US3096893A - Loading machine - Google Patents

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 theline 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 orcrawler 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. Amain 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.

Theconveyor 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 theframe 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. Theconveyor mechanism 12, as herein shown includes three interconnected trough shapedSections 13, 14 and 1.5. Theforward section 13 forms a material receiving and inclined elevating section and may be tixedly mounted upon themain frame 11. Oppositeforward wall portions 16 and 17 of theforward section 13 are inclined outwardly toward the sides of the machine and with an upwardly extending forward inclinedforward wall 18 define a hopper for receiving the material dumped thereonto. The center section 14 of theconveyor mechanism 12 is joined to the rearward end of theforward scction 13 through pivotal mounting means 19. of the center section 14 about a horizontal axis with respect to theforward 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 theconveyor mechanism 12. Thus it may be seen that when thehydranlic cylinder 20 is extended therearward section 15 of theconveyor mechanism 12 are pivoted upwardly about the horizontal axis of pivotal mounting means 19, and when thehydraulic cylinder 20 iS retracted the-se sections 14 and 1.5 are pivoted downwardly about the same axis. Thehydraulic cylinder 20 permits vertical adjustment of the rearward end of theconveyor mechanism 12 relative to a shuttle car or other conveyor system for efiicient transfer of any load of material from theconveyor mechanism 12.Hydraulic cylinders 21 are provided for adjustably maintaining therearward section 15 in any angled position relative to the center section 14 in a horizontal plane. The head end of each of thehydraulic cylinders 21 is pivotally connected to abracket 22 carried on the sidewalls of the center section 14. The rod end of each of thehydraulic cylinders 21 is pivotally connected to the sidewalls of therearward section 15 through pivotal mounting means 23. Thus, it may be seen when one of thehydraulic cylinders 21 is extended, therearward section 15 of theconveyor mechanism 12 is caused to pivot relative to the center section .t4 in a horilivotal mounting means 19 permit pivotal movement i thecenter section 14 and 30, the underside zontal plane, this pivoting causing retraction of the oppositehydraulic cylinder 21.

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

Turning next to the means for loading theconveyor mechanism 12, aboom 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 theboom 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 theboom 30 is pivotally connected to aslide member 32. As may be seen in FIGURES 3 and 4 eachslide 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 theboom 30 is pivotally connected to the upstanding llange of one of theslide members 32 by means of apin 33. The H- shaped section of eachslide member 32 engages a pair ofopposed rails 34 and 35. Each pair ofrails 34 and 35 is secured to theframe 11 on one side of the machine by a plurality of bolts such asbolt 36 shown in FIGURE 4. The depending flange of eachslide member 32 is connected with achain 37 between one pair of the links thereof. Eachchain 37 passes in opposite directions from the depending flange about adrive sprocket 38 and anidler 39. The ends of thechain 37 are interconnected by a suitable turnbuckle orcoupling 40. Eachsprocket 38 is rotatively mounted on one side of theframe 11 toward the rear thereof and each idler 39 is rotatively mounted on one side of theframe 11 toward the front thereof.

Each portion of theboom 30 is slidably supported at the forward end of the machine by anindividual cylinder 41. Eachcylinder 41 is carried on one side of theframe 11 at the forward end thereof and immediately below one portion of theboom 30. The piston rod of eachcylinder 41 is provided with ashoe 42 pivotally connected thereto by means of apin 43. Eachshoe 42 is positioned in cooperation with the underside of one portion of the boom of each portion of theboom 30 having a rail configuration conforming to the shape of theshoes 42.

From the foregoing description it may be seen that when the `sprocket 38 is rotated clock-wise as viewed in the drawings, thechain 37 will be moved to in turn move theslide member 32, which in turn will cause `theboom 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 thesprocket 38 is rotated in a counterclockwise direction theboom 30 is moved rearwardly relative to the machine. It may further be seen that when thehydraulic cylinders 41 are extended, the forward end of theboom 30 is pivoted upwardly about the axis ofpins 33 and when thehydraulic cylinders 41 are retracted the forward end of the boom is lowered. The means for operating thesprockets 38 and thehydraulic cylinders 41 will be described below.

Turning next to a detailed description of the bucket arrangement for the rst embodiment of the present invention, thebucket 45 comprises a pair of spaced-apartsidewalls 46 interconnected by abottom wall 47 and aback wall 48. The forward marginal edge of thebottom wall 47 is provided with suitable digging teeth. Eachside wall 46 of thebucket 45 is provided with amember 49 having a rearwardly extending ear orflange 50 and an outwardly extendingstop member 51. Thebucket 45 is pivotally carried on depending leg portions 44 of theboom 30 by means of a pair ofpins 52, eachpin 52 being carried by one of the depending leg portions of the `boom 30 and iournalled through one of theears 50 of themembers 49. The axis of pivoting of thebucket 45 about thepins 52 is such that when thebucket 45 is pivoted completely counter-clockwise as viewed in the drawings, thebucket 45 is moved into theforward section 13 of theconveyor mechanism 12 with the upper portions of the rear wall 4S and theside walls 46 positioned in the hopper defined by theside walls 16 and 17 and theforward wall 18 of theforward section 13 of theconveyor mechanism 12 as may easily be seen in FIGURE 6.

To pivot thebucket 45 to its various operative positions, abell crank 53, ahydraulic cylinder 54, alever 55 and ahydraulic cylinder 56 are provided for each side arm of theboom 30 and each side of thebucket 45. Since these elements are formed in duplicate only those of one side arm of the boom and one side of thebucket 45 are here described. Thebell crank 53 is pivotally carried on themember 49 by apin 57. The pivot axis of thepin 57 is located on themember 49 so that one leg or lever arm of the bell crank will engage ethe underside of thestop 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 thehydraulic cylinder 54 by apin 58. The head end of thehydraulic cylinder 54 is pivotally connected to one end of thelever 55 by apin 59, and the other end of thelever 55 is pivotally carried on the horizontal portion of theboom 30 by apin 60. The head end of thehydraulic cylinder 56 is pivotally connected to thelever 55 intermediate the ends thereof by apin 61, and the rod end of thehydraulic cylinder 56 is pivotally connected to the horizontal portion of theboom 30 by apin 62 located thereon forwardly of thepin 60. Thehydraulic cylinders 54 and 56 are of such a size, and thelever 55 and the bell crank 53 are of such a length, that when thehydraulic cylinder 56 is substantially completely retracted and thehydraulic cylinder 54 is substantially completely extended, thebucket 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 thehydraulic cylinder 54 is retracted, the one lever arm bell crank 53 will engage thestop member 51 to pivot thebucket 45 rearwardly from the position shown in FIGURE 2 to that shown in FIG- URE 3, and if thehydraulic cylinder 56 is then extended, thelever 55 will be moved counter-clockwise as viewed in the drawings to move thehydraulic cylinder 54 and thebucket 45 through the bell crank 53 and thestop 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 thebell 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, thehydraulic cylinder 54 will act through a relatively long moment arm to exert an initially relatively powerful lifting or breakout force on thebucket 45, and since thereafter in the further retraction of thehydraulic cylinder 54 the moment arm is decreased, the pivoting of thebucket 45 will occur at increasing speeds.

In the second embodiment of the means for pivoting thebucket 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, thebucket 45 is pivotally carried on the depending portions of theboom 30 bypins 52 andmembers 49. Since the bucket pivoting arrangement is formed in duplicate for each portion of theboom 30 and on each side of the bucket 4S, again, only those members on one side thereof Will be described. Thebell crank 53 is pivotally carried on themember 49 by apin 57. One leg or lever arm of the bell crank 53 is positioned to engage thestop 51 as in the previously described embodiment. Theother lever arm 65 of the bell crank 53 which is relatively longer than the lirst mentioned lever arm or leg is pivotally connected to alink 66 by a pin 67. The other end of thelink 66 is pivotally connected to one end of alever 68 by apin 69. The other end of thelever 68 is pivotally connected to the rod end of thehydraulic cylinder 54 by a pin 7l). 'I'lie head end of lthehydraulic 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 thelever 68 intermediate the ends thereof by apin 73. The other end of the lever 71 is pivotally carried on one portion of theboom 30 by apin 60. The head end of thehydraulic cylinder 56 `is pivotally connected to the lever 71 by apin 61 which is located on the lever 71 between thepins 60 and 72. The rod end of thehydraulic cylinder 56 is pivotally carried on one portion of theboom 30 by apin 62 which is located on that portion of theboom 39 forwardly of thepin 60.

The various described members of the second embodiment of the bucket pivoting arrangement are so formed and positioned that when thehydraulic 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, thelever 68 will be pivoted in a clockwise direction as viewed in FIGURE 9 to pivot the bell crank 53 through thelink 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 thehydraulic 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 thelever 68, thelink 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 thehydraulic cylinder 54 is used in the break-out and initial dumping action of thebucket 45, and further in that the force and speed of the bucket in pivoting may be varied by different relative locations of thepins 69, 73 and 70 on thelever 68.

Turning next to the means for operating the various elements of the machine, the crawler mechanism l0, thehydraulic cylinders 20 and 21 of theconveyor mechanism 12, and thehydraulic cylinders 4l, 54 and 56 are operated by any suitable power means (not shown). Themain motor 75 which may be seen i-n FIGURE 1 supplies power for thesprockets 38. Themotor 75 is mounted upon theframe 11 and its output shaft delivers power to atransmission 76. The output of the transmission 16 s connected in parallel -to a speed-reducer 77 land to thehydraulic tluid pump 78 shown in FIGURE 8. Twoclutches 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 theframe 11 with its output shaft extending transversely of the machine and connected in driving relationship to thesprockets 38 on each side of the machine. It may thus be seen that when one of the `clutches 79 or 80 `is energized, thespeed reducer 81 is operated to drive thesprockets 38 in one direction; and when the other of theclutches 79 or 80 is operated, thespeed reducer 81 is operated to drive thesprockets 38 in an opposite direction.

Referring to FIGURES 3 land 8,live control assemblies 83, 84, 85, 86 and 87 are employed. Thefirst assembly 83 is shown in FIGURE 8 as a hydraulic valve.Asscmbly 84 is another hydraulic valve similar tovalve 83 and is provided for operation of thehydraulic cylinders 56. Thehydraulic valve 84 is connected by suitable conduits to a pressure source (not shown), `a reservoir (not shown), and to thehydraulic cylinders 56. Theassembly 85 is also a hydraulic control valve and is provided for operation of thehydraulic cylinders 54. Thehydraulic control valve 85 is connected by suitable conduits to a hydraulic lluid pump and reservoir (not shown), and to thehydraulic cylinders 54. Thecontrol assemblies 86 and 87 are provided for controlling the operation of thecrawler track mechanism 10. Thesecontrol assemblies 86 and 87 may be connected by any suitable means (not shown) to the driving elements of thecrawler track mechanism 10. Any suitable means known in the art (not shown) may be provided for controlling the operation of thehydraulic cylinders 20, 21 and 41.

As shown in FIGURE 8, the low pressure side ofthehydraulic uid pump 78 is connected to thereservoir 88 byconduit 90. The high pressure side of thehydraulic fluid pump 78 is connected to passageway 91 invalve 83 by conduit 92. Thevalve spool 93 ofvalve 83 is provided with three annular groove-s 94, 95 and 96 separated by twoannular 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 theconduits 102 and 103, apassageway 104 connected to aconduit 105, and acheck valve 106 formed in passageway 91 between the connection of conduit 92 thereto and anannular groove 107. Thecheck valve 106 will permit hydraulic fluid flow from passageway 91 toannular groove 107, but will prevent any hydraulic tluid flow in the reverse direction. When thevalve 83 is in the neutral position shown in FIGURE 8, hydraulic [luid from conduit 92 will how through passageway 91 `about theannular groove 96 of thevalve spool 93, throughpassageway 104 toconduit 105. Fromconduit 105 the hydraulic tluid will ow throughconduits 108 and 109 toreservoir 88. In the neutral position, land 97 of thevalve spool 93 will seal hydraulic huid from theannular grooves 100 and 101 of the valve body, and hydrauliclluid conduits 102 and 103 are vented to thereservoir 88 throughannular grooves 100 and 101 of the valve body,annular grooves 94 and 95 of thevalve spool 93, andpassageway 104 to and throughconduits 105, 108 and 109. When thevalve spool 93 is moved inwardly of the valve body, land 98 of thevalve spool 93 Will block passageway 91 frompassageway 104. High pressure hydraulic tluid will then ow through thecheck valve 106,annular groove 107 of the valve body, annular groove 94 of thevalve spool 93, `annular groove 100 of the valve body and throughconduit 102.Conduit 103 will remain vented to thereservoir 88. When thevalve spool 93 is moved outwardly of the valve body, passageway 91 is again blocked from fluid communication withpassageway 104 iby a land on the inner end of the valve `spool 93. High pressure hydraulic lluid will then flow from passage- Way 91 throughcheck valve 106, throughannular groove 107 of the valve body, through `annular groove 95 of thevalve spool 93, throughannular groove 101 of the valve body and through.conduit 103. Theconduit 102 will be vented over the circuit previously described. Thus, it may be seen that whenvalve spool 93 is in the u cylinder 8 neutral position fluid flows through thevalve 83 toreservoir 88 andconduits 102 and 103 are vented. Whenspool 93 is moved in and out respectively, high pressure fluid flows toconduit 102 whileconduit 103 is vented; and lluid flows toconduit 103 andconduit 102 is vented.

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

Similarly toconduit 102,conduit 103 is connected in parallel to acylinder 115 and avalve 116. Thecylinder 115 is connected to operate the clutch 80 of thespeed reducer 77 through alever arrangement 117. The outlet port of thevalve 116, which is identical in construction tovalve 112, is connected to conduit by means of conduit 118. Thevalve 116 is on one side of the machine at a position where the valve spool thereof can interconnectconduits 103 and 118 When theslide member 32 is moved to its rearwardmost position by thechain 37. The system for theboom 30 further includes a pressure relief valve 1.19 which is connected betweenconduits 92 and 108 and which will operate to by-pass Huid from the high pressure side of thepump 78 to thereservoir 88 whenever the pressure in conduit 92 exceeds a certain predetermined amount.

Considering the operation of thc hydraulic system for theboom 30 and assuming thespool 93 is moved inwardly of the body ofvalve 83, the high pressure fluid inconduit 102 will operate cylinder 111 which in turn operates clutch 79 of speed `reducer 77. This causes thespeed reducer 77 to rotatesprockets 38 in a clockwise direction as viewed in FIGURE 8. This moves thechain 37 which in turn moves theslide members 32 forwardly. As theslide members 32 move forwardly, theboom 30 will be carried forwardly as previously described, and if the valve spo-ol 93 is held inwardly until theslide member 32 reaches its forwardmost position, thevalve 112 will be operated to permit the high pressure fluid in conduit to ow through conduits 11.4 and 109 to thereservoir 88. This venting of huid fromconduit 110 will permit the clutch 79 to be disengaged thereby stopping the drive to thesprockets 38. If thevalve spool 93 is moved outwardly of the valve body of thevalve 83, the high pressure hydraulic lluid then directed throughconduit 103 will operate thehydraulic cylinder 115 to in turn cause an operation of the clutch 80 which will in turn cause power to be delivered to thesprockets 38 to rotate thesprockets 38 in a counter-clockwise direction as viewed in FIGURE 8 to move the boom rearwardly relative to the machine. When theslide member 32 and theboom 30 reach their rearwardmost position, theslide member 32 will operate thehydraulic valve 116 to vent high pressure hydraulic fluid from the hydraulic throughconduits 118, 105, 108 and 109 to thereservoir 88. With the high pressure hydraulic fluid vented fromhydraulic cylinder 115, clutch 80 will be disengaged and the drive to thesprockets 38 will be disconnected. It is, of course, not necessary that theslide member 32 be moved only from one extreme position to the other since by operating thevalve spool 93 of thevalve 83 to the neutral position any high pressure hydraulic fluid in theconduits 102 and 103 is vented to thereservoir 88 to thereby cause disengagement of either 9 of theclutches 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 thehydraulic cylinders 54 and 56 of either embodiment of the present invention operated so that thebucket 45 is positioned such as shown in FIGURE 2, thecrawler track mechanism 10 may be operated to position thebucket 45 immediately before a pile of material to be rem-oved. With the crawler track mechanism then stopped, and with theconveyor 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. Thebucket 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 thebucket 45 is substantially filled with the material to be removed, thehydraulic cylinders 54 are operated to cause the loadedbucket 45 to break away the material in thebucket 45 from that remaining in the pile and further ll the bucket in a scooping action. Operation of thehydraulic cylinders 56 will then cause the load in the bucket to be dumped therefrom over therear Wall 48 of thebucket 45 onto theforward section 13 of theconveyor mechanism 12. Theconveyor mechanism 12 will then carry that material rearwardly of the machine. As the pile immediately in front of the machine is removed, theboom 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 ofbucket 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 thehydraulic cylinders 41, thebucket 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, themain frame 11 is shown as being mounted on rubber tire mountedtraction wheels 25 instead of the continuouscrawler track mechanisms 10. Thetraction wheels 125 serve to propel the machine along the ground and to crowd thedigger 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.

Thebucket 45 is directly connected to themain 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 thetraction wheels 125, on aboom structure 126. Theboom structure 126 includesboom arms 127 extending along each side of the forward wall portions 1:6 and 17 of theconveyor mechanism 12 and beyond the forward ends thereof and connected together at their forward ends by across tube 129. Theboom arms 127 are pivotally mounted at their rear end-s on the outsides of thewall portions 16 and 17 onsupport structures 130, onpivot pins 131 mounted at their outer ends onblocks 133, welded or otherwise secured `to said support structures. The pivot pins 131 also form pivotal mountings for actuatinglevers 135 for thebucket 45.

as shown in FIGURE pile has been moved theboom 30 and themechanism 10 again itself until the bucket n Eachboom arm 127 is adjustably supported adjacent the forward end of theconveyor mechanism 12 on ahydraulic cylinder 136 trunnioned adjacent its lower end in asupport 137 extending laterally from themain frame 11, on trunnion pins 139. Thehydraulic cylinder 137 has apiston rod 140 extensible therefrom, shown in FIGURE l2 as being threaded through atransverse pin 141 pivotally mounted at its ends in parallel spacedarm portions 143 and 144 of theboom arm 127. Theinner arm portion 144 of the `boom arm 127 has a dependingleg portion 145 extending inwardly of thehydraulic 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 theconveyor mechanism 12, having slidable bearing engagement with abearing plate 147 extending vertically of theconveyor mechanism 12 and shown in FIGURE l2 as being secured thereto. The bearingplates 146 and 147 have sliding contact with each other and serve to limit lateral displacement of the 'boom structure 126 during operation of thedigger bucket 45 and to provide slidable engaging surfaces for the boom structure during vertical adjustment thereof by operation of thehydraulic cylinders 136.

Thedigger bucket 45 is transversely pivoted to the forward end portion of theboom structure 126 on laterally spacedears 149 extending rearwardly from theside walls 46 of said digger bucket. As shown in FIGURE 13, theears 149 are pivotally mounted on transverse pivot pins 150 onbearings 151. Eachpivot pin 150 is mounted at one end on thearm portion 127 of theboom structure 126 and at its opposite end on a lug 153 extending upwardly from thetube 129 inwardly of theboom arm portion 127 and welded or otherwise secured tothetransverse tube 129. Nuts andwashers 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 eachside wall 46 of the `bucket 45 on a pivot pin .157. The bell crank 155 `has a depending arm or leg having anengaging end portion 158 engagcable with thestop member 51 extending outwardly from theside wall 46 of thebucket 45 when the bell crank is pivoted in `a counter clockwise direction to pivot thefbucket 45 upwardly about the axis of thepivot pin 150. It ywill be noted from FIGURE l() that the operative connection from the `hell crank 155 to thebucket 45 is such that the bucket may pivot upwardly relative to theengaging 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 thebell crank 155.

The bell crank 155 also has an upwardly extending leg orlever arm 159 having :aclevis 160 of an adjustable link 161, pivotaily connected to its upper end on apivot 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 theactuating lever 135 and pivotally connected therewith on a ball 164 mounted on apivot pin 165 mounted in said clevis at its ends (FIGURES l() and 15).

Theactuating lever 135 is actuated by aAhydraulic cylinder 166 having apiston rod 167 exten-sible therefrom. Thehydraulic cylinder 166 has a connector 16S extending from the head end thereof between thearm portions 143 and 144 of theboom arm 127 and pivotally connected thereto on apivot pin 169.

Thepiston rod 167 extends betweenconnector plates 170 welded or otherwise secured to opposite sides of theactuator lever 135 intermediate the ends thereof, and is pivotally connected to said actuator plates bypivot 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 theactuator 135 is designated by A. The axis of thepivot pin 157 is designated by B and the axis of connection of theear 149 to theboom 127 on thepivot pin 150 is designated by C. The axis of connection of the link 161 to thelever arm 159 of thebellcrank 155 is designated by D.

As iluid under pressure is admitted to the head end of thecylinder 166 to extend thepiston rod 167 therefrom, thebellcrank 155 will initially pivot upwardly about axis B and engage theengaging end portion 158 of saidbellcrank 155 with thestop 51 and then pivot thebucket 45 upwardly. During initial upward pivotal movement of thebucket 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 andlever arm 159 in angularly disposed relation with respect to each other. Thebellcrank 155, stop 51 andbucket 46 will then move upwardly as a unit. As the pull on thelever 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 thelever arm 159 will engage a camming face 164 on theboom arm 127, preventing the link 161 `andlever arm 159 from straightening out or moving past a dead center position. Thebucket 45 will then pivot relatively to thebellcrank 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 thestop 51 engages thelever arm 159 of the bellcrank 1557 stopping movement of the bucket and jarring the loose material therein to fall onto theconveyor 24.

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

It will `also be noted that tbestop 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 thearm 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 andlever arm 159 holding the digger bucket in its discharge position until thepiston rod 167 is retractihly moved with respect to thehydraulic cylinder 166, to move the digger bucket to a loading position.

The free connection between the bell crank 155 and thedigger 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 thearm 159 with a jarring action, to jar any `moist material in the bucket to flow downwardly therealong onto the receiving end portion of theconveyor 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 withclaim 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 (1)

1. 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

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