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Publication numberUS3773384 A
Publication typeGrant
Publication dateNov 20, 1973
Filing dateApr 16, 1971
Priority dateApr 16, 1971
Publication numberUS 3773384 A, US 3773384A, US-A-3773384, US3773384 A, US3773384A
InventorsAnderson R
Original AssigneeAnderson R
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Mining machine
US 3773384 A
Abstract
A mining machine and more particularly a mining machine having a rotary drum type cutting head which cuts clearance for the supporting structure thereof.
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Description  (OCR text may contain errors)

United States Patent 11 1 Anderson Nov. 20, 1973 MINING MACHINE 2,758,826 8/1956 Paget 299/89 x 3,101,932 8/1963 Wright 299/89 X [76] lnvemor- Anderson 304 16th 3,307,880 3/1967 Newton et aL 299/89 x Franklln, 16323 3,157,438 11/1964 Lundquist 299/89 x [22] Filed: Apr. 16, 1971 [21] Appl No; 134 734 Primary ExaminerEmest R. Purser Attorney-E. Wallace Breisch [52] US. Cl. 299/76, 299/89 [51] Int. Cl. E21c 27/24 [57] ABSTRACT [58] Field of Search 299/89, 64, 75, 76

A mmmg machme and more partlcularly a mmmg ma- [56'] References Cited chine having a rotary drum type cutting head which UN STATES PATENTS cuts clearance for the sl pporting structure thereof.

3,7l2,679 1/1973 Amoroso 299/89 X 26 Claims, 6 Drawing Figures PAIENIEMuvzo ms SHEET 3 [IF 5 INVENTOR ROGER C. ANDERSON MINING MACHINE Some continuous mining apparatus of a type used in underground mining have a rotary drum type cutting head to dislodge mineral from a mine vein and are operable to provide mine passageway or room into which the apparatus advances and mining progresses. The means for driving such cutting head have been accomplished in a variety of ways, for example; chain drives, and direct gear drive with a chain cutting clearance for the gearing. Such driving arrangements have proved somewhat satisfactory; however, the use of a chain as a cutting and/or driving member is relatively expensive, requires continued maintenance and sometimes inhibits the conveying of the dislodged mineral away from the mining face.

By use of the present invention which transmits driving forces to the cutting head by means of a shaft and a plurality of reduction gearing carried within the cutting head, the shaft can be of a relatively small diameter and accordingly there is no requirement to have a driven chain or the like to cut clearance for the shaft. The clearance for the shaft is cut by closely spaced or overlapping cutter elements. Obviously, inasmuch as a cutter chain is not required by the present invention, the above described disadvantages of a cutting chain are non-existent in a cutting head driven by means of the present invention.

Additional features of the present invention include symmetrical driving of cutter head sections; a symmetrical extension of cutter head portions; and two or three point support of the cutter head by the mining boom.

These and other objects and advantages of the present invention will become more readily apparent from a reading of the following description and drawings in which:

FIG. 1 is a plan view of a mining machine embodying the principles of this invention;

FIG. 2 is a side elevational view of the mining machine shown in FIG. 1;

FIG. 3 (shown as FIGS. 3A and 3B) is a plan view, partially in section, of a first embodiment of a cutter head assembly constructed according to the principles of the present invention;

FIG. 4 is a partial plan view, partly in section, of a second embodiment of a cutter head assembly constructed according to the principles of the present invention; and

FIG. 5 is a partial plan view, partly in section, of a third embodiment of a cutter head assembly constructed according to the principles of the present invention.

A continuous mining machine generally designated at 10, which embodies the principles of this invention, may assume various forms but, for illustrative purposes, herein comprises a crawler base 14 carrying a frame 16 on which a forwardly extending mining boom 18 is pivotally mounted at the forward end of the frame 16 to swing up and down between a mine roof 20 and a mine floor 22. A cutting head assembly 24 of the present invention' extends transversely of boom 18 and is rotatably secured thereto at the forward end thereof. Pivotally mounted at the forward end of frame 16 and extending forwardly therefrom beneath the boom 18 is a conventional loading head 26 having oscillatory gathering arms 28 for engaging mined mineral and moving such mineral rearwardly and inwardly towards a well known conveying means of the mining machine 10. Conventional fluid jacks 32 serve to swing the boom 18 in a vertical plane about the pivot axis thereof.

The cutting head assembly 24 is driven from motors 36 and 38 which, as shown, are positioned an equal distance from the longitudinal centerline of machine 10 such that, as viewed in FIG. 1, motors 36 and 38 are respectively on the left and right side of centerline XX. Motors 36 and 38 are suitably rigidly secured to boom 18. The drive from motors 36 and 38 is delivered to a pair of universal drive shafts 42 and 44 respectively.

For the purposes of the hereinafter set forth description; left and right shall refer to the relative positions of elements shown in FIGS. 3a and 3b with reference to the centerline XX; inner and outer shall refer, respectively, to towards and away from the centerline XX along the longitudinal axis YY of cutter head assembly 24; and forward and rearward shall refer, respectively, to towards and away from the cutting head of machine 10 along axis XX.

As hereinafter described in detail, cutter head assembly 24 comprises; axially aligned and axially spaced outer cutter drums, shown as left and right cutter drums 46 and 48 respectively; and an intennediate cutter drum 50 which is in axial alignment with drums 46 and 48 and spaced therebetween. Cutter drums 46, 48 and 50 are supported by and cut clearance for a gearing and support casing 52. Gearing and support casing 52 includes left and right sections 54 and 56 respectively.

The drive from shaft 42 is delivered through a speed reducing train 58 of gearing rotatably supported within casing section 52 to drive outer cutter drums 46 and 48. The drive from shaft 44 is delivered through a speed reducing train 60 of gearing rotatably supported within casing 54 to drive the intermediate cutter drum 50.

Casing sections 54 and 56 are rigidly secured to boom 18 by means of respective forwardly extending spaced casing connecting portions 62 and 64 which rigidly communicate between the rearwardmost sides of sections 54 and 56 and a casing mounting plate 66 suitably rigidly secured to a forward end portion of boom 18. Mounting plate 66 extends laterally on axis XX and is generally parallel to axis YY of cutting head assembly 24. Connecting portions 62 and 64 have a lateral width thereof shown as being slightly greater than the respective diameters of shafts 42 and 44. Connecting portions 62 and 64 additionally have bores and 68 extending forwardly therethrough, generally parallel to axis XX, receiving forward portions of the respective shafts 42 and 44 therethrough. Cutter drum 50 extends intermediate connecting portions 62 and 64. Cutter drum 46 extends outwardly (to the left in FIG. 3a) from portion 64 and cutter drum 48 extends outwardly (to the right in FIG. 3b) from portion 62.

It is to be noted that inasmuch as shafts 42 and 44 directly carry the drive from respective cutting head motors 36 and 38 and furthermore and inasmuch as respective speed reducing trains 58 and 60 are rotatably carried within casing sections for which clearance is cut by respective cutter drums, the diameter of shafts 42 and 44 are relatively less than the diameter of similar shafts which would be required if speed reduction took place prior to entrance of the drive forces into the cutter head assembly (i.e., as speed is reduced, torque is increased with the resultant requirement of a greater diameter drive shaft to handle the increased torque).

The above set forth observation accounts for the relatively narrow width of connecting portions 62 and 64 and, accordingly, driven cutting chains or the like are not required to cut clearance for such sections and, as hereinafter described, clearance is cut by cutting elements closely spaced to portions 62 and 64.

Casing section 54 has a generally annular cross section and includes: a central gear supporting portion 70 which rotatably supports gear train 58 within the interior thereof; a cutter drum support portion 72 which has an outer diameter thereof less than the outer diameter of casing portion 70 and extends outwardly therefrom and which rotatably supports left cutter drum 46 adjacent the outer periphery thereof; and cutter drum and gear supporting portion 74 which has an outer diameter thereof less than the outer diameter of casing portion 70, extends inwardly therefrom and which rotatably supports the intermediate cutter drum 50 and the radial innermost surfaces of gear train 60 adjacent the outer periphery thereof.

Casing section 56 has a generally annular cross section and includes: a central gear supporting portion 76 which rotatably supports the radial outermost surfaces of gear train 60 within the interior thereof; and cutter drum support portion 78 which has an outer diameter thereof less than the outer diameter of casing portion 76 and extends outwardly therefrom and which rotatably supports right cutter drum 48 adjacent the outer periphery thereof.

The outer diameter of casing portion 74 is less than the inner diameter of casing portion 76 and to the right of centerline X-X at right end portion thereof is received with and radially inwardly spaced from casing portion 76 for the purpose of the hereinabove mentioned disposition of gear train 60 therebetween. At the extreme right end of casing portion 74 at least one integral casing connecting portion 80 extends radially outwardly therefrom and the radial outermost end thereof is secured to casing section 56 in any suitable manner, for example bolt 82 which threadably engages such radial outermost end and the right end of easing portion 76.

With a construction of gearing and support casing 52 as described hereinabove wherein the respective left and right sections 54 and 56 thereof are secured together any external forces applied to casing 52 will be resisted by the entire casing 52 because such forces will be distributed throughout the casing 52. If the connection of sections 54 and 56 was not made, externally applied forces would create a substantially greater moment on respective connecting portions 62 and 64 and could possibly result in permanent bending at portions 62 and 64 and/or an inefficient operating structure be cause of excessive deflection or misalignment.

The forwardmost end of drive shaft 44 terminates within the rearward interior of casing portion 76 intermediate the internal periphery thereof and the external periphery of casing portion 74. The forwardmost end of shaft 44 has a bevel gear 84 secured thereto which is in toothed engagement with an annular bevel reduction gear 86 to form a 90 bevel reduction set. Bevel gear 86 is coaxial with cutter head assembly 24 with respect to axis YY thereof and has an annular coaxially aligned sun gear 88 fixedly secured thereto. Sun gear 88 extends longitudinally inwardly (to the left) from bevel gear 86 and the innermost end thereof is in toothed engagement with a coaxially aligned, annular,

planetary reduction set 90. Planetary reduction set 90 includes a plurality of planetaries 91 which have an annular coaxially aligned planetary cage 92 fixedly secured thereto at the inner or output ends thereof. Planetary cage 92 extends longitudinally inwardly (to the left) from planetaries 91 and has the innermost end thereof in toothed engagement with a coaxially aligned, planetary reduction set 94. Planetary reduction set 94 includes a plurality of planetaries 95 which have an annular coaxially aligned planetary cage 96 fixedly secured thereto at the inner or output ends thereof. Planetary cage 96 extends longitudinally inwardly (to the left) from planetaries 95 and is in driving engagement with the intermediate cutter drum 50 for the rotatable driving thereof. The driving engagement between cage 96 and cutter drum 50 is shown as being to the right and left of machine center line X-X.

Bevel gears 84 and 86, sun gear 88, planetary reduction sets 90 and 94 and planetary cages 92 and 96 comprise speed reducing train 60 which is described hereinabove as being rotatably supported by easing portion 74 and/or casing portion 72.

The forwardmost end of drive shaft 42 terminates within the rearward interior of casing portion 70 and has a bevel gear 98 secured thereto which is in toothed engagement with an annular bevel reduction gear 100 to form a 90 bevel reduction set. Bevel gear 100 is coaxial with cutter head assembly 24 with respect to axis Y-Y thereof and has an annular coaxially aligned sun gear 102 fixedly secured thereto. Sun gear 102 extends longitudinally inwardly (to the right) from bevel gear 100 and the innermost end thereof is in toothed engagement with a coaxially aligned, annular, planetary reduction set 104. Planetary reduction set 104 includes a plurality of planetaries 105 which have an annular coaxially aligned planetary cage 106 fixedly secured thereto at the inner or output ends thereof. Planetary cage 106 extends longitudinally inwardly (to the right) from planetaries 105 and has the innermost end thereof in toothed engagement with a coaxially aligned, annular, planetary reduction set 110. Planetary reduction set 110 includes a plurality of planetaries 111 which have an annular coaxially aligned planetary cage 112 fixedly secured thereto at the inner or output ends thereof. Planetary cage 112 extends radially inwardly from planetary set 110 and has an annular right outer drum driving portion 114 extending inwardly (to the right) from the inner end of set 110 and an annular left drum driving portion 116 extending outwardly (to the left) from the inner end of gear 1 10. Bevel gears 98 and 100, sun gear 102, planetary reduction sets 104 and 110 and planetary cages 106 and 112 comprises speed reducing train 58 which is described hereinabove as being rotatably supported by easing portion 70.

Cage portion 116; extends axially outwardly (to the left in FIG. 3a) is radially inwardly spaced from the radial innermost surfaces of planetary gears 104 and l 10, and the axially outermost extent thereof is shown as stopping short of the axially outermost end of the bevel reduction gear 98. A portion of the inner periphery of cage portion 116, located at the axial outer end thereof, is in splined driving engagement with an elongated left cutter drum drive shaft 120. Drive shaft is coaxial with respect to axis Y-Y and extends axially outwardly (to the left) from the point of splined engagement with cage portion 118 and the axially outer- .tion of the inner periphery of cage portion 114, located at the axial inner end thereof, is in splined driving en-.

gagement with an elongated left cutter drum drive shaft 122. Drive shaft 120 is coaxial with respect to axis YY and extends axially outwardly (to the right) from the point of splined engagement with portion 144 and the axially outermost end thereof is outwardly spaced from the outermost end of the casing section 56.

The left and right cutter drums 46 and 48 each comprise a hollow cylindrical outer member 124 and a hollow cylindrical inner support and guide member 126. The'outer periphery of member 126 is spaced radially inwardly from the innermost end thereof. The left cutter drum 46 is rotatably supported by gear and support casing 52 by means of thrust roller bearings 128 being disposed intermediate the outer periphery of cutter drum support portion 72 and the inner periphery of guide member 126. The right cutter drum 46 is rotatably supported by casing 52 by means of bearings 128 being disposedintermediate the outer periphery of cutter drum support portion 78 and the inner periphery of guide member 126. v

The outermost end of each drive shaft 120 and 122 is suitably secured to the inner end of a generally cylindrical end cap member 130 of respective cutting head extensions 132. Extensions 138 additionally include a generally hollow cylindrical drum member 134 which has an end cap member 130 fixedly secured thereto at the outer end thereof. An inner end portion of drum member 134 is slidably and captively received within an outer portion of respective cutter drums 46 and 48 intermediate the inner periphery of member 124 and the outer periphery of member 126.

Cutter drums 46 and 48 each have a plurality of radially inwardly extending keys 136 which cooperate with respective keyways 138. Keyways 138 are spaced about the outer periphery of drum member 134 and extend generally parallel to axis YY.

With such a construction of cutting head extensions 132 as described hereinabove, extensions 132 are driven directly from a respective drum drive shaft and cutter drums 46 and 48 are driven from the cooperating key and keyways intermediate the drums 46 and 48 and the respective drum member 134 thereat. The axial length of keyways 138 allow for the axial extension and retraction of cutting head extensions 132. As contemplated hydraulic fluid will be provided through casing passageways 140 for the extension and retraction of cutting head extensions 132. Passageways 140 are in communication with a suitable fluid pressure source (not shown).

Well known screw type continuous conveyor scrolls 142 are secured to the outer periphery of cutter drums 46, 48 and 50 and cutting head extensions 132. Scrolls 142 have a plurality of suitable bit holders 14 and secured adjacent the outer peripheral edges thereof in a suitable spaced orientation to one another. A cutter bit 146 is inserted in each bit holder 120. Cutter bits 146 bob deep penetrating point attack conical bits. The respective bits 146 adjacent connecting portions 62 and 64 are positioned such that they cut clearance for portions 62 and 64 during mining operations. The scrolls 142 are suitably arranged to convey a portion of mineral mined by bits 146 inwardly from such bit locations towards the center line XX of machine 10.

It is to be noted that inasmuch as cutter drums 46 and 48 are independently driven with respect to the intermediate cutter drum 50, drums 46 and 48 do not necessarily have to rotate in time with the intermediate cutter drum 50. Of course if desired a suitable arrangement could be provided to insure synchronized rotation of all cutter drums of cutter head assembly 24.

Various modifications can be made to cutter head assembly 24 without departing from the scope of the invention discussed therein, for example: assembly 24 carries a three-step gear reduction within the cutter casing wherein it is contemplated that more or less gear reductions can be carried therein, in the latter case '1 single or multiple speed reduction take place prior to the torque being transmitted to shaft 42 and/or 44; only a single cutting head extension arrangement be provided on one side of the cutter head assembly 24; other means can be provided for extending cutting head end extensions such as extensions 132; the cutter head assembly 24 can have either side portions thereof skewed towards the center.

FIG. 4 illustrates a second embodiment of a cutter head assembly 300 constructed according to the principles of this invention. 5

The cutter head assembly 300 is driven from motors 36 and 38 which, as shown, are positioned and secured to machine 10 in a manner as hereinbefore described with reference to head assembly 24. The drive from motors 36 and 38 is delivered to a pair of universal drive shafts, each shaft being designated as 302.

Inasmuch as cutter head assembly 300 is identical on the left and right side of machine center line X--X, the discussion hereinafter will be limited to the description of the left hand side of assembly 300 with the implicit understanding that the description of the right hand side is similar to the hereinafter set forth description of the left hand side.

For the purposes of the hereinafter set forth description; left and right shall refer to the relative positions of elements of assembly 300 with reference to the centerline XX; inner and outer shall refer, respectively, to towards and away from the centerline X-X along the longitudinal axis YY of cutter head assembly 300; and forward and rearward shall refer, respectively, to towards and away from the cutting head of machine 10 along axis XX.

As hereinafter described in detail, cutter head assembly 300 comprises axially spaced and axially aligned outer cutter drums 304, and an intermediate cutter drum 306 which is in axial alignment with drums 30-1 and spaced therebetween. Cutter drums 304 and 306 are supported by and cut clearance for a gearing and support casing 308. Gearing and support casing 308 includes left and a right sections 310. The drive from shafts 302 is delivered through speed reducing trains 312 of gearing each of which is rotatably supported within respective casing sections 310.

Casing sections 300 are rigidly secured to boom 18 by means of respective forwardly extending spaced casing connecting portions 314 which rigidly communicate between the rearward most sides of sections 310 and a casing mounting plate 316 which is rigidly secured to a forward end portion of boom 18. Mounting plate 316 extends laterally of axis X-X and generally parallel to axis YY of cutting head assembly 300. Connecting portions 314 have a lateral width thereof shown as being slightly greater than the diameter of shafts 302 and each portion 314 have a bore 317 extending forwardly therethrough, generally parallel to axis XX, for receiving forward portions of a respective shaft 302 therethrough. Cutter drum 306 extends intermediate connecting portions 314 and cutter drums 304 extend outwardly from a respective connecting portion 314.

Each casing section 310 has a generally annular cross section and includes: a gear supporting portion 318 which rotatably supports gear train 312 within the interior thereof; and an outer cutter drum support portion 320 which has an outer diameter thereof less than the outer diameter of casing portion 318 and extends outwardly therefrom and which rotatably supports an outer cutter drum 304 adjacent the outer periphery thereof.

The forwardmost end of drive shaft 302 terminates within the rearward interior of casing portion 318 and has a bevel gear 322 secured thereto which is in toothed engagement with an annular bevel reduction gear 324 to form a 90 bevel reduction set. Bevel gear 324 is coaxial with cutter head assembly 300 with respect to axis Y-Y thereof and has an annular coaxially aligned sun gear 326 secured thereto. Sun gear 326 extends longitudinally inwardly (to the right) from bevel gear 324 and has the innermost ends thereof in toothed engagement with a coaxially aligned, annular, planetary reduction set 328. Planetary reduction set 328 includes a plurality of planetaries 330 which have an annular coaxially aligned planetary cage 332 fixedly secured thereto at the inner or output ends thereof. Planetary cage 332 extends longitudinally inwardly (to the right) from planetaries 330 and has the innermost end thereof in toothed engagement with a coaxially aligned, annular planetary reduction set 334. Planetary reduction set 334 includes a plurality of planetaries 336 and at the inner or output ends thereof drivingly engage an annular coaxially aligned hollow driving cylinder 338 adjacent one end thereof. Driving cylinder 338 extends radially inwardly from planetary set 334 and at the radially innermost periphery thereof is in splined engagement with a portion of the radially outer periphery of a drum drive shaft 340. Driving cylinder 338 extends intermediate planetary reduction sets 334 and the axial ends thereof are drivingly engaged at the inner or output ends of a respective reduction set 334. An intermediate portion of the outer periphery of cylinder 338 is in driving engagement with the intermediate cutter drum 305 for the rotatable driving thereof.

Bevel gears 322 and 324 sun gear 326, planetary reduction sets 328 and 334 and planetary cage 332 and driving cylinder 338 comprise the speed reducing train 312 which is described hereinabove as being rotatably supported by casing portion 318.

Drum drive shaft 340 is coaxial with respect to axis Y-Y and extends outwardly from the point of splined engagement with driving cylinder 338 and the axially outermost end thereof is outwardly spaced from the outermost end of the casing section 310.

The outer cutter drums 304 each comprise a hollow cylindrical outer member 342 and a hollow cylindrical inner support and guide member 344. The outer periphery of member 344 is spaced radially inwardly from the member 342 and such tied together at the innermost ends thereof. Cutter drum 304 is rotatably supported by gear and support casing 308 by means of thrust bearings 346 being disposed intermediate the outer periphery of cutter drum support portion 320 and the inner periphery of guide member 344.

The outermost end of each drive shaft 340 is suitably secured to the inner end of a generally cylindrical end cap member 348 of a respective cutting head extension 350. Extension 350 additionally includes a generally hollow cylindrical drum member 352 which has an end cap 348 fixedly secured thereto at the outer end thereof. An inner end portion of drum member 352 is slidably and captively received within an outer portion of cutter drum 340 intermediate the inner periphery of member 342 and the outer periphery of member 344.

Each cutter drum 304 has a plurality of radially inwardly extending keys 354 which cooperate with respective keyways 356. Keyways 356 are spaced about the outer periphery of drum member 304 and extend generally parallel to axis YY.

With such a construction of cutting head extensions 350 as described hereinabove, extensions 350 are driven directly from a respective drum drive shaft 340 and cutter drum 304 is driven from the cooperating key and keyways intermediate drum 304 and the respective drum member 352 thereat. The axial length of keyways 356 allow for the axial extension and retraction of cutting head extensions 350. As contemplated hydraulic fluid will be provided through casing passageways 358 for the extension and retraction of cutting head extensions 350. Passageways 358 are in communication with a suitable fluid pressure source (not shown). As discussed hereinbefore with respect to assembly 24 screw type continuous conveyor scrolls 142 are suitably secured to the outer periphery of cutting drums 304 and 306.

It is to be noted that inasmuch as a common member (driving cylinder 338) has respective ends thereof keyed to drum drive shafts 340, cutter drums 304 and 306 will have syncronized rotation.

Various modifications can be made to cutter head assembly 300 without departing from the scope of the invention discussed therein, for example those modifications discussed hereinbefore with reference to cutter head assembly 24.

FIG. 5 illustrates a third embodiment of a cutter head assembly 400 constructed according to the principles of this invention.

A cutter head assembly 400 is driven from motors 36 and 38 which, as shown, are positioned and secured to machine 10 in a manner as hereinbefore described with reference to head assembly 24. The drive from motors 36 and 38 is delivered to a pair of universal drive shafts, each shaft being designated as 302.

As hereinafter described in detail, cutter head assembly 400 comprises a pair of axially spaced and axially aligned outer cutter drums 304, and a pair of intermediate cutter drums 406 which are in axial alignment with each other and with drums 304. Drums 406 are spaced between drums 304 and are axially spaced from each other. Cutter drums 304 and 406 are supported by and cut clearance for a gearing and support casing 408. Gear and support casing 408 includes left and right sections 410 and an intermediate section 412. The drive 9 from shafts 302 is delivered through speed reducing trains 414 of gearing each of which trains 414 is rotatably supported within casing 408.

Cutter head assembly 400 is similar to the cutterhead assembly 300 described hereinabove in that the cutterhead configuration and driving arrangement are symmetrical on the left and the right side of axis X-X of machine 10, and, further, a plurality of reduction gearing as carried within the head assembly, however, assembly 400 differs from the latter mentioned assembly in that, as hereinafter described in detail, assembly 400 includes a three point support back to the cutter boom and, further, assembly 400 includes four axially aligned and axially spaced cutter drums rather than three.

Inasmuch as cutter head assembly 400 is identical on the left and right sides of machine centerline X-)(, the discussion hereinafter will be limited to the description of the left hand side of assembly 400 with the implicit understanding that the description'of the right hand side thereof issimilar to the hereinafter set forth description of the left hand side. Furthermore, it is hereby noted that the portions of cutter head assembly 400 axially outwardly of drive shafts 302 are substantially identical to similar oriented portions of cutter head assembly 300, and accordingly, for a showing and description of such portions, reference is made to the description and showing of the similar oriented portions of cutter head assembly as shown in FIG. 4 and described in the respective description thereto. One further point to be noted is within as much as elements of assembly 400 are substantially identical or similar to respective elements of assembly 300 as hereinbefore described, elements of assembly 400 which are identicalto respective elements of assembly 300 are hereinbefore and hereinafter identified by the same reference numerals and similar elements are identified by the same reference numerals primed.

For the purposes of the hereinafter set forth description: left and right shall refer to the relative positions of elements of assembly 400 with reference to the centerline X-X; inner and outer shall refer, respectively, to towards and away from the centerline X'X along the longitudinal axis Y-Y of cutter head assembly 400; and forward and rearward shall refer; respectively, to towards and away from the cutting head of machine 10 along axis X-X.

Casing sections 410 are rigidly secured to boom 18 by means of respective forwardly extending spaced cas ing connecting portions 416 which rigidly communicate between the rearwardmost sides of sections 410 and easing mounting plate 418 which is rigidly secured to a forward end portion of boom 18. Mounting plate 418 extends laterally of axis X-X and generally parallel to axis Y-Y of cutting head assembly 400. Connecting portions 416 have a lateral width thereof shown as being slightly greater than the diameter of shafts 302 and each portions 416 has a bore 317 extending forwardly therethrough, generally parallel to axis X-X, for receiving forward portions of a respective shaft 302 therethrough.

Casing section 412 is rigidly secured to boom 18 by means of a forwardly extending casing connecting portion 420 which rigidly communicates between the rearwardmost' side of section 410 and the casing mounting plate 18. Connecting portion 420 is shown as having a lateral width thereof substantially equal to the lateral width of portions 416 and the forward extent of portion 420 is along axis X--X. Each cutter drum 406 extends intermediate connecting portion 420 and a respective connection portion 416 and drums 406 extend outwardly from a respective connecting portion 416.

Each section 410 has a generally annular cross section and includes: a gear supporting portion 422 which rotatably supports gear train 414 and an outer cutter drum support portion 320.

The forwardmost end of drive shaft 302 terminates within the rearward interior of casing portion 422 and has a bevel gear 424 secured thereto which is in toothed engagement with an annular bevel reduction gear 426 to form a bevel reduction set. Bevel gear 426 is coaxial with cutter head assembly 400 with respect to axis Y-Y thereof and has a tubular coaxially aligned sun gear 428 secured thereto. Sun gear 428 extends longitudinally inwardly (to the right) from bevel gear 426 and has the innermost ends thereof in toothed engagement with a coaxially aligned, annular, planetary reduction set 430. Planetary reduction set 430 includes a plurality of planetaries 432 which have an annular coaxially aligned planetary cage 434 fixedly secured thereto at the inner or output ends thereof. Planetary cage 434 extends longitudinally inwardly (to the right) from planetaries 432 and has the innermost ends thereof in toothed engagement with a coaxially aligned, annular planetary reduction set 436. Planetary reduction set 436 includes a plurality of planetaries 438 and at the inner or output ends thereof drivingly engage an annular coaxially aligned planetary cage 440. Planetary cage 440 has the radially outermost periphery thereof in rigid communication with cutter drum 406 adjacent the inner end thereof. A portion of the radially innermost periphery of planetary cage 440 is in splined engagement with a portion of the radially outer periphery of a drum drive shaft 340'.

Bevel gears 424 and 426, sun gear 428, planetary reduction sets 430 and 436 and planetary cages 434 and 440 comprise the speed reducing train 414 which is described hereinabove as being rotatably supported with in casing 408.

Drive shaft 340' is coaxial with respect to axis Y-Y and extends outwardly from the point of splined engagement with cage 440. For further details of shaft 340' and the supporting and driving arrangement thereof reference is hereby made to the description of assembly 300 as set forth hereinbefore.

It is to be noted that inasmuch as cutter drums 304 and 406 on one side of centerline X-X are indepen dently driven with respect to the cutter drums 304 and 406 on the other side of centerline XX, one pair of such drums do not have to rotate in time with respect to the other pairs of such drums. Of course if desired a suitable arrangement could be provided to insure syncronized rotation of a cutter drums of cutter head assembly 400.

Various modifications can be made to cutter head assembly 400 without departing from the scope of the invention discussed therein, for example, those modifications discussed hereinbefore with reference to cutter head assembly 24.

What is claimed is:

1.. A mining machine cutting structure adapted to be supported solely for vertical movement relative to a supporting mining machine chassis, comprising: a rigid member having a forward portion and laterally spaced support portions extending rearwardly of said forward portion for powered rotation about a longitudinal axis of said head member; said head member having sections thereof extending along said axis outwardly from and intermediate said spaced support portions; said sections having cutter supporting portions adapted to carry cutters, respectively, to mine a path in a bedded deposit of mineral the width of which path exceeds the transverse profile of the mining machine chassis; said cutter supporting portions being located with respect to each other to provide, when carrying cutters, clearance for said head member and said spaced support portions; and certain ones of said cutter supporting portions being movable in orbits located closely adjacent the sides of said support portions, respectively, to cut clearance for said spaced support portions by cutters supported by said certain ones of said cutter supporting portions solely upon movement of said certain ones of said cutter supporting portions through said orbits.

2. A mining machine cutting structure as specified in claim 1 wherein the forward portion of said rigid member has at least a rigid continuous section thereof extending intermediate said spaced support portions.

3. A mining machine cutting structure as specified in claim 1 additionally including cutters supported by said cutter supporting portions to move in parallel orbits spaced axially along the longitudinal axis of said head member.

4. A mining machine cutting structure as specified in claim 1 including two spaced support portions only and said sections comprise a single cutter drum extending intermediate said spaced support portions and a pair of outer cutter drums each of which extend outwardly from a respective spaced support portion along said axis.

5. A mining machine cutting structure as specified in claim 1 including three spaced support portions only and said sections comprise a pair of cutter drums each of which extend intermediate adjacent spaced support portions and a pair of outer cutter drums each of which extend outward from a respective spaced support portion along said axis.

6. A mining machine cutting structure as specified in claim 1 additionally including driven gear means supported by said rigid member to drive said head member about said axis.

7. A mining machine cutting structure as specified in claim 6 wherein said drive gear means includes a plurality of speed reduction gear means carried within the interior of at least some of said sections.

8. A mining machine cutting structure as specified in claim 6 wherein said head member additionally includes head shaft means extending along said axis for transmitting the drive from at least some of said driven gear means to at least some of said sections.

9. A mining machine cutting structure as specified in claim 8 including two spaced support portions only and said sections comprise a single cutter drum extending intermediate said spaced support portions and a pair of outer cutter drums each of which extend outwardly from a respective spaced support portion along said axis.

10. A mining machine cutting structure as specified in claim 9 wherein; said driven gear means comprise two independently driven gear trains; each of said gear trains being driven adjacent the forward end of a respective input shaft; and said input shafts extending forwardly through a respective spaced support portion.

11. A mining machine cutting structure as specified in claim 9 wherein said outer cutter drums are rotatably driven by said head shaft means and said single cutter drum is rotatably driven directly by said driven gear means.

12. A mining machine cutting structure'as specified in claim 11 wherein said driven gear means comprise two independently driven gear trains.

13. A mining machine cutting structure as specified in claim 12 wherein one of said gear trains drives said head shaft means and the other of said gear trains drives said single cutter drum.

14. A mining machine cutting structure as specified in claim 9 wherein said head shaft means comprises two separate head shafts each of which extend along said axis on a respective side of said head member.

15. A mining machine cutting structure as specified in claim 14 wherein said driven gear means and at least one of said head shafts have cooperable means thereon to provide for limited axial movement of said at least one of said head shafts along said axis.

16. A mining machine cutting structure as specified in claim 14 wherein said head shafts and said sections are coaxial with respect to said axis.

17. A mining machine cutting structure as specified in claim 14 wherein said driven gear means comprise two independently driven gear trains and each of said gear trains drives a respective head shaft and said single cutter drum is driven by both of said head shafts.

18. A mining machine cutting structure as specified in claim 8 including three spaced support portions only and said sections comprise a pair of intermediate cutter drums each of which extend intermediate adjacent spaced support portions and a pair of outer cutter drums each of which extend outward from a respective spaced support portion along said axis.

19. A mining machine cutting structure as specified in claim 18 wherein said outer cutter drums are rotatably driven by said head shaft means and said intermediate cutter drums are rotatably driven directly by said driven gear means.

20. A mining machine cutting structure as specified in claim 18 wherein said head shaft means comprises two separate head shafts each of which extend along said axis on a respective side of said head member.

21. A mining machine cutting structure as specified in claim 20 wherein said driven gear means and at least one of said head shafts have cooperable means thereon to provide for limited axial movement of at least one of said head shafts along said axis.

22. A mining machine cutting structure as specified in claim 22 wherein said head shafts and said sections are coaxial with respect to said axis.

23. A mining machine cutting structure as specified in claim 19 wherein said driven gear means comprise two independently driven gear trains.

24. A mining machine cutting structure as specified in claim 23 wherein one of said gear trains drives one of said head shafts and one of said intermediate cutter drums and the other of said gear trains drives the other of said head shafts at the other of said intermediate cutter drums.

25. A mining machine cutting structure as specified in claim 18 wherein; said driven gear means comprise two independently driven gear trains; each of said gear trains being driven adjacent the forward end of a respective input shaft; and said input shafts extending forwardly through a respective spaced support portion.

26. A mining machine cutting structure as specified in claim 25 wherein the spaced support portions through which said input shafts extend are the outermost spaced support portions.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION PATENT NO. 3 773 384 DATED I November 20, 1973 I I Roger C. Anderson It is certified that error-fappears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Claim 1, line 2, :after "vertical" insert arcuete line 6, after "portion" insert an elongated head member supported by said forward portion of said rigid member line 12, after "width" insert and heighth Signed and Sea-led this Seventeenth Day August 1976 [SEAL] v Arrest:

RUTH C. MASON C. MARSHALL DANN Arresting Officer Commissioner of Patents and Trademarks

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Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3966257 *Aug 26, 1974Jun 29, 1976Lee-Norse, CompanyDriving arrangement for rotary mining heads of mining machines
US4098539 *Aug 31, 1976Jul 4, 1978Vereinigte Osterreichische Eisen- Und Stahlwerke - Alpine Montan AktiengesellschaftCutting machine
US4253705 *Jun 12, 1979Mar 3, 1981National Mine Service CompanyContinuous mining machine having a boom member with a fixed material dislodging means
US4310199 *Sep 20, 1979Jan 12, 1982National Mine Service CompanyCutter drum assembly for a continuous mining machine
US4486051 *Nov 19, 1982Dec 4, 1984Joy Manufacturing CompanyMining Machine
US4582363 *Jan 3, 1984Apr 15, 1986National Mine Service CompanyDrive assembly for mining machine cutter drum
US4786112 *Jul 16, 1987Nov 22, 1988Voest-Alpine AktiengesellschaftDriving arrangement for driving the cutting rolls of a drift advancing machine
US4836613 *Jan 21, 1988Jun 6, 1989Adam Roger F JCutterhead for water jet assisted cutting
US5108154 *May 14, 1990Apr 28, 1992Voest-Alpine Zeltweg Gesellschaft M.B.H.Drive arrangement for shearing drums
US5143423 *Jan 18, 1991Sep 1, 1992Tamrock World Corporation, N.V.Drum assembly for a continuous miner
US5548914 *Nov 10, 1994Aug 27, 1996Anderson; David B.Gun trigger mechanism
US5582466 *Jul 10, 1995Dec 10, 1996Coaltex, Inc.Advance/retreat cutting miner with simple conveyor
US5964507 *Oct 20, 1997Oct 12, 1999Mining Technologies, Inc.Apparatus for mining a mineral seam
US6890037 *Feb 21, 2003May 10, 2005Joy M M Delaware, Inc.Cutting drum web deflector
WO2012034145A1 *Aug 30, 2011Mar 22, 2012Sandvik Mining And Construction G.M.B.H.Cutting device for movable mining machines for underwater use
Classifications
U.S. Classification299/76, 299/78
International ClassificationE21C27/00, E21C27/24
Cooperative ClassificationE21C27/24
European ClassificationE21C27/24
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