connection between said member and said propelling weight, and means for varying the point of connection of said linkage connection to said member, to change the point where the maximum velocity of movement of said propelling weight occurs from the forward to return strokes thereof and to reverse the di-

Images