US3096893A

US3096893A - Loading machine

Info

Publication number: US3096893A
Application number: US10715A
Authority: US
Inventors: Anthony R Biedess
Original assignee: Goodman Manufacturing Co LP
Current assignee: Goodman Manufacturing Co LP
Priority date: 1960-02-24
Filing date: 1960-02-24
Publication date: 1963-07-09
Anticipated expiration: 1980-07-09

Description

July 9, 1963 A. R. BIEDEss 3,096,393

LOADING MACHINE Filed Feb. 24. 1960 s sheets-sheet 1 July 9, 1963 A. R. BIEDEss 3,096,893

LOADING MACHINE Filed Feb. 24. 1960 8 Sheets-Sheet 2 INVENTUR.

Anhony R. Biedess BY ATTORNEY A. R. BIEDESS LOADING MACHINE July 9, 1963 8 Sheets-Sheet 3 Filed Feb. 24. 1960 "0 INVENTUR.

Anhony R. Biedess Fig. 7

ATTORNEY July 9, 1963 A. R. BIE-DESS 3,096,893

LOADING MACHINE Filed Feb. 24, 1960 8 Sheets-Sheet 4 IN VEN TOR.

g By nhony R. Biedess M Q 7g2-wmv July 9, 1963 A. R. BIEDEss 3,096,893

LOADING MACHINE Filed Feb. 24. 1960 8 Sheets-Sheet 5 INVENT OR.

Anhony R. Biedess BY 7' ORA/EV July 9, 1963 A. R. BIEDEss 3,096,893

LOADING MACHINE Filed Feb. 24, 1960 8 Sheets-Sheet 6 July 9, 1963 A. R. Biani-:ss 3,096,893

LOADING MACHINE Filed Feb. 24. 1960 8 Sheets-Sheet 7 INVENTOR. mfo/yy P. 5mn/ess A. R. BIEDESS LOADING MACHINE July 9, 1963 8 Sheets-Sheet 8 Filed Feb. 24, 1960 NN n x S MN T. .e M.. MN. @rml M 'lilla-WJ 1P. IESEFFFWW V NwN W ,m M W A www.

United States Patent Olilce 3,096,893 LOADING MACHINE Anthony R. Biedess, Chicago, III., assigner to Goodman Manufacturing Company, Chicago, III., a corporation f Illinois Filed Feb. 24, 1969, Ser. No. 10,715 7 Claims. (CI. 214-30) This invention relates generally to mocking machines for loading rock and the like, operable in tunnels or mines underground where limited head room is available, and more particularly rela-tes to improvements in the :boom arrangement and bucket operating mechanism for Such machines.

Mucking machines for loading rock and the like, as known in the art, generally comprise a main frame supported on traction means for propelling the main frame along the ground, which main frame has a conveyor mechanism extending rearwardly therealong from a position in advance thereof adjacent the ground and has a digging bucket disposed in advance of -the forward end of Vthe main frame, which is crowded into the mined loose material on the ground and lifts and discharges the loose material onto the conveyor.

The digging bucket usually has digging teeth extending in advance thereof and slidable along the ground and crowded into the mined material along the ground to ll the bucket therewith. The bucket is then lifted upwardly in an angular path toward the conveyor mechanism to dump its load on the conveyor mechanism, which carries the mined material along the machine beyond the rear end of 'the main frame for dumping into shuttle cars or other means .for transporting the mined material from the working face.

A problem in the design of such machines is to so design the machine, that it will efficiently operate in places of low headroom and pick up the relatively heavy rock from the ground and raise and discharge the rock onto the conveyor mechanism in a substantially continuous operation with little or no delay, particularly in picking up the heavy rock Efrom the ground.

It is also advantageous that the maneuvering of the machine and the conveyor mechanism during the crowding and loading operation be reduced to a minimum to facilitate the spotting of shuttle cars or other material transporting means at the discharge end of the conveyor mechanism and to provide as continuous a flow of mined material to the shuttle cars or other material carrying means as possible commensurate with loading and transporting conditions.

ln order to etciently pick up and load the material, it is essential that the digging bucket be carried in advance of the forward end of the machine and be so supported that it may readily Slide over small obstructions on the ground encountered by the digging teeth at the leading edge of the bucket when crowded into the mined material, and that mechanism for operating the bucket provide a relatively high tearing force for tearing the loaded bucket upwardly through the mined material on top 0f the bucket at a relatively slow rate of speed and then move the loaded bucket to its discharge position at a higher rate of speed.

It is, therefore, an object of the present invention to provide a mucking machine for loading rock `and the like arranged Vwith a view toward incorporating all of the foregoing advantageous features in the machine.

Another object of the invention is to provide an improved form of mucking machine so constructed and arranged as to operate in places of confined headroom to elciently tear the loaded digging bucket away from the mined material and quickly dump the mined material onto the material carrying conveyor of the machine.

3,096,893 Patented July 9, 1963 Still another object of the invention is to provide a bucket operating mechanism for mucking machines of the rock loading type accommodating the bucket to readily follow on even ground and ride over obstructions on the ground as the `bucket is being crowded into the loose material being loaded.

Still another object of the invention is to provide a bucket operating mechanism particularly adapted for mucking machines of the rock loading type, in which the leverage arrangement of the bucket operating mechanism is so arranged as to provide a high mechanical advantage for breaking away t e loaded `bucket `from the loose material being loaded and to reduce the mechanical advantage and increase the speed of travel of the bucket as it moves to a discharge position after it has been torn away from the material being loaded.

Still another object of the invention is to provide an improved form of mucking machine of the rock loading type so arranged as to enable the discharge end portion of the conveyor mechanism to be maintained relatively stationary during the digging and loading of the mined material onto the receiving end of the conveyor mechamsm.

A still `further object of the invention is to provide an improved form of `boom arrangement for a mucking machine of the rock loading type, wherein the boom, operatively carrying a digging and loading bucket at its forward end, may be operated to crowd the bucket into the loose material being loaded, while the mucking machine remains in a relatively stationary position on the ground.

This application is a continuation-impart of my application Serial No. 737,048, filed May 22, 1958, and now abandoned.

These and other objects of the invention will appear `from time to time as the following specification proceeds "ind with reference to the accompanying drawings wherein:

FIGURE l is a plan view of one embodiment of a mucking machine constructed according to the present invention;

FIGURE 2 is ya side elevational view of the machine shown in FIGURE l;

FIGURE 3 is a partial side elevational view of the embodiment shown in FIGURES 1 and 2 with the boom moved forwardly of the machine and with the bucket in a carrying position;

FIGURE 4 is an enlarged cross sectional view of a portion of the structure shown in FIGURE 3 and taken along the line 4--4 of FIGURE 3; f

FIGURE 5 is an enlarged partial view of the structure shown in FIGURE 3 and taken along the line 5-5 of FIGURE 3;

FIGURE 6 is an enlarged side elevational view partially in cross section of a portion of the embodiment of the present invention shown in the previous figures and with th-e bucket in the dump position;

FIGURE 7 is a side elevational view showing the bucket moved into a pile of material to be removed;

FIGURE 8 is a circuit diagram showing the hydraulic controls for moving the boom longitudinally of the machine;

FIGURE 9 is a side elevational view showing another embodiment of the bucket operating mechanism;

FIGURE l0 is a fragmentary View in side elevation of the forward end portion of a modified formgof mocking machine constructed in accordance with the present invention, in which the machine is mounted on rubber tire mounted traction wheels and the bucket is operated by a modified form of bucket operating mechanism;

FIGURE ll is a fragmentary View in side elevation similar to FIGURE l0, but showing the bucket in a discharge position;

FIGURE l2 is a fragmentary plan view looking substantially along line 12-12 of FIGURE 10;

FIGURE 13 is a fragmentary vertical sectional view taken substantially along line 13-13 of FIGURE l0;

FIGURE 14 is a fragmentary vertical sectional view taken substantially along line 14--14 of FIGURE 10; and

FIGURE l5 is a fragmentary horizontal sectional view looking substantially along line 1515 of FIGURE l0.

In the embodiment of the invention illustrated in FIP- URES l to 8 of the drawings, continuous traction tread devices or crawler track mechanisms 10 are shown as being provided to support and advance the machine during the loading operation and to propel the machine from working place to working place. A main frame 11 is suitably mounted on the crawler track mechanisms 1t) and extends rearwardly therefrom a substantial distance, as shown in FIGURE 2. The rearward. overhanging portion of the frame l1 is dropped a certain amount to accommodate a conveyor mechanism to extend along the main frame at a convenient height for efficient operation in places of limited head room.

The conveyor mechanism 12 may be a laterally liexible center strand chain and flight type of conveyor, such as is shown and described in the United States Patents Nos. 2,197,169; 2,388,885 and 2,642,982. The conveyor iS suitably carried on the frame 11 and extends from a position in advance of the forward end thereof adjacent the ground rearwardly along said main frame in an inclined path and beyond the rear end of said main frame in a generally horizontal plane to overhang a shuttle car or other device being loaded. The conveyor mechanism 12, as herein shown includes three interconnected trough shaped Sections 13, 14 and 1.5. The forward section 13 forms a material receiving and inclined elevating section and may be tixedly mounted upon the main frame 11. Opposite

forward wall portions

16 and 17 of the forward section 13 are inclined outwardly toward the sides of the machine and with an upwardly extending forward inclined forward wall 18 define a hopper for receiving the material dumped thereonto. The center section 14 of the conveyor mechanism 12 is joined to the rearward end of the forward scction 13 through pivotal mounting means 19. of the center section 14 about a horizontal axis with respect to the forward section 13. The rearward end of the center section 14 is connected to the forward end of the rearward section for articulated movement therebetween about a vertical axis. A hydraulic cylinder 2t) is mounted on the rearward end of the frame l1 to upstand therefrom and serves to adjustably support the center section 14 and the rearward `section 15 of the conveyor mechanism 12. Thus it may be seen that when the hydranlic cylinder 20 is extended the rearward section 15 of the conveyor mechanism 12 are pivoted upwardly about the horizontal axis of pivotal mounting means 19, and when the hydraulic cylinder 20 iS retracted the-se sections 14 and 1.5 are pivoted downwardly about the same axis. The hydraulic cylinder 20 permits vertical adjustment of the rearward end of the conveyor mechanism 12 relative to a shuttle car or other conveyor system for efiicient transfer of any load of material from the conveyor mechanism 12. Hydraulic cylinders 21 are provided for adjustably maintaining the rearward section 15 in any angled position relative to the center section 14 in a horizontal plane. The head end of each of the hydraulic cylinders 21 is pivotally connected to a bracket 22 carried on the sidewalls of the center section 14. The rod end of each of the hydraulic cylinders 21 is pivotally connected to the sidewalls of the rearward section 15 through pivotal mounting means 23. Thus, it may be seen when one of the hydraulic cylinders 21 is extended, the rearward section 15 of the conveyor mechanism 12 is caused to pivot relative to the center section .t4 in a horilivotal mounting means 19 permit pivotal movement i the center section 14 and 30, the underside zontal plane, this pivoting causing retraction of the opposite hydraulic cylinder 21.

The conveyor mechanism 12 further comprises a center strand endless chain 24 carrying a plurality of flights 25 in spaced apart relationship with respect to each other throughout the entire length of the chain 24 and connected thereto for movement about horizontal and vertical axes in a well known manner. The chain 24 extends over a suitable sprocket (not shown) rotatably earried at the rearward end of the rearward section 15, and below the rearward section 15, the center section 14 and the forward section 13 to the forward end of the forward section 13. At the `forward end of the conveyor mechanism 12, the chain 24 is passed about a suitable idler (not shown) and further extends from the idler along the upper surface of the bottom walls of the forward section 13, the center section 14 and the rearward section 15 of the conveyor mechanism 12. The chain 24 of the conveyor mechanism 12 is driven by a suitable electric motor 26 through gearing 27, shaft 28 and speed reducer 29. The output shaft of the speed reducer 29 is drivingly connected to the sprocket (not shown) for the chain 24. The electric motor 26 and the power train therefrom to the chain 24 `are carried on one side of the rearward section 15 of the conveyor mechanism 12.

Turning next to the means for loading the conveyor mechanism 12, a boom 30 is provided and formed in duplicate portions disposed on each side of the machine, the portions being interconnected at the forward end thereof by a cross-member 31. Each portion of the boom 30 is somewhat L-shaped with the relatively long leg thereof extending generally horizontally and with the relatively short leg thereof depending downwardly from the horizontal leg. The rearward end of each portion of the boom 30 is pivotally connected to a slide member 32. As may be seen in FIGURES 3 and 4 each slide member 32 is formed to have an H-shaped center section `and a pair of flanges, one formed to opstand from the H- Shaped section and one formed to depend therefrom. The rearward end of each portion of the boom 30 is pivotally connected to the upstanding llange of one of the slide members 32 by means of a pin 33. The H- shaped section of each slide member 32 engages a pair of opposed rails 34 and 35. Each pair of rails 34 and 35 is secured to the frame 11 on one side of the machine by a plurality of bolts such as bolt 36 shown in FIGURE 4. The depending flange of each slide member 32 is connected with a chain 37 between one pair of the links thereof. Each chain 37 passes in opposite directions from the depending flange about a drive sprocket 38 and an idler 39. The ends of the chain 37 are interconnected by a suitable turnbuckle or coupling 40. Each sprocket 38 is rotatively mounted on one side of the frame 11 toward the rear thereof and each idler 39 is rotatively mounted on one side of the frame 11 toward the front thereof.

Each portion of the boom 30 is slidably supported at the forward end of the machine by an individual cylinder 41. Each cylinder 41 is carried on one side of the frame 11 at the forward end thereof and immediately below one portion of the boom 30. The piston rod of each cylinder 41 is provided with a shoe 42 pivotally connected thereto by means of a pin 43. Each shoe 42 is positioned in cooperation with the underside of one portion of the boom of each portion of the boom 30 having a rail configuration conforming to the shape of the shoes 42.

From the foregoing description it may be seen that when the `sprocket 38 is rotated clock-wise as viewed in the drawings, the chain 37 will be moved to in turn move the slide member 32, which in turn will cause `the boom 30 to be moved forwardly, for example, from a position such as shown in FIGURE 2 to a position such as shown in FIGURE 3. If the sprocket 38 is rotated in a counterclockwise direction the boom 30 is moved rearwardly relative to the machine. It may further be seen that when the hydraulic cylinders 41 are extended, the forward end of the boom 30 is pivoted upwardly about the axis of pins 33 and when the hydraulic cylinders 41 are retracted the forward end of the boom is lowered. The means for operating the sprockets 38 and the hydraulic cylinders 41 will be described below.

Turning next to a detailed description of the bucket arrangement for the rst embodiment of the present invention, the bucket 45 comprises a pair of spaced-apart sidewalls 46 interconnected by a bottom wall 47 and a back wall 48. The forward marginal edge of the bottom wall 47 is provided with suitable digging teeth. Each side wall 46 of the bucket 45 is provided with a member 49 having a rearwardly extending ear or flange 50 and an outwardly extending stop member 51. The bucket 45 is pivotally carried on depending leg portions 44 of the boom 30 by means of a pair of pins 52, each pin 52 being carried by one of the depending leg portions of the `boom 30 and iournalled through one of the ears 50 of the members 49. The axis of pivoting of the bucket 45 about the pins 52 is such that when the bucket 45 is pivoted completely counter-clockwise as viewed in the drawings, the bucket 45 is moved into the forward section 13 of the conveyor mechanism 12 with the upper portions of the rear wall 4S and the side walls 46 positioned in the hopper defined by the

side walls

16 and 17 and the forward wall 18 of the forward section 13 of the conveyor mechanism 12 as may easily be seen in FIGURE 6.

To pivot the bucket 45 to its various operative positions, a bell crank 53, a hydraulic cylinder 54, a lever 55 and a hydraulic cylinder 56 are provided for each side arm of the boom 30 and each side of the bucket 45. Since these elements are formed in duplicate only those of one side arm of the boom and one side of the bucket 45 are here described. The bell crank 53 is pivotally carried on the member 49 by a pin 57. The pivot axis of the pin 57 is located on the member 49 so that one leg or lever arm of the bell crank will engage ethe underside of the stop member 51 when the bell crank 53 is pivoted counterclockwise as viewed in FIGURE 2 of the drawings. The other leg or lever arm of the bell crank 53 is pivotally connected to the rod end of the hydraulic cylinder 54 by a pin 58. The head end of the hydraulic cylinder 54 is pivotally connected to one end of the lever 55 by a pin 59, and the other end of the lever 55 is pivotally carried on the horizontal portion of the boom 30 by a pin 60. The head end of the hydraulic cylinder 56 is pivotally connected to the lever 55 intermediate the ends thereof by a pin 61, and the rod end of the hydraulic cylinder 56 is pivotally connected to the horizontal portion of the boom 30 by a pin 62 located thereon forwardly of the pin 60. The

hydraulic cylinders

54 and 56 are of such a size, and the lever 55 and the bell crank 53 are of such a length, that when the hydraulic cylinder 56 is substantially completely retracted and the hydraulic cylinder 54 is substantially completely extended, the bucket 45 is positioned for digging at the ground level of the base of the crawler tractor mechanism such as shown in FIGURE 2. These elements are further so formed and positioned that when the hydraulic cylinder 54 is retracted, the one lever arm bell crank 53 will engage the stop member 51 to pivot the bucket 45 rearwardly from the position shown in FIGURE 2 to that shown in FIG- URE 3, and if the hydraulic cylinder 56 is then extended, the lever 55 will be moved counter-clockwise as viewed in the drawings to move the hydraulic cylinder 54 and the bucket 45 through the bell crank 53 and the stop member 51 from a position such as shown in FIGURE 3 to that shown in FIGURE 6 `with `the stop means 51 engaging the other lever arm of the bell crank 53. Ylt may be seen that when the bucket is pivoted rearwardly from the position shown in FIGURE 2 to that shown in FIGURE 3, the hydraulic cylinder 54 will act through a relatively long moment arm to exert an initially relatively powerful lifting or breakout force on the bucket 45, and since thereafter in the further retraction of the hydraulic cylinder 54 the moment arm is decreased, the pivoting of the bucket 45 will occur at increasing speeds.

In the second embodiment of the means for pivoting the bucket 45 as illustrated in FIGURE 9, members identical to those of the first embodiment are designated by the same numerals. As shown in FIGURE 9, the bucket 45 is pivotally carried on the depending portions of the boom 30 by pins 52 and members 49. Since the bucket pivoting arrangement is formed in duplicate for each portion of the boom 30 and on each side of the bucket 4S, again, only those members on one side thereof Will be described. The bell crank 53 is pivotally carried on the member 49 by a pin 57. One leg or lever arm of the bell crank 53 is positioned to engage the stop 51 as in the previously described embodiment. The other lever arm 65 of the bell crank 53 which is relatively longer than the lirst mentioned lever arm or leg is pivotally connected to a link 66 by a pin 67. The other end of the link 66 is pivotally connected to one end of a lever 68 by a pin 69. The other end of the lever 68 is pivotally connected to the rod end of the hydraulic cylinder 54 by a pin 7l). 'I'lie head end of lthe hydraulic cylinder 54 is pivotally connected to a lever 71 intermediate its ends by a pin 72. One end of the lever 71 is pivotally connected to the lever 68 intermediate the ends thereof by a pin 73. The other end of the lever 71 is pivotally carried on one portion of the boom 30 by a pin 60. The head end of the hydraulic cylinder 56 `is pivotally connected to the lever 71 by a pin 61 which is located on the lever 71 between the pins 60 and 72. The rod end of the hydraulic cylinder 56 is pivotally carried on one portion of the boom 30 by a pin 62 which is located on that portion of the boom 39 forwardly of the pin 60.

The various described members of the second embodiment of the bucket pivoting arrangement are so formed and positioned that when the

hydraulic cylinders

54 and 56 are substantially completely retracted, the bucket 4S is positioned in the digging position at ground level as shown in FIGURE 9. If the .hydraulic cylinder 54 is then extended, the lever 68 will be pivoted in a clockwise direction as viewed in FIGURE 9 to pivot the bell crank 53 through the link 66 in a counter-clockwise direction from the position shown in FIGURE 9 to one wherein the bucket is pivotally positioned such as shown, for example, in FIGURE 3. If the hydraulic cylinder 56 is then extended, the lever 71 will be pivoted in a counterclockwise direction as shown in FIGURE 9 to further pivot the bucket v45 through the lever 68, the link 66, and the bell crank 53, to fthe dump posi-tion such as shown, for example, in FIGURE 6. The second embodiment of the bucket pivoting arrangement differs from the rst in that the large end of the piston of the hydraulic cylinder 54 is used in the break-out and initial dumping action of the bucket 45, and further in that the force and speed of the bucket in pivoting may be varied by different relative locations of the

pins

69, 73 and 70 on the lever 68.

Turning next to the means for operating the various elements of the machine, the crawler mechanism l0, the

hydraulic cylinders

20 and 21 of the conveyor mechanism 12, and the

hydraulic cylinders

4l, 54 and 56 are operated by any suitable power means (not shown). The main motor 75 which may be seen i-n FIGURE 1 supplies power for the sprockets 38. The motor 75 is mounted upon the frame 11 and its output shaft delivers power to a transmission 76. The output of the transmission 16 s connected in parallel -to a speed-reducer 77 land to the hydraulic tluid pump 78 shown in FIGURE 8. Two

clutches

79 and 80 are associated with the output shaft of the speed-reducer 77 and will drive the output shaft in either direction depending upon which clutch is operated. The output shaft or" `the speed-reducer 77 is further connected to a worm-type speed reducer 8l. The speed rcducer 8l, which as shown in FIGURES l and 2 is 7 mounted on the frame 11 with its output shaft extending transversely of the machine and connected in driving relationship to the sprockets 38 on each side of the machine. It may thus be seen that when one of the `

clutches

79 or 80 `is energized, the speed reducer 81 is operated to drive the sprockets 38 in one direction; and when the other of the

clutches

79 or 80 is operated, the speed reducer 81 is operated to drive the sprockets 38 in an opposite direction.

Referring to FIGURES 3 land 8,

live control assemblies

83, 84, 85, 86 and 87 are employed. The first assembly 83 is shown in FIGURE 8 as a hydraulic valve. Asscmbly 84 is another hydraulic valve similar to valve 83 and is provided for operation of the hydraulic cylinders 56. The hydraulic valve 84 is connected by suitable conduits to a pressure source (not shown), `a reservoir (not shown), and to the hydraulic cylinders 56. The assembly 85 is also a hydraulic control valve and is provided for operation of the hydraulic cylinders 54. The hydraulic control valve 85 is connected by suitable conduits to a hydraulic lluid pump and reservoir (not shown), and to the hydraulic cylinders 54. The

control assemblies

86 and 87 are provided for controlling the operation of the crawler track mechanism 10. These

control assemblies

86 and 87 may be connected by any suitable means (not shown) to the driving elements of the crawler track mechanism 10. Any suitable means known in the art (not shown) may be provided for controlling the operation of the

hydraulic cylinders

20, 21 and 41.

As shown in FIGURE 8, the low pressure side ofthe hydraulic uid pump 78 is connected to the reservoir 88 by conduit 90. The high pressure side of the hydraulic fluid pump 78 is connected to passageway 91 in valve 83 by conduit 92. The valve spool 93 of valve 83 is provided with three annular groove-

s

94, 95 and 96 separated by two annular lands 97 and 98 and is biased to the neutral position shown in FIGURE 8 by the spring assembly 99. In `addition to the passageway 91, the valve body is provided with two annular grooves and 101 respectively connected to the

conduits

102 and 103, a passageway 104 connected to a conduit 105, and a check valve 106 formed in passageway 91 between the connection of conduit 92 thereto and an annular groove 107. The check valve 106 will permit hydraulic fluid flow from passageway 91 to annular groove 107, but will prevent any hydraulic tluid flow in the reverse direction. When the valve 83 is in the neutral position shown in FIGURE 8, hydraulic [luid from conduit 92 will how through passageway 91 `about the annular groove 96 of the valve spool 93, through passageway 104 to conduit 105. From conduit 105 the hydraulic tluid will ow through

conduits

108 and 109 to reservoir 88. In the neutral position, land 97 of the valve spool 93 will seal hydraulic huid from the

annular grooves

100 and 101 of the valve body, and hydraulic

lluid conduits

102 and 103 are vented to the reservoir 88 through

annular grooves

100 and 101 of the valve body, annular grooves 94 and 95 of the valve spool 93, and passageway 104 to and through

conduits

105, 108 and 109. When the valve spool 93 is moved inwardly of the valve body, land 98 of the valve spool 93 Will block passageway 91 from passageway 104. High pressure hydraulic tluid will then ow through the check valve 106, annular groove 107 of the valve body, annular groove 94 of the valve spool 93, `annular groove 100 of the valve body and through conduit 102. Conduit 103 will remain vented to the reservoir 88. When the valve spool 93 is moved outwardly of the valve body, passageway 91 is again blocked from fluid communication with passageway 104 iby a land on the inner end of the valve `spool 93. High pressure hydraulic lluid will then flow from passage- Way 91 through check valve 106, through annular groove 107 of the valve body, through `annular groove 95 of the valve spool 93, through annular groove 101 of the valve body and through. conduit 103. The conduit 102 will be vented over the circuit previously described. Thus, it may be seen that when valve spool 93 is in the u cylinder 8 neutral position fluid flows through the valve 83 to reservoir 88 and

conduits

102 and 103 are vented. When spool 93 is moved in and out respectively, high pressure fluid flows to conduit 102 while conduit 103 is vented; and lluid flows to conduit 103 and conduit 102 is vented.

Conduit 102. is connected to conduit 110 which is connected to a cylinder 111. Conduit 110 is connected to a valve 112. Cylinder 111 is connected by a lever 113 to clutch 79 ol speed reducer 77 so that when the cylinder 111 is extended, clutch '79 is operated. Valve 112 has a spool spring-biased to block conduit 110 from the outlet port connected to conduit 114. Conduit 114 also connects to conduit 109. Valve 112 is carried on the frame 11 and is positioned at the forward end of the chain 37 with the valve spool aligned so the slide member 32, carrying the rear end of the boom 30, will engage the spool of the valve 112 when the slide member 32 is moved to its forwardmost position by the chain 37. The slide member 32 will then operate the valve 112 to provide free fluid flow from conduit 110 to conduit 114.

Similarly to conduit 102, conduit 103 is connected in parallel to a cylinder 115 and a valve 116. The cylinder 115 is connected to operate the clutch 80 of the speed reducer 77 through a lever arrangement 117. The outlet port of the valve 116, which is identical in construction to valve 112, is connected to conduit by means of conduit 118. The valve 116 is on one side of the machine at a position where the valve spool thereof can interconnect conduits 103 and 118 When the slide member 32 is moved to its rearwardmost position by the chain 37. The system for the boom 30 further includes a pressure relief valve 1.19 which is connected between conduits 92 and 108 and which will operate to by-pass Huid from the high pressure side of the pump 78 to the reservoir 88 whenever the pressure in conduit 92 exceeds a certain predetermined amount.

Considering the operation of thc hydraulic system for the boom 30 and assuming the spool 93 is moved inwardly of the body of valve 83, the high pressure fluid in conduit 102 will operate cylinder 111 which in turn operates clutch 79 of speed `reducer 77. This causes the speed reducer 77 to rotate sprockets 38 in a clockwise direction as viewed in FIGURE 8. This moves the chain 37 which in turn moves the slide members 32 forwardly. As the slide members 32 move forwardly, the boom 30 will be carried forwardly as previously described, and if the valve spo-ol 93 is held inwardly until the slide member 32 reaches its forwardmost position, the valve 112 will be operated to permit the high pressure fluid in conduit to ow through conduits 11.4 and 109 to the reservoir 88. This venting of huid from conduit 110 will permit the clutch 79 to be disengaged thereby stopping the drive to the sprockets 38. If the valve spool 93 is moved outwardly of the valve body of the valve 83, the high pressure hydraulic lluid then directed through conduit 103 will operate the hydraulic cylinder 115 to in turn cause an operation of the clutch 80 which will in turn cause power to be delivered to the sprockets 38 to rotate the sprockets 38 in a counter-clockwise direction as viewed in FIGURE 8 to move the boom rearwardly relative to the machine. When the slide member 32 and the boom 30 reach their rearwardmost position, the slide member 32 will operate the hydraulic valve 116 to vent high pressure hydraulic fluid from the hydraulic through

conduits

118, 105, 108 and 109 to the reservoir 88. With the high pressure hydraulic fluid vented from hydraulic cylinder 115, clutch 80 will be disengaged and the drive to the sprockets 38 will be disconnected. It is, of course, not necessary that the slide member 32 be moved only from one extreme position to the other since by operating the valve spool 93 of the valve 83 to the neutral position any high pressure hydraulic fluid in the

conduits

102 and 103 is vented to the reservoir 88 to thereby cause disengagement of either 9 of the

clutches

79 or 80 and stopping the boom 3G in any selected intermediate position.

Turning next to a brief description of the operation of the instant invention in order that the construction thereof may be more readily understood, reference is again made to FIGURES 2, 3, 6, 7 and 9 of the drawings. With the

hydraulic cylinders

54 and 56 of either embodiment of the present invention operated so that the bucket 45 is positioned such as shown in FIGURE 2, the crawler track mechanism 10 may be operated to position the bucket 45 immediately before a pile of material to be rem-oved. With the crawler track mechanism then stopped, and with the conveyor mechanism 12 then operating and having its rearward end dispos-:d over a shuttle car or some other conveyor means, the hydraulic system previously described may be operated to slide the boom forward. The bucket 45 and the digging teeth or edge thereof Will then be projected into the pile of material to be removed (FiGURE 7). Because one leg of the bell crank 53 engages the underside of the stop S1, the bucket in moving forwardly may easily slide over any obstructions at ground lever. When the bucket 45 is substantially filled with the material to be removed, the hydraulic cylinders 54 are operated to cause the loaded bucket 45 to break away the material in the bucket 45 from that remaining in the pile and further ll the bucket in a scooping action. Operation of the hydraulic cylinders 56 will then cause the load in the bucket to be dumped therefrom over the rear Wall 48 of the bucket 45 onto the forward section 13 of the conveyor mechanism 12. The conveyor mechanism 12 will then carry that material rearwardly of the machine. As the pile immediately in front of the machine is removed, the boom 30 may be gradually moved forwardly without moving the machine is working the face of the pile such 7. Only when the face of the beyond the forwardmost reach of bucket 45 need the crawler track be operated to move thc machine in close proximity to the pile. The described digging operations need not be performed only at the ground level of the machine. By suitable extensions of the hydraulic cylinders 41, the bucket 45 may be caused to dig at higher levels.

1n the modilication of the invention illustrated in FIG- URES l to 15 inclusive, the same part numbers will be applied to the same parts as in the first and second forms of the invention.

In FIGURES and l1, the main frame 11 is shown as being mounted on rubber tire mounted traction wheels 25 instead of the continuous crawler track mechanisms 10. The traction wheels 125 serve to propel the machine along the ground and to crowd the digger bucket 45 into the material to be loaded and are driven in a manner similar to that shown and described in my application Serial No. 9,501, filed February 18, 1960 `and entitled Rock Loading Machine. The four traction wheels and drive to said traction wheels, therefore, need not herein be shown lor described further.

The bucket 45 is directly connected to the main frame 11 for vertical and angular movement with respect thereto, to be crowded into the mined material by movement of said main frame toward the mined material by the tractive effort of the traction wheels 125, on a boom structure 126. The boom structure 126 includes boom arms 127 extending along each side of the forward wall portions 1:6 and 17 of the conveyor mechanism 12 and beyond the forward ends thereof and connected together at their forward ends by a cross tube 129. The boom arms 127 are pivotally mounted at their rear end-s on the outsides of the

wall portions

16 and 17 on support structures 130, on pivot pins 131 mounted at their outer ends on blocks 133, welded or otherwise secured `to said support structures. The pivot pins 131 also form pivotal mountings for actuating levers 135 for the bucket 45.

as shown in FIGURE pile has been moved the boom 30 and the mechanism 10 again itself until the bucket n Each boom arm 127 is adjustably supported adjacent the forward end of the conveyor mechanism 12 on a hydraulic cylinder 136 trunnioned adjacent its lower end in a support 137 extending laterally from the main frame 11, on trunnion pins 139. The hydraulic cylinder 137 has a piston rod 140 extensible therefrom, shown in FIGURE l2 as being threaded through a transverse pin 141 pivotally mounted at its ends in parallel spaced arm portions 143 and 144 of the boom arm 127. The inner arm portion 144 of the `boom arm 127 has a depending leg portion 145 extending inwardly of the hydraulic cylinder 136 in a downward direction for a portion of the length of said hydraulic cylinder and having a bearing plate 146 on the side thereof adjacent the conveyor mechanism 12, having slidable bearing engagement with a bearing plate 147 extending vertically of the conveyor mechanism 12 and shown in FIGURE l2 as being secured thereto. The bearing plates 146 and 147 have sliding contact with each other and serve to limit lateral displacement of the 'boom structure 126 during operation of the digger bucket 45 and to provide slidable engaging surfaces for the boom structure during vertical adjustment thereof by operation of the hydraulic cylinders 136.

The digger bucket 45 is transversely pivoted to the forward end portion of the boom structure 126 on laterally spaced ears 149 extending rearwardly from the side walls 46 of said digger bucket. As shown in FIGURE 13, the ears 149 are pivotally mounted on transverse pivot pins 150 on bearings 151. Each pivot pin 150 is mounted at one end on the arm portion 127 of the boom structure 126 and at its opposite end on a lug 153 extending upwardly from the tube 129 inwardly of the boom arm portion 127 and welded or otherwise secured tothe transverse tube 129. Nuts and washers 154 are threaded on opposite ends of the pivot pin 15) to retain said pin in position.

A bell crank 155, similar to the bei] crank 53 is pivotally mounted on each side wall 46 of the `bucket 45 on a pivot pin .157. The bell crank 155 `has a depending arm or leg having an engaging end portion 158 engagcable with the stop member 51 extending outwardly from the side wall 46 of the bucket 45 when the bell crank is pivoted in `a counter clockwise direction to pivot the fbucket 45 upwardly about the axis of the pivot pin 150. It ywill be noted from FIGURE l() that the operative connection from the `hell crank 155 to the bucket 45 is such that the bucket may pivot upwardly relative to the engaging face 158 when being crowded into the loose material during the loading operation, to accommodate the bucket to ride along uneven ground and over high spots on the ground free from the bell crank 155.

The bell crank 155 also has an upwardly extending leg or lever arm 159 having :a clevis 160 of an adjustable link 161, pivotaily connected to its upper end on a pivot pin 162 extending through said clevis and lever arm. The opposite end of the link 161 has a clevi-s 163 threaded thereon and extending along opposite sides of the actuating lever 135 and pivotally connected therewith on a ball 164 mounted on a pivot pin 165 mounted in said clevis at its ends (FIGURES l() and 15).

The actuating lever 135 is actuated by a Ahydraulic cylinder 166 having a piston rod 167 exten-sible therefrom. The hydraulic cylinder 166 has a connector 16S extending from the head end thereof between the arm portions 143 and 144 of the boom arm 127 and pivotally connected thereto on a pivot pin 169.

The piston rod 167 extends between connector plates 170 welded or otherwise secured to opposite sides of the actuator lever 135 intermediate the ends thereof, and is pivotally connected to said actuator plates by pivot pin 171.

In describing the operation of the mechanism of FIG- URES l0 and ll, the mechanism on only one side of the machine will herein be referred to, for the purpose of simplicity. 1n these Figures, the axis of connection 1 1 of the link 161 to the actuator 135 is designated by A. The axis of the pivot pin 157 is designated by B and the axis of connection of the ear 149 to the boom 127 on the pivot pin 150 is designated by C. The axis of connection of the link 161 to the lever arm 159 of the bellcrank 155 is designated by D.

As iluid under pressure is admitted to the head end of the cylinder 166 to extend the piston rod 167 therefrom, the bellcrank 155 will initially pivot upwardly about axis B and engage the engaging end portion 158 of said bellcrank 155 with the stop 51 and then pivot the bucket 45 upwardly. During initial upward pivotal movement of the bucket 45, the moment arm supplying the force to raise the bucket and tear the bucket from rock piled thereon will be from D to C, the weight ofthe bucket and rock thereon will hold the link 161 and lever arm 159 in angularly disposed relation with respect to each other. The bellcrank 155, stop 51 and bucket 46 will then move upwardly as a unit. As the pull on the lever arm 159 causes 161 and 159 to approach a straightened condition, however, 161 and 159 will then act as a pulling link and the bucket will continue its upward movement about point C. The moment arm will then be reduced to the distance from B to C. As the bucket is pivoted upwardly about the shorter moment arm the lever arm 159 will engage a camming face 164 on the boom arm 127, preventing the link 161 `and lever arm 159 from straightening out or moving past a dead center position. The bucket 45 will then pivot relatively to the bellcrank 155 and the stop 5l will move away from the engaging end portion 153 of said bellcrank.

During movement of the bucket from the broken line position shown in FIGURE l1 to the solid line discharge position shown, the speed of travel of the bucket moving about the shortened moment arm will materially increase and the bucket will move upwardly to its discharge position at a relatively high rate of speed until the stop 51 engages the lever arm 159 of the bellcrank 1557 stopping movement of the bucket and jarring the loose material therein to fall onto the conveyor 24.

During lowering of the bucket, fluid under pressure is admitted to the piston rod end of the cylinder 166, pivoting the bucket in a downward direction about the moment arm D-C. llfhe link 161 and lever arm 159 will then move angularly with respect to each other until gravity takes over and the stop 51. comes into engagement with the engaging end portion 153 of the bellcrank 155. Continued lowering movement of the bucket into the gathering position shown in FIGURE will then be under the control of the cylinder 166 and piston rod 167.

It will `also be noted that tbe stop 51, while accommodating relatively free upward movement of the digger bucket during the operation of crowding said digger bucket in the material being loaded, may also be positively engaged with the arm 159 of the bell crank 155 as the digger bucket is moved to its discharge position and serves to jar moist material from the digger bucket, the link 161 and lever arm 159 holding the digger bucket in its discharge position until the piston rod 167 is retractihly moved with respect to the hydraulic cylinder 166, to move the digger bucket to a loading position.

The free connection between the bell crank 155 and the digger bucket 45, thus besides accommodating the digger bucket to freely ride along rises on the ground without affecting the operating mechanism for the bucket, also serves `as a stop for the digger bucket when in its discharge position and engages the arm 159 with a jarring action, to jar any `moist material in the bucket to flow downwardly therealong onto the receiving end portion of the conveyor mechanism 12.

While I have herein shown and described various forms in which my invention may be embodied, it should be understood that various other variations and modifications in the invention may be attained without departing from the spirit and scope of thc novel concepts thereof as defined by the claims appended hereto.

I claim as my invention:

l. In a loading machine, a mobile frame, a conveyor extending along said frame from a position adjacent the ground at the forward end thereof and fixed from vertical movement with respect to said frame at its forward end, a boom transversely pivoted to said frame rearwardly of the forward end thereof and extending in advance of said frame, hydraulic cylinder and piston means supporting the forward end of said boom on said frame and vertically adjusting said boom about its axis of pivotal connection to said trame, a digger bucket transversely pivoted to the forward end of said boom and extending in advance thereof for slidable engagement with the ground, a bellcrank pivotally connected to one side of said digger bucket intermediate its ends and having depending and upwardly extending lever arms, a stop projecting outwardly from the side of said bucket between said arms of said bellcrank for engagement therewith, a pivoted actuating lever having two angularly extending arms, means pivotally mounting said actuating lever on said frame at the end of one arm thereof, hydraulic cylinder and piston means pivotally connected between said boom and said actuating lever adjacent the juncture of said arms, whereby an upper of said arms extends generally along said hydraulic cylinder and piston means, and linkage means connecting the free end of the upper of said arms with the upwardly extending arm of said bellcrank, to pivot said bellcrank to engage said stop and swing said bucket upwardly from a loading to a dumping position.

fl. A. loading machine in accordance with claim l, wherein the actuating lever is pivoted to the frame coaxially with the axis of pivotal connection of the boom to the frame and wherein the linkage means is extensible and retractible to vary the angular relation of the digger bucket with respect to the ground.

3. ln a loading machine, a mobile frame, a conveyor extending along said frame and having a forward receiving end at a Fixed elevation with respect to the ground, a boom transversely pivoted to said frame rearwardly of the forward end thereof and extending in advance of said frame, a digger bucket transversely pivoted to the forward end of said boom and depending from said boom into engagement with the ground, means for holding said boom in position and vertically adjustably moving said boom with respect to the ground, a bellcrank transversely pivoted to one side of said digger bucket for movement about an axis spaced beneath and forwardly of the axis of pivotal connection of said digger bucket to said boom when seid digger bucket is in engagement with the ground, a stop projecting laterally of said digger bucket, said bellcrank having a lever arm depending from its axis of connection to said digger bucket and extending underneath said stop when said digger bucket is in engagement with the ground and having a second upright lever arm extending upwardly of the axis of connection of said bellcrank to said digger bucket, an actuating lever transversely pivoted to said frame and extending upwardly of its axis of pivotal connection to said frame, an extensible and retractible operating member transversely pivoted to said boom and pivot-ally connected with said actuating lever intermediate the ends of said actuating lever, a rigid tink, a transverse pivot pin connecting one end of said link to the free end of said actuating lever, a second transverse pivot pin connecting the opposite end of said link with the upright arm of said bcllcrank, the relationship between the axis of connection of said bucket to seid boom. said bellcrank to said bucket and the axes of said pivot pins being such that when said bucket is in depending relation with respect to said boom, the weight of said bucket and the rock loaded thereon will engage said stop with said depending arm of said bellcrank and effect initial upward movement of said bucket about a lever :um equal to the distance between the axis ol connection of said bucket to said boom and the axis of said pivot pin connecting said link to the upright arm of said bellcrank, and as said bucket moves toward a discharge position, said link and the upright arm of said bellcrank will move into aligned relation with each other and pivot said bucket to a discharge position about a shorter moment arm equal to the distance between the axis of connection of said bucket to said boom and said bellcrank to said bucket and move said stop away from said depending lever arm of said bucket.

4. A loading machine in accordance with claim 3, wherein said boom has a camming face thereon engageable with said upright arm of said bellcrank and retaining said link and upright arm from moving past dead center positions with respect to each other as said bucket moves to its discharge position.

`5. In a loading machine, a mobile frame, a conveyor extending along said frame and having a forward receiving end in fixed relation with respect to said frame, a boom transversely pivoted to said frame rearwardly of the forward end thereof and extending in advance of said frame, means for retaining said boom in position and vertically moving said boom with respect to said frame, a digger bucket transversely pivoted to the forward end of said boom and extending in advance thereof for slidable engagement with the ground, an extensible and retractible operating member pivotally connected to said boom, an actuating lever transversely pivoted to said frame, an operative connection between said operating member and said actuating lever, linkage means connecting the free end of said actuating lever with said digger `bucket to effect upward movement of said digger bucket from a digging to a discharge position, bearing plates extending vertically along the outer sides of said conveyor, other bearing plates extending vertically along the inner sides of said boom and having slidable engagement with said rst mentioned bearing plates to retain said boom from lateral shifting movement in all positions of elevation thereof with respect to the ground.

6. A loading machine in accordance with claim 5, wherein the boom includes two parallel spaced boom arms extending along opposite sides of the conveyor and connected together in advance of the forward end of the conveyor, wherein the boom arms are adjustably -Io oijneJpq uo spun plainte; .Iraqi zuaoeipe pazloddns inders and pistons operative to raise and lower said boom arms about their axes of pivotal connection to said frame, and wherein the bearing plates extending vertically along the inner sides of the boom, are mounted on the boom arms adjacent the forward ends thereof, and the bearing plates extending vertically along opposite sides of the conveyor are adjacent the forward end of the conveyor.

7. In a loading machine, a mobile frame, a conveyor extending along said frame and having a forward receiving end portion xed with respect to said frame, a boom transversely pivoted to said frame rearwardly of the forward end thereof and extending in advance of said frame, hydraulic cylinder and piston means supporting the forward end of said boom on said frame and vertically adjusting said boom about its axis of pivotal connection to said frame, a digger bucket transversely pivoted to the forward end of said boom and extending in advance thereof for slidable engagement with the ground, a bellcrank pivotally connected `to one side of said digger bucket intermediate its ends and having depending and upwardly extending lever arms, a stop projecting outwardly from the side of said digger bucket between said arms of said bellcrank, an actuating lever pivoted to said frame coaxial with the axis of pivotal connection of said boom to said frame, said actuating lever having two angularly extending arms extending vertically of the axis of said actuating lever to said frame, hydraulic cylinder and piston means pivotally connected between said boom and said actuating lever adjacent the juncture of said arms, whereby an upper of said arms extends generally along said hydraulic cylinder and piston means, and a rigid link connecting the free end of the upper of said arms with the upwardly extending arm of said bellcrank for actuating said bellcrank upon operation of said actuating lever to swing said bucket upwardly from a loading to a dumping position.

References Cited in the tile of this patent UNITED STATES PATENTS 1,739,624 Whamond Dec. 17, 1929 1,797,459 Whaley Mar. 24, 1931 1,814,067 Whaley July 14, 1931 2,530,714 McDougall Nov. 21, 1950 2,619,243 Biedess Nov. 25, 1952 2,714,459 Hay Aug. 2, 1955 2,768,499 Pilch Oct. 3G, 1956

Claims

3. IN A LOADING MACHINE, A MOBILE FRAME, A CONVEYOR EXTENDING ALONG SAID FRAME AND HAVING A FORWARD RECEIVING END AT A FIXED ELEVATION WITH RESPECT TO THE GROUND, A BOOM TRANSVERSELY PIVOTED TO SAID FRAME REARWARDLY OF THE FORWARD END THEREOF AND EXTENDING IN ADVANCE OF SAID FRAME, A DIGGER BUCKET TRANSVERSELY PIVOTED TO THE FORWARD END OF SAID BOOM AND DEPENDING FROM SAID BOOM INTO ENGAGEMENT WITH THE GROUND, MEANS FOR HOLDING SAID BOOM IN POSITION AND VERTICALLY ADJUSTABLY MOVING SAID BOOM WITH RESPECT TO THE GROUND, A BELLCRANK TRANSVERSELY PIVOTED TO ONE SIDE OF SAID DIGGER BUCKET FOR MOVEMENT ABOUT AN AXIS SPACED BENEATH AND FORWARDLY OF THE AXIS OF PIVOTAL CONNECTION OF SAID DIGGER BUCKET TO SAID BOOM WHEN THE DIGGER BUCKET IS IN ENGAGEMENT WITH THE GROUNG, A STOP PROJECTING LATERALLY OF SAID DIGGER BUCKET, SAID BELLCRANK HAVING A LEVER ARM DEPENDING FROM ITS AXIS OF CONNECTION TO SAID DIGGER BUCKET AND EXTENDING UNDERNEATH SAID STOP WHEN SAID DIGGER BUCKET IS IN ENGAGEMENT WITH THE GROUNG AND HAVING A SECOND UPRIGHT LEVER ARM EXTENDING UPWARDLY OF THE AXIS OF CONNECTION OF SAID BELLCRANK TO SAID DIGGER BUCKET, AN ACTUATING LEVER TRANSVERSELY PIVOTED TO SAID FRAME AND EXTENDING UPWARDLY OF ITS AXIS OF PIVOTAL CONNECTION TO SAID FRAME, AN EXTENSIBLE AND RETRACTIBLE OPERATING MEMBER TRANSVERSELY PIVOTED TO SAID BOOM AND PIVOTALLY CONNECTED WITH SAID ACTUATING