|Publication number||US3857516 A|
|Publication date||Dec 31, 1974|
|Filing date||Jul 7, 1972|
|Priority date||Jul 8, 1971|
|Also published as||CA971581A, CA971581A1, DE2232993A1, DE2232993C2|
|Publication number||US 3857516 A, US 3857516A, US-A-3857516, US3857516 A, US3857516A|
|Inventors||Noren C, Taylor N|
|Original Assignee||Noren C, Taylor N|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (9), Referenced by (21), Classifications (8)|
|External Links: USPTO, USPTO Assignment, Espacenet|
Hittite States Patent [1 1 Taylor et al.
[111' 3,857,516 [4 1 Dec. 31, 1974 1 ROCK-CUTTING MACHINES [76} Inventors: Nicholas Simon Hall Taylor,
Sturevagen 11, 133 O0 Saltsjobaden; Carl Anders Nor-en, Kocktorpsvagen 55 a, 132 O0 Saltsjo-Boo, both of Sweden  Filed: July 7, 1972  Appl. No.: 269,835
.  Foreign Application Priority, Data UNITED STATES PATENTS Donisthorpe 299/42 531,019 12/1894 Campbell 299/42 2,501,639. 3/1950 Warren 239/587 X 3,165,361 l/l965 Dawson et al.. 299/43 3,241,772 3/1966 Thompson.... 239/587 X 3,521,820 7/1970 Cooley 1 239/101 3,565,191 2/1971 Bowen r 175/422 X 3,592,387 7/1971 Pilott 239/18 C 3,708,121 l/l973 Hall et a1 239/102 Primary Examiner-M. Henson Wood, Jr. Assistant Examiner-John J. Love Attorney, Agent, or Firm-Eric Y. Munson  ABSTRACT movable with the pressure intensifiers and the jets emitted by the nozzles cut slots in the rock face.
. 8 Claims, 6 Drawing Figures PATENTEDBEB31 IBM 3'. 857. 51s
SHEET 2 OF 5 PATENTED l 3. 8571. 516
SHEET u, 0F 5 PATENTEDDEB31 I974 sum 5 [IF 5' I ROCK-CUTTING MACHINES SUMMARY OF THE INVENTION This invention relates to cutters particularly but not exclusively for cutting rock.
According to one aspect of the invention there is provided a cutter comprising means adapted to be fixed at least temporarily in position, a nozzle operatively connected to the fixed means and being movable relative thereto and generator means carried by the fixed means and operatively connected to and movable together with the nozzle and being adapted to supply fluid under pressure to the nozzle so that the latter can emit a high velocity jet.
Preferably the fixed means comprises a preferably movable frame and a head carrying the nozzle and being carried by and movable along the frame. The head preferably also carries the generator means; The generator means preferably comprises a piston and cylinder device (hereinafter called the ejector device) discharging through the nozzle. The means to actuate the generator preferably comprises a power piston and cylinder device connectable to a source of hydraulic pressure. The effective area of the power piston is preferably substantially greater than that of the ejector piston and may be between twelve and twenty-four times this size preferably between fifteen and eighteen times the size and preferably approximately seventeen times this size.
The power piston is preferably single acting and actuates one ejector piston but it may be a double acting piston actuating two ejector pistonsrespectively on forward and return strokes. I
The ejector cylinder .is preferably connected to the nozzle through a pipe movable to adjust the location of the nozzle. Means are preferably provided for moving the head along the frame. The moving and fixed means may vary with the length of the cut that it is intended to make. The fixed means may be a pair of rails and the head a carriage running along the rails. In this case the moving means may be a motor carried by the carriage and adapted to propel the latter along the rails. Where the fixed means is a movable frame, the moving means may comprise an elongated hydraulic or pneumatic jack or it may comprise a chain or the like connected to the head and to means for advancing the chain so that the head is thereby advanced.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a rock cutter of the invention,
FIG. 2 is a plan of the rock cutter at the stope face,
FIG. 3 is a view in the direction of arrow 3 in FIG. 2,
FIG. 4 is an enlarged detail section of the intensifiers;
FIG. 5 is a view similar to FIG. 2 ofa modified rock cutter of the invention, and
FIG. 6 is a section through the intensifier used therein.
DESCRIPTION OF DIFFERENT EMBODIMENTS OF THE INVENTION Referring now to FIGS. 1 to 4, a rock cutter 10 of the invention comprises a frame 12 which is mounted on levelling jacks 14 and provided with spragging jacks 16 so that it may be firmly located in position adjacent to a stope face. A valve arrangement 18 is carried by the frame and this serves to control the jacks l4 and 16 and to carry out the other operations as will be described. Slidably carried by the frame 12 is a head 20 carrying a plate 211 on which is mounted a pair of pressure intensifiers 22. Each intensifier comprises a power cylinder 24 and an ejector cylinder 26 the latter being connected via an outlet tube 28 to a nozzle 30. The cylinders 24 and 26 being subject to very high pressures, as will be described, are of extremely robust construction. A hand operated jack screw 31 (see FIG. 2) is provided to move the plate 21 on the head to adjust the location of the nozzles 30 relative to the stope face.
The head 20 is slidably mounted on a pair of longitudinally extending slide beams 32. Movement of the head 20 is effected by means of a pair of chains 34 which are driven by a pair of sprocket wheels 36 at one end of the frame 12 and which passes over a pair of idler sprocket wheels 38 atthe other end of the frame 12. The idler sprocket wheels 38 are carried by an idler shaft 40 mounted in bearings in housings 41. The sprocket wheels 36 are carried by a drive shaft 42 mounted in bearings in housings 44. A reversible hydraulic motor 46 is connected to drive the drive shaft 42 and is controlled by the valve 18. Traversing limit valves 48 are provided adjacent each end of the stroke of the head 20 to cause the latter to reverse its direction of movement. Buffers or shock absorbers 50 are provided at the ends of the frame 12 in case the head 20 should tend to overrun its path.
The intensifiers 22 are shown in section in FIG. 4. Within the power cylinder 24 there is a power piston 52. A co-axial extension 54 to the power piston 52 is slidably and sealably fitted to the ejector cylinder 26 and its free end 56 forms an ejector piston. A conduit 58 passes through the end wall 60 of each of the power cylinders 24. The two conduits 58 lead to a directional control valve 62 which is carried in a housing 63 mounted on the head 20. This valve 62 is connected to power and drain conduits 64 and 66 and is arranged so that one of the power cylinders 24 is connected to the hydraulic power source and the other is connected to drain save in the initial position in which both are connected to drain. The exhaust sides of the two power cyl inders 24 (ie that part of each cylinder which is on the side of the power piston remote from the end walls 60) are connected together by a short conduit 68 so that as one piston 52 is advanced (ie moved away from the end wall) the other piston is forced by the exhausting fluid to retract. Means to compensate for any leakage of this exhausting fluid is provided. Care must be taken that this device does not overcompensate and overfill the exhaust sides of the power cylinders.
The ejector cylinders 26 are each supplied with water under low pressure. This water is fed in through a bore 70 passing through the power piston 52 and its extension 54. A one way valve 72 prevents reverse flow of water through this bore 70. The bore of a tube 74 carried by the piston 52 forms a continuation of the bore 70. This tube 74 passes through an opening in the end wall 60 and is sealed thereto by seals 76. The free end of the tube 74 is received within an end tube 78 which is of sufficient length to accomodate the movement of the tube 74. Teed off this end tube 78 is a waterconduit 80. The two conduits 80 lead to the valve housing 63 where they are joined together and are connected to a water supply conduit 82.
Also contained within the end tube 78 is an hydraulic valve 84 having a movable detector member 86 which runs along the tube 74. When the piston 52 is at the forward end of its stroke, the member 86 will be free of the tube 74 and will cause a signal to be passed to the valve 62 to reverse the hydraulic flows to the intensifiers 22.
Each outlet tube 28 is of shallow Z-shape. It has a flange 88 at its inner end. A locking gland nut 90 screwed into the end wall of the ejector cylinder locks the outlet tube in any set or desired position.
Lugs 91 are provided on the frame for the attachment of chains which, by means of winches (all not shown), may be used to move the frame within the stope.
It will be noted that the effective area of the power piston 52 is substantially greater than that of the ejector cylinder and is preferably approximately 17 times that area. The pressure of the oil supplied to the power cylinder 24 is of the order of 300 bars and therefore the pressure of the water is slightly less than seventeen times this amount. The preferred diameter of the jet in the nozzle 30 is 0.6 mm while the range of convenient diameters is 0,4 mm to 1,2 mm. The period required to complete one stroke of the pistons is 2,5 seconds. The speed of movement of the head at present is up to 1 metre per second. The preferred length of traverse of the head is such that the stroke of the ejector cylinder can be synchronized with the traversing stroke of the head. The nozzle is made of a wear resisting material such as a cemented carbide.
In operation, the machine is set up at the stope face 92 and is located between the hanging and footwalls 94 and 96 by the jacks 14 and 16. The outlet tubes are arranged at the correct angular position and locked by nuts 86. The position of the plate on the head 20 is adjusted by the jack screw 31 so that the nozzles 30 are the correct distance from the stope face 92. The head is caused to traverse and during this traverse a jet is emitted from one of the nozzles. On completion of a traverse, the head is moved in the reverse direction and the other nozzle 30 emits a jet. After a number of passes a slot of up to 2 inches depth may be formed in granite or I inch in quartzite. The width of the slot will be of the order of l to 2 millemetres. The setting of the outlet tubes 28 is such that two slots may be formed or that both jets act to form a single slot. When used in deep gold mines, the pressure to which the rock is subjected by the thousands of feet of rock thereabove is such that rock will spall out from the stope face when the slot is cut and it will probably be unnecessary for a pair of slots to be cut. For coal mining and other low level mining on the other hand, at least two slots are necessary and the material between these slots must be broken out.
'A modified cutter of the invention shown in FIG. 5 comprises a frame that includes end pieces 112 and 114 carrying spragging and levelling jacks 116 and 118 and being connected together by elongated guides 120. The guides 120 are comprised by a pair of piston rods which each carry intermediate its ends a piston (not shown). Cylinders 122 respectively slide on these pistons. The cylinders 122 are connected together at their ends by cross-members 124. A bracket 126 forming a head spans the cylinders 122 and carries a double acting pressure intensifier or jet generator 128' in such manner that it, the jet generator 128, can be fixed thereon in angularly adjusted positions. The bracket or head 126 can be located at either end of the cylinders 122.
Referring now to FIG. 6, the pressure intensifier or jet generator 128 comprises a body 130 formed with a central hydraulic power cylinder 132 and on either side thereof two smaller ejector cylinders 134. A double acting power piston 136 fits the power cylinder 132 and carries two piston rods 138 which fit the ejector cylinders 134 respectively to provide ejector pistons therefor. The diameter of the piston face of the power piston 136 is four times that of the ejector piston 138 so that the area of the piston face is fifteen times that of each ejector piston. Hydraulic connections 140 and 142 enter into the sides of the power cylinder 132. A valve controlled water inlet 144 enters and a water outlet 146 leaves each of the ejector cylinders 134. The water outlets each lead to a nozzle 148 having a l millimetre bore so as to eject a very fine jet.
The two hydraulic connections 140 and 142 are respectively connected to hydraulic lines (not shown) which lead to a directional control valve that connects the lines alternatively to a motor driven hydraulic pump and to drain. Both the water inlets 144 are connected via a one way valve to awater line that leads to a source of water supply. The pump is designed and arranged to supply hydraulic fluid at such a pressure and volume that the piston 136 traverses the power cylinder 134 between 0,5 and 1,0 seconds and the water jet is ejected from the nozzles at a pressure of the order of 3 to 10 kilobars.
If desired the nozzles may be connected as described paper, plywood, and plastic. A. particularly advantageous use of the cutter is for cutting asbestos.
It will be seen that with the arrangements herein described the means for providing the very high pressure of the water, i.e., the intensifier, is fixed relative to the nozzle when the machine is in use. Both the intensifier and nozzle are mounted on the head and are moved relative to the material being cut. It will be appreciated therefore that there is no necessity for providing high pressure moving seals which would be required if the nozzle were to be movable relative to the intensifier. By I avoiding this requirement the presently acute problem of how to provide such seals is obviated.
It will also be noted that the distance of the nozzles from the rock face is easily adjustable so that optimum spacing can be effected in operation. It will be appreciated that here too, the intensifier and nozzle move as one during the adjustment.
The invention is not limited to the precise constructional details herein described and illustrated. For example the intensifiers may be arranged so that jets are emitted over part only of the traverse of the head. Usually this will take place in such a way that a number of this way one or two continuous slots will be formed after two traverses.
Also if desired the water inlet to the ejector cylinders may be through a conduit co-axial with the high pressure outlets from these ejector cylinders. Suitable nonreturn valves would have to be used in such an arrangement.
1. A cutter comprising means adapted to be fixed at least temporarily in position, a nozzle operatively connected to the fixed means-and being movable relative thereto and generator means carried by the fixed means and operatively connected to and movable together with the nozzle and being adapted to supply fluid under pressure to the nozzle to produce a high velocity jet, said generator means comprising an ejector piston and an ejector cylinder discharging through said nozzle; means for actuating said generator means comprising a power piston co-axial with said ejector piston and a power cylinder connectable to a source of pressurized hydraulic fluid; a passage extending through said power piston and said ejector piston for passing pressurized fluid into said ejector cylinder; a tube connectable to a source of low pressure fluid carried by said power piston and projecting from said power cylinder, and detector means for detecting the location of the end of the tube, to control the supply of hydraulic fluid to said power cylinder.
2. A cutting device according to claim 1, wherein said pressure amplifying means consists of a double-' acting, differential piston pump, each end of which is connected to a jet nozzle.
3. A cutter comprising a frame and a head carried by said frame, a pair of nozzles and a pair of generator means, each connected to one of said nozzles, said nozzles and said generator means being carried by said head, said generator means being operatively connected to and movable together therewith relative to said frame and being adapted for supplying fluid under pressure to said nozzles to produce a high velocity jet, said generator means comprising an ejector piston and an ejector cylinder discharging through said nozzles,
means for actuating said generator means comprising a power piston and a power cylinder connectable to a source of pressurized hydraulic fluid, the exhaust sides of said power cylinders being interconnected and filled with hydraulic fluid so that as one of the power pistons moves in one direction, the other one moves in the opposite direction.
4. A cutting device for producing eroding high velocity liquid jets for slitting a rock surface, comprising:
a stationary main frame; I
a support head guided relative to said main frame for movement along the rock surface;
power means for propelling said support head along said main frame, a cutter unit carried by said support head for directing liquid jets in a direction substantially perpendicular to the direction of movement of said support head;
said cutter unit comprising a hydraulically powered pressure amplifying means and two separate jet nozzles;
said pressure amplifying means being arranged to alternately feed liquid to said two jet nozzles.
5. A cutting device according to claim 4, wherein said pressure amplifying means consists of two singleacting, differential piston pumps, each connected to a jet nozzle, said pumps being hydraulically interconnected for performing alternating power strokes.
6. A cutting device according to claim 5, wherein said pumps are connected to the jet nozzles through pipes which are adjustable to vary the locations of the nozzles.
7. A cutting device according to claim 5, wherein said pump is adjustably mounted upon the support head for varying the locations of the jet nozzles.
8. A cutting device according to claim 5, wherein the support head propelling means and said pumps are adapted to each other in such a way that the duration of a single working stroke of said pumps coincides with the full travel of the support head along the main frame. 7
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|U.S. Classification||239/752, 299/42, 239/101, 299/17|
|International Classification||E21C25/00, E21C25/60|