US3225842A - Self-propelled percussion tool assembly - Google Patents

Self-propelled percussion tool assembly Download PDF

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US3225842A
US3225842A US249851A US24985163A US3225842A US 3225842 A US3225842 A US 3225842A US 249851 A US249851 A US 249851A US 24985163 A US24985163 A US 24985163A US 3225842 A US3225842 A US 3225842A
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tool
hydraulic
carriage
valve
percussion tool
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US249851A
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William R Roeschen
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Rex Chainbelt Inc
Rexworks Inc
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Rex Chainbelt Inc
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Assigned to REXWORKS, INC., A CORP. OF DE. reassignment REXWORKS, INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: REXNORD INC.
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    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C23/00—Auxiliary devices or arrangements for constructing, repairing, reconditioning, or taking-up road or like surfaces
    • E01C23/06—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road
    • E01C23/12—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor
    • E01C23/122—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor with power-driven tools, e.g. oscillated hammer apparatus
    • E01C23/124—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor with power-driven tools, e.g. oscillated hammer apparatus moved rectilinearly, e.g. road-breaker apparatus with reciprocating tools, with drop-hammers

Definitions

  • the present invention relates to powered percussion tools of a type heretofore in use for a variety of purposes, such as the tamping of fills, cutting and breaking of pavements, driving of posts and pilings, and the like, and has as an object the provision of a novel and improved unitary organization of such a percussion tool characterized by high operative adaptablity and marked practical advantages.
  • the present invention is directed to a precussion tool including an arrangement of hydraulic components which utilizes maximum shear forces to cause complete fracture of a pavement, or complete tamping of an earth fill, through the average range of materials for each single blow; and, in addition thereto, incorporates a hydraulic dampening arrester in the tool operating assembly to stop the impact tool as soon after the point of impact as the operator may determine to be required to prevent damage. Therefore, the arrangement of the present invention does not allow the tool to follow through and cause the vertical compression and displacement shock effects on existing or new utilities arranged below the tool assembly.
  • the percussion tool assembly of the present invention has incorporated a range of approximately 3 feet in vertical adjustment from the level so that the tool can reach the desired impact area in coordination with the hydraulic dampening range.
  • the percussion tool assembly in accordance with the present invention has many uses depending upon the type of tool employed.
  • the tools may be easily interchanged.
  • the assembly may, for example, have a tool adapted to. drive posts, pilings, and the like, in a usual manner and at various angles of adjustment both with respect to a horizontal and a transverse plane.
  • the assembly may be provided with a tool adapted to serve as a chisel and the assembly applied to cut and trench through pavements of diverse composition; with a tool adapted to serve as an impact nose and the assembly operated to crush and break pavements and other solid matter; with a tool adapted to serve as a tamping foot and the assembly applied to pack and firm fills of loose materials.
  • a percusison tool of the type described is especially advantageous and effective when joined with a motor vehicle for self-propulsion at rates appropriate to move the tool from place to place along roads and highways, and for alternative travel at very slow creeping speeds susceptible of correlation with the rate of tool operation.
  • FIGURE 1 is a top plan view of a typical embodiment of the invention as arranged for practical use in one customary adjusted disposition of the percussion tool assembly,
  • FIGURE 2 is a side elevation of the organization according to FIGURE 1, broken lines in the view indicating alternative positions to which elements of the percussion tool assembly may be adjusted,
  • FIGURE 3 is a front-end elevation of the organization according to FIGURE 1 with the tool assembly in a lateral position of adjustment different from that proviously illustrated,
  • FIGURE 4 is a fragmentary, detailed segment of the assembly according to FIGURE 3 illustrating an alter native adjusted position of the percussion tool assembly
  • FIGURE 5 is a schematic drawing of the hydraulic control apparatus for operating the various hydraulic means of the percussion tool assembly
  • FIGURE 6 is a detailed view in longitudinal section of the lower end of the main hydraulic piston-cylinder assembly
  • FIGURE 7 is a fragmentary, detailed view in vertical section taken along section line 77 in FIGURE 6, and
  • FIGURE 8 is a detailed view in vertical section taken substantially along section line 88 in FIGURE 6.
  • a motor vehicle is arranged with the frame thereof including longitudinal bearer members 10 and 10 being supported by rear wheels 11 and front wheels 13 secured, respectively, to the rear axle 12 and the front axle 14.
  • a conventional motor 15 is provided to drive axle 12 and axle 14 through gearing 16 and gearing 18, respectively, in two different speed ranges, one for highway travel and one for creeping during operation of the percussion tool.
  • the conventional automotive drive for highway travel is schematically shown in FIGURE 1.
  • This drive includes the motor 15 which drives a transfer case 20 through drive shaft 19.
  • the transfer case may be adjusted in a conventional manner by lever 21 to apply power to the drive shaft 23 for the front axle gearing 16 and/or the drive shaft 25 for the rear axle gearing 18.
  • Lever 22 is the gear-shift lever for the transmission 17 of the motor 15.
  • the transfer case also con tinuously drives hydraulic pump 300 which supplies a low pressure and a high pressure hydraulic fluid for controlling the position of the tool as described in detail hereinafter.
  • the drive system as schematically described above is adequate and useful for propulsion of"themotor vehicles along roads and highways.
  • steady advancement at very slow, creep speeds greatly contributes to the effectiveness of the tool assembly for use in many operations, such as the packing of trench fills, the scoring of pavements, the breaking of pavements, and the like, and the speed ratios of conventional automotive transmissions are inadequate to provide the steady, creeping advance of the carriage appropriate for effective correlation with operation of the tool assembly without damage to the conventional equipment.
  • a feature of the instant invention is the association with the conventional automotive drive of an alternatively employable, supplementary transmission, available at the will of the operator, to apply power from the motor 15 for the provision of a creep drive.
  • the creep drive of the present tool utilizes gearing within the above-described transfer case 20, drive shafts 23 and 25, and gear boxes 16 and 18.
  • a hydraulic creep motor provides an alternative power source for the automotive drive gearing in the transfer case 20. This power source is applied to the axles through the above-described drive shafts.
  • Motor 30 is operated by low pressure hydraulic fluid supplied from pump 300 (see FIGURE 5). Pump 300 is operative at all times with motor 15.
  • the percussion tool assembly of the present invention is mounted upon the powered vehicle described above by longitudinally extending frame members 52 and 53 pivotally secured in spaced parallel relationship to the opposite frame members 10 and 10' of the motor vehicle by means of brackets 54 and 55, note FIGURE 2, which are rigidly provided on the frame.
  • the frame members 52 and 53 extend outwardly of the carriage for the motor vehicle and project beyond the end of the frame adjacent the axle 14.
  • aligned bearings 52 for example, see FIGURE 3, within which a shaft 56 is journaled.
  • Shaft 56 spans the frame members 52 and 53 transversely of the vehicle at their outer ends, Brackets 58 which are journaled on shaft 56 pivotally support the frame assembly of the percussion tool assembly, generally indicated by numeral 60, on this shaft.
  • the frame assembly 60 includes a vertical guide tower or frame 61 for the percussion tool the frame being slidably supported for horizontal movement on the two angle irons 62 arranged one above the other and forming tracks for displacement of the frame 61 transversely of the vehicle.
  • the angle irons 62 are secured in spaced relationship by the brackets 58 and by additional brackets 64. End pieces 66 also aid in securing the angle irons 62 in spaced relationship and provide limit stops for the transverse movement of the vertical frame 61 along the tracks formed by the angle irons.
  • the vertical frame 61 is supported on the angle irons 62 by a rigid box-like frame member 102 which partially surrounds the angle irons 62 and has rollers 104 and 105 journaled therein and engaging the angle iron tracks.
  • the frame member 102 is adapted to be moved along the tracks formed by members 62 by a hydraulic motor means 210 as described in detail hereinafter.
  • a rigid plate 106 is pivotally secured to the frame 102 by a pivot means 108. This plate 106 pivotally supports the vertical frame 61 which includes two U-shaped arms 109 and 110, which are secured to plate 106, and spaced upright vertical posts 112 which form the guide means for the tool and its weight 114 and are secured to arms 109 and 110.
  • the percussion tool includes heavy weight 114 which slides along the upright posts 112 and a tool 120 removably secured to the weight.
  • a lower U-shaped arm member 118 secures the bottom ends of the two posts 112 together and protects the weight 114 and the tool 120.
  • the weight 114 together with the tool 120, is raised and lowered along a path determined by the position of the upright posts 112 by means of a pulley and cable system including pulley 154 secured to the upper end of the post 112 and a multiple sheave arrangement 156, 156'.
  • the multiple sheave arrangement is used to raise and lower the weight by means of cable 152 through the action of a main piston-cylinder assembly including cylinder and piston rod 176 which is described in detail hereinbelow with reference to FIGURES 5, 6, 7, and 8.
  • the cylinder 175 and the pulley system are secured to and supported by the plate 106 by conventional bracket means as illustrated in FIGURE 2.
  • the weight 114 has guide grooves formed therein which partially surround posts 112 to maintain the same in proper position.
  • the tool assembly 61 may be adjusted with respect to the motor vehicle in various manners. For instance, the tool assembly may be moved transversely of the motor vehicle along tracks 62; the percussion tool assembly may be laid back over the motor vehicle by pivoting about axis 56 as indicated in dotted lines in FIGURE 2 in order to place the same in position for travel along roads and highways; the percussion tool may be tilted about a longitudinal axis 108' of the vehicle as illustrated in FIGURE 4; and the entire percussion tool assembly may also be raised and lowered with respect to the horizontal by pivoting about the axis where frame member 52 and member 53 are joined to the brackets 54 and 55 as illustrated by dotted lines in FIGURE 2.
  • the various movements allow many uses of the tool without moving the vehicle.
  • piston-cylinder assembly 220 which is pivotally secured to the frame member 52 by a bracket 222 and to one of the members 58 separating the angle irons 62 by brackets 224. Hydraulic fluid is supplied to a respective side of the piston to expand or retract the same and pivot the support assembly 60 about axis 56 of the shaft 56.
  • Hydraulic pressure fluid is supplied the cylinder-piston assembly 220 from a hydraulic system including the pump 30f ⁇ operated by motor 15 as desc ib d in detail ftstz Hydraulic motor 210 propels the vertical frame 61 transversely of the vehicle by means of the rollers 104 and 105' which track along angle irons 62.
  • the hydraulic motor 210 drives a gearing system 212 which meshes with gear rack 214 secured to the frame members 58 and 64. This hydraulic motor 210 also is controlled by the above mentioned hydraulic system described in detail hereinafter.
  • Tilting of the percussion tool assembly about a longitudinal axis of the vehicle, as illustrated in FIGURE 4, is accomplished by piston-cylinder assembly 230, which is pivotally secured to the box frame 102 and to the arm member 110. Expansion of the hydraulic cylinder-piston assembly pivots the plate 106, and therewith vertical frame 61 which is supported thereby, about the axis 108 of journal 108. Pins 111 projecting forwardly from the plate 106 limit the degree of pivoting.
  • Raising and lowering of the percussion tool assembly 60 vertically with respect to the ground is accomplished by pivoting the frame members 52 and 53 about the pivot points of their respective supporting brackets 54 and 55. Pivoting of the frame members 52 and 53 is accomplished by a pair of piston-cylinder assemblies 250 and 251 which are pivotally connected to the vehicle frame by brackets 254 and 255, respectively. Each assembly 250 and 251 is also pivotally secured, respectively, to one of the frame members 52 and 53 by brackets 252 and 253. Actuation of the piston-cylinder assemblies likewise is controlled by the hydraulic control system described in detail hereinafter.
  • This actuation raises and lowers the tool assembly 60 vertically with respect to the ground in an arc determined by the length of the frame members 52 and 53 and their pivot points at the brackets 54 and 55, respectively.
  • the vertical frame 61 may be maintained in its vertical position by a corresponding compensating actuation of piston-cylinder assembly 220.
  • FIGURE 5 The hydraulic system for operating the various pistoncylinder units of the percussion tool assembly and for operating the main lift cylinder 175 is illustrated in detail by FIGURE 5.
  • the system as illustrated in FIGURE includes three main valves including a selector valve 320, a dump valve 350 and a sensing valve 380 including accumulator 395 and an auxiliary valve bank 200 including six auxiliary valves 201-206.
  • Auxiliary valves 201 through 204 respectively, control operation of the pistoncylinder assemblies 251, 250, 230, and 220 for the positioning of the tool assembly 60 as described hereinabove.
  • Auxiliary valves 205 and 206 respectively, control operation of the hydraulic motors 30 and 210 for the purposes described hereinabove.
  • the valves 201-206 are conventional Vickers spool valves having a central, neutral position and two outlets.
  • the first four double throw valves which are used to supply hydraulic fluid under pressure from the pump system 300 to either side of the pistons of each piston-cylinder assembly 220, 230, 250 and 251, operate by extending or retracting the selected pistons and the last two valves are for supplying fluid to the hydraulic motors 30 and 210 for operation thereof in either direction in a conventional manner.
  • Operation of the individual cylinder-piston assemblies for positioning of the percussion tool assembly 60 is a manual operation.
  • the engine driven pump assembly 300 includes a low pressure pump 301 and a high pressure pump 302 operating, respectively, at approximately gallons per minute and 25 gallons per minute. Operation of the hydraulic motor and piston-cylinder units is accomplished by the low pressure pump 301.
  • the high pressure pump 302 is used to operate the main lift cylinder assembly.
  • auxiliary valve 201 of the valve bank 200 and line 207 to the lower side of the piston.
  • This hydraulic fluid raises or extends the piston, forcing the fluid above the piston through line 208, the auxiliary valve bank 200 and thence through return line 310, line 311 or line 313 and relief valve 312 and line 314 to the sump 315 for the pump system 300.
  • This fluid in flowing to the sump 315 may be passed through a filter 316.
  • the main lift cylinder 175 may be operated either manually or automatically by hydraulic fluid from high pressure pump 302 controlled by the system illustrated in FIGURE 5.
  • the selector valve 320 which determines the type of operation is in its neutral position. In this position, the oil is trapped behind the piston of the lift cylinder to hold the tool in a fixed position while the oil from the high pressure pump 302 is bypassed by selector valve 320 from line 321 through chamher. 322 to line 322 which is, in turn, connected to the sump tank 315 for the pump system 300.
  • selector valve 320 is in the neutral position, the oil trapped in the lift cylinder is blocked by four valves.
  • the valves are (a) the selector valve 320 where the oil in chamber 323 cannot escape into line 322' unless the selector valve spool 330 is purposely shifted; (b) check valve 340; (c) the main relief valve 345 which only will open ifthe main lift cylinder pressure exceeds a preset value greater than that required to hold the weight 114 and tool 120 in a fixed position; and (d) the dump valve 350 which only opens on automatic cycle.
  • the selector valve spool 330 In order to lower the tool 120 at a controlled rate, the selector valve spool 330 is shifted to the left, as illustrated in FIGURE 5; by the throw-arm assembly 325: This opens chamber 323 to line 322 closing the valve mentioned under (a) above. In order to raise the tool 120 at a controlled rate, the selector spool 330 is moved to the right to block passage of oil from line 321 to line 322. The flow path is then through lines 326, 352 and 400. Control of the raising speed can be achieved over a portion of the stroke of spool 330 since the flow from the high pressure pump 302 can be split by the degree of orificing between line 321 and line 322.
  • Manual lowering of the lift cylinder piston is accomplished by shifting the selector valve to allow dum ing from line 323' to line 322'.
  • the hydraulic system may also be operated on an automatic cycle which is initiated by moving the selector valve spool 330 to the right to completely block line 321. This movement also blocks line 311 and exhaust flow from the low pressure pump 301 in line 310 is forced back through line 313, back passage pressure relief valve 312 and line 381' creating a pilot pressure in passages 381 and 334 of the sensing valve 380. It is noted that the back pressure relief valve 312 is by-passed by line 311 in all other selector valve spool positions. This is done to insure against inadvertent opening of the dump valve 350 when not on automatic cycle.
  • line 353 leading to the chamber behind the dump valve spool 360 is open to the sump tank for the pump system 300 because the passage between chambers 396 and 389 of the accumulator 395 remains open and because chamber 389 is in turn connected to line 385 which is in turn open to line 386 which is always open to the sump tank through the drain 402.
  • chamber 389 is blocked and the oil in line 353 between chamber 396 and the damp valve spool 360 is trapped.
  • chamber 396 is opened to chamber 397 so that pilot pressure fluid is admitted behind the dump valve spool 360.
  • Line 387 opens to line 386 when chamber 389 becomes pressurized.
  • the accumulator spool 405 then begins to return. Note that the accumulator spool 405 cannot begin to reset prior to this time because check valve 420 prevents a back-flow to the main lift cylinder line 400 when the pressure in that line falls during acceleration.
  • the accumulator spool 405 takes a very short time to reset after line 387 opens to line 386. This means that chamber 396 will open to chamber 389 is an extremely short time since chamber 389 is now open to unrestricted pilot pressure. This, in turn, will move the dump valve spool 360 to the wide-open position in this short time at which time oil is flowing out of the lift cylinder 175 as the tool 120 is accelerating downwardly.
  • the reset spool 406 will move continuously due to the ever-increasing rate of flow passing out of the lift cylinder 175. However, as soon as the tool 120 hits bottom and the flow from the lift cylinder stops, the reset spool 406 will immediately return to its spring offset position where the oil behind the dump valve spool 360 in line 353 is released due to the fact that chamber 389 is reopened to drain through e 386. Re easing the oil from line 353 will, of course, allow the dump valve 350 to close and start the cycle over again by starting the up-stroke of the piston rod 176 for the main lift cylinder 175.
  • an adjustable hydraulic dampening arrester has been incorporated into the main lift cylinder 175 to bring the impact forces and the movement of the tool to a complete stop as soon after entering the point of impact as the operator may determine to use.
  • This hydraulic dampening arrester is illustrated in detail by FIGURES, 6, 7, and 8.
  • the arrester is incorporated into the lower end of the main lift cylinder and includes the extended lower end 192 of the cylinder which has a cross-sectional area smaller than that of the main cylinder 175.
  • the reduced lower end 192 is provided with a restricted by-passage channel 177 which due to its restricted area cushions the fall of the piston.
  • Piston rod 176 has an enlarged main piston area 180 which corresponds essentially to the diameter of the main portion of the cylinder 17 5 and is sealed with respect thereto.
  • the lower reduced end of the piston which is secured to the area 180, however, corresponds essentially in diameter to the extended end portion 192 of reduced area in the cylinder 17 5 and is sealed with respect thereto at the bottom end of the down-stroke for the piston rod 176.
  • an adjustable needle valve 199 is incorporated in the restricted escape passage leading from the annulus 191.
  • the restricted escape passage 177 extends vertically downward to a horizontal passage 181 that leads outward to the needle valve 199.
  • the escaping fluid flowing in these passages passes through an orifice 194 that cooperates with and is controlled by the needle valve 199. From the controlled orifice 194, the fluid flows through horizontal passages 179 and 183 into the reduced end portion 192 of the cylinder 175 from whence it escapes through the opening 178 into the line 400 of the hydraulic system.
  • the effective area of the restricted passage may be varied and consequently the rate of the return flow of the hydraulic fluid trapped beneath the piston 180 may be regulated to control the timing of the stroke cushioning action.
  • the downward movement of the impact tool may be arrested at any predetermined distance below the point of impact that may be appropriate to prevent damage to underlying structures and the like. This is accomplished by adjusting the length of the cable 152 to cause the checking action of the reduced cylinder end 192 to occur at a selected position of the impact tool relative to the guide tower 61 and then positioning the tower at the proper elevation to provide for the desired impact While limiting further movement or follow-through of the tool by the arresting action.
  • a percussion tool unit comprising a powered, selfpropelled carriage adapted for operation in two speed ranges, respectively, for travel on highways at moderate speeds and for creep travel when the units is in operation, and percussion tool means carried by said self-propelled carriage, the improvement comprising a frame assembly for supporting said tool means on said carriage including vertical frame means for guiding said tool means in vertical movements and horizontal movements transversely of said carriage and for tilting thereof about a first axis extending transversely of said carriage, said vertical frame means including vertical support means for guiding said tool means during vertical movements thereof,
  • said frame asembly further including means securing said vertical frame means to said carriage, said last-mentioned means being pivotally secured to said carriage for pivoting about a third axis extending transversely of said carriage whereby said vertical frame means may be raised and lowered with respect to said carriage and also being pivotally secured to said vertical frame means to form said first axis ex- 10 tending transversely of said carriage whereby said vertical frame means may be laid back over said carriage, and
  • hydraulic means for adjusting said tool means and vertical frame means in the various positions thereof with respect to said carriage including a source of hydraulic pressure fluid
  • first hydraulic means for moving said vertical support means along said track means second hydraulic means for pivoting said vertical frame means about said first axis, third hydraulic means for pivoting said vertical frame means about said third axis, and fourth hydraulic means for pivoting said vertical support means about said second axis, said first, second, third, and fourth hydraulic means being operatively connected to said hydraulic pressure fluid source,
  • a main lift piston-cylinder hydraulic unit for raising-and lowering said tool means in said vertical support means during each working stroke thereof, a hydraulic damping arrestor and buffer means in one end of said main lift piston-cylinder hydraulic unit for controlling the impact forces of said tool means at the impact end of a stroke of said tool means,
  • said track means includes a pair of angle irons extending transversely of said carriage and spaced a distance in front thereof, and wherein said means for securing said vertical support means to said track means includes roller means adapted to track along said angle irons, and wherein said first hydraulic means includes a reversible hydraulic motor secured to said means for securing said vertical support means and said track means and operatively connected to said hydraulic pressure fluid source, gear means operated by said motor and gear rack means secured to said track means, said gear means meshing with said gear rack means.
  • said means for securing said vertical support means to said track means further includes a frame partially surrounding said roller means and a plate secured thereto for pivoting about an axis constituting said second axis, said vertical support means being secured to said plate, and wherein said fourth hydraulic meansincludes a hydraulic pistoncylinder unit pivotally secured to both said frame and said plate and operatively connected with said hydraulic pressure fiuid source forpivoting said plate relative to said frame about said second axis.
  • a self-powered percussion tool unit comprising a powered, self-propelled carriage adapted for operation in two speed ranges, respectively, for travel on highways atmoderate speeds and for creep travel when the unit is in operation, and percussion tool means carried by said self-propelled carriage
  • a frame assembly for supporting said tool means on said carriage including a vertical frame means for guiding said tool means in vertical movements and horizontal movements transversely of said carriage and for tilting thereof about a first axis extending transversely of said carriage, and means securing said vertical frame means to send carriage for pivotal movement about a second axis extending transversely of said carriage whereby said vertical frame means may be raised and lowered with respect to said carriage, said securing means being pivotally connected to said vertical frame means to form said first axis extending transversely of said carriage whereby said vertical frame means may be laid back over said carriage, said vertical frame means including vertical support means for guiding said tool means during vertical movement thereof, said means securing said vertical frame means including means for supporting said vertical
  • said hydraulic means for adjusting said tool means and vertical frame means in the various positions thereof includes a source of hydraulic pressure fluid, separate hydraulically operated means operatively connected to said source for moving said vertical support means horizontally transversely of said carriage, for pivoting said vertical frame means about said first axis, for pivoting of said vertical frame means about said second axis, and for pivoting said vertical support means about said third axis, and first means for operatively connecting said main lift unit to said source of pressure fluid.
  • said means for operating said main lift unit includes a selector valve arranged in said first means for controlling the connection of said main lift unit to said source, said selector valve having three basic valve positions corresponding to manual exhaust of said main lift unit, manual lift of said main lift unit and automatic operation of said main lift unit, said selector valve including means for varying the speed of manual lifting and exhausting of said main lift unit, a dump valve controlled by a pilot pressure drawn from said source, said dump valve being operative only during automatic operation of said main lift unit to allow exhausting thereof, control means for said dump valve including second means operatively connecting said dump valve to said pilot pressure when said selector valve is in the automatic valve position thereof, and sensing valve means including a first valve operatively arranged in said first means for sensing exhaust flow from said main lift unit, means for by-passing pressure fluid through said first valve from said source to said main lift unit during lift thereof, an accumulator valve in said second means, and third means operatively connecting said accumulator valve to said first means for applying pressure from
  • a percussion tool apparatus for impacting a surface being worked, a vehicle chassis, a source of power mounted on said vehicle chassis, a generally vertical guide tower adjustably carried by said chassis, a percussion tool slidably mounted in said vertical guide tower in manner adapted to impact upon the surface being worked in performing a tamping operation or the like, a hydraulic actuator mounted on said guide tower, power transmitting apparatus operatively interconnecting said hydraulic actuator on said tower with said percussion tool slidably mounted in said tower in manner to effect reciprocation by said actuator of said tool in said tower through a stroke of predetermined length, a hydraulic buffer incorporated in said hydraulic actuator and operative thereon in manner to check and cushion the downward stroke of said tool at the lower end of its sliding movement in said guide tower, a hydraulic power system operatively connected to said source of power in manner to be driven thereby and connected to said hydraulic actuator to drive it, and means to adjust the vertical position of said adjustably carried tower relative to said vehicle chassis, whereby said tower may be positioned vertically at an elevation to cause said tool
  • a vehicle chassis including a source of power, a generally vertical guide tower movably carried by said chassis for adjustment relative thereto in positioning its lower end in desired operative relationship with a surface to be worked upon by said percussion tool apparatus, a weighted percussion tool slidably mounted in said vertical guide tower in manner adapted to impinge upon the surface being worked, a hydraulic cylinder mounted on said guide tower for adjusting movement therewith, a piston and piston rod operating in said hydraulic cylinder on said tower, a pulley and cable power transmitting apparatus operatively interconnecting said piston rod and said slidably mounted percussion tool in such manner that when said piston rod is extended from said cylinder said percussion tool is raised in said vertical guide tower, a hydraulic power and control system operatively interconnecting said source of power and said hydraulic cylinder in manner to provide for controlled actuation of said piston rod, a hydraulic buffer system incoporated in said hydraulic cylinder and operating to check and cushion the retracting movement of said piston in said cylinder as said
  • a mobile percussion tool apparatus comprising a vehicle chassis including a source of power and a hydraulic actuating and control system operatively connected to and driven by said source of power, a percussion tool carrying structure mounted on said vehicle chassis including a pair of spaced parallel supporting arms extending longitudinally of and projecting at one end of said chassis, means pivotally connecting the proximal ends of said arms to said chassis for pivotal movement in vertical planes, a generally vertical tool guiding tower adjustably connected to the projecting distal ends of said pivotally mounted arms for vertical movement therewith when said arms are pivoted, a weighted percussion tool slidably mounted in said vertical guide tower and operatively connected to a main lift piston-cylinder hydraulic unit of said hydraulic actuating and control system for lifting and dropping thereby, a hydraulic damping arrestor and buffer means in said main lift piston-cylinder hydraulic unit for controlling the impact forces of said percussion tool at the impact end of a stroke of said tool, hydraulically actuated lifting means connected to said pivotally mounted arms and operatively connected to said actuating and
  • a power driven carriage a transverse horizontal trackway movably mounted at one end of said carriage, power driven means operatively connected to raise or lower said horizontal trackway bodily relative to said carriage, a frame member slidably mounted on said movable trackway for movement therealong transversely of said carriage, a vertically disposed guideway pivotally mounted on said frame member for tilting movement about an axis disposed longitudinally of said carriage, and a percussion tool slidably mounted in said vertically disposed guideway for reciprocatory impacting operation therein, the arrangement being such that said tool guideway may be raised or lowered relative to said carriage by operation of said power driven trackway raising or lowering means and may be traversed transversely of said carriage and tilted in its transverse plane to position it for guiding said percussion tool in impacting a surface being worked, a hydraulic actuator for said percussion tool, and a variably controlled hydraulic buffer at one end of said actuator to control movement of said percussion tool after impactv References Cited

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Description

Dec. 28, 1965 w, o sc 3,225,842
SELF-PROPELLED PERCUSSION TOOL ASSEMBLY Filed Jan. '7, 1963 3 Sheets-Sheet 1 FIG.3 F|e.4
3 2 4 INVENTOR.
W. R. ROESCHEN I BY ATTORNEYS Dec. 28, 1965 w. R. ROESCHEN 3,225,842
SELF-PROPELLED PERCUSSION TOOL ASSEMBLY Filed Jan. '7, 1965 5 Sheets-Sheet 2 INVENTOR.
W. R; ROESCHEN Q-OQUMQ A TTORNE Y5 Dec. 28, 1965 w. R. ROESCHEN 3,225,842
SELF-PROPELLED PERCUSSION TOOL ASSEMBLY Filed Jan. '7, 1963 3 Sheets-Sheet 3 DUMP vi? 350 SELECTOR VALVE 320 INVENTOR W R. ROESCHEN A TTORNE YS United States Patent Wisconsin Filed Jan. 7, 1963, Ser. No. 249,851 Claims. (Cl. 173-24) The present invention relates to powered percussion tools of a type heretofore in use for a variety of purposes, such as the tamping of fills, cutting and breaking of pavements, driving of posts and pilings, and the like, and has as an object the provision of a novel and improved unitary organization of such a percussion tool characterized by high operative adaptablity and marked practical advantages.
There are two basic conditions which must be met in percussion tool construction which determine the design features necessary for such equipment. Engineering tests have shown that when fracturing street surfaces, for example, a shear force must be generated which is great enough to fracture the surface at every single blow. In so doing, the generating point of lateral shock waves is isolated when the surface is ruptured, and beyond approximately ten feet from the point of impact, the resulting vibrations are of less than 3 mils amplitude and are deemed to be within the danger to persons and danger to structures safe range. However, the vertical shock waves produced by the impact, referred to as displacement of the fill below the tool, are of serious consequence. These impact forces continue downward until compression of the underlying material resists and cancels out the imposed forces, i.e., until the impact tool meets a force sufficiently strong to stop its downward movement. Consequently, this displacement causes strain on existing utilities lying below the surface being worked on by the tool due to the pressures exerted on the pipe joints, changes of position, and scaling of old pipes and the like caused thereby. The damage may not be noticeable immediately, but frequently early failure of such utilities is a definite consequence of such vertical impact forces. Similar disadvantages are present when percussion tools are used for the tamping of earth fills. For example, if a utility has been placed in a trench and the tool is being used to tamp the earth fill, such vertical impact forces may cause displacement of the utility and thereby damage the same.
The present invention is directed to a precussion tool including an arrangement of hydraulic components which utilizes maximum shear forces to cause complete fracture of a pavement, or complete tamping of an earth fill, through the average range of materials for each single blow; and, in addition thereto, incorporates a hydraulic dampening arrester in the tool operating assembly to stop the impact tool as soon after the point of impact as the operator may determine to be required to prevent damage. Therefore, the arrangement of the present invention does not allow the tool to follow through and cause the vertical compression and displacement shock effects on existing or new utilities arranged below the tool assembly.
When installing new utilities, it is necessary to compact gently, and effectively, the first foot of dirt directly over the new installation. In all cases, this is a highly critical job and when the dirt is back-filled into the trench, there may be an existing void or air pocket and protection must be guaranteed that the impact equipment will not fall through this void and damage the utility. Here again, the hydraulic dampening control of the percussion tool operating assembly allows impact at the proper level above 0 the utility with surety that the percussion tool will not 7 fall through a void area and cause damage to the utility.
In order to effectively use this stroke checking, it is necessary to provide a means for vertical positioning of the tool since the stroke thereof is limited. The percussion tool assembly of the present invention has incorporated a range of approximately 3 feet in vertical adjustment from the level so that the tool can reach the desired impact area in coordination with the hydraulic dampening range. One of these features, i.e., the impact at the proper level and the vertical positioning of the hammer tower, without the other would be valueless.
The percussion tool assembly in accordance with the present invention has many uses depending upon the type of tool employed. The tools may be easily interchanged. The assembly may, for example, have a tool adapted to. drive posts, pilings, and the like, in a usual manner and at various angles of adjustment both with respect to a horizontal and a transverse plane. Alternatively, the assembly may be provided with a tool adapted to serve as a chisel and the assembly applied to cut and trench through pavements of diverse composition; with a tool adapted to serve as an impact nose and the assembly operated to crush and break pavements and other solid matter; with a tool adapted to serve as a tamping foot and the assembly applied to pack and firm fills of loose materials. A percusison tool of the type described is especially advantageous and effective when joined with a motor vehicle for self-propulsion at rates appropriate to move the tool from place to place along roads and highways, and for alternative travel at very slow creeping speeds susceptible of correlation with the rate of tool operation.
It is an object of the instant invention to provide a practical and efficient unitary organization for the above purposes.
Other principle objects of the present invention are to provide a mobile vehicle upon which the percussion tool is pivotally mounted in a vertical frame assembly which may be tilted with respect to the longitudinal axis ofthe vehicle and with respect to the transverse direction thereof, to provide means for mounting various tool elements in the vertical frame to drive posts, break concrete, etc., to provide hydraulic means for raising and lowering the vertical frame carrying the percussion tool with respect to the main frame, to raise and lower the tool with respect to the impact area, to adjust the frame laterally of the vehicle and maintain the frame in a desired horizontal position with respect to the vehicle when the Wheels of the vehicle encounter uneven ground, to tilt the vertical frame with respect to the longitudinal axis and transverse direction of the vehicle; and, to provide an improved control means for operation of said hydraulic means as desired.
These and other objects of the present invention will become evident with regard to the details of structure which are illustrated in the accompanying drawings, wherein:
FIGURE 1 is a top plan view of a typical embodiment of the invention as arranged for practical use in one customary adjusted disposition of the percussion tool assembly,
FIGURE 2 is a side elevation of the organization according to FIGURE 1, broken lines in the view indicating alternative positions to which elements of the percussion tool assembly may be adjusted,
FIGURE 3 is a front-end elevation of the organization according to FIGURE 1 with the tool assembly in a lateral position of adjustment different from that proviously illustrated,
FIGURE 4 is a fragmentary, detailed segment of the assembly according to FIGURE 3 illustrating an alter native adjusted position of the percussion tool assembly,
FIGURE 5 is a schematic drawing of the hydraulic control apparatus for operating the various hydraulic means of the percussion tool assembly,
FIGURE 6 is a detailed view in longitudinal section of the lower end of the main hydraulic piston-cylinder assembly,
FIGURE 7 is a fragmentary, detailed view in vertical section taken along section line 77 in FIGURE 6, and
FIGURE 8 is a detailed view in vertical section taken substantially along section line 88 in FIGURE 6.
In the organization of the improved percussion tool assembly of the present invention, as illustrated in FIG- URE 1, for example, a motor vehicle is arranged with the frame thereof including longitudinal bearer members 10 and 10 being supported by rear wheels 11 and front wheels 13 secured, respectively, to the rear axle 12 and the front axle 14. A conventional motor 15 is provided to drive axle 12 and axle 14 through gearing 16 and gearing 18, respectively, in two different speed ranges, one for highway travel and one for creeping during operation of the percussion tool.
The conventional automotive drive for highway travel is schematically shown in FIGURE 1. This drive includes the motor 15 which drives a transfer case 20 through drive shaft 19. The transfer case may be adjusted in a conventional manner by lever 21 to apply power to the drive shaft 23 for the front axle gearing 16 and/or the drive shaft 25 for the rear axle gearing 18. Lever 22 is the gear-shift lever for the transmission 17 of the motor 15. The transfer case also con tinuously drives hydraulic pump 300 which supplies a low pressure and a high pressure hydraulic fluid for controlling the position of the tool as described in detail hereinafter.
The drive system as schematically described above is adequate and useful for propulsion of"themotor vehicles along roads and highways. However, steady advancement at very slow, creep speeds greatly contributes to the effectiveness of the tool assembly for use in many operations, such as the packing of trench fills, the scoring of pavements, the breaking of pavements, and the like, and the speed ratios of conventional automotive transmissions are inadequate to provide the steady, creeping advance of the carriage appropriate for effective correlation with operation of the tool assembly without damage to the conventional equipment. Hence, a feature of the instant invention is the association with the conventional automotive drive of an alternatively employable, supplementary transmission, available at the will of the operator, to apply power from the motor 15 for the provision of a creep drive.
The creep drive of the present tool utilizes gearing within the above-described transfer case 20, drive shafts 23 and 25, and gear boxes 16 and 18. A hydraulic creep motor provides an alternative power source for the automotive drive gearing in the transfer case 20. This power source is applied to the axles through the above-described drive shafts. Motor 30 is operated by low pressure hydraulic fluid supplied from pump 300 (see FIGURE 5). Pump 300 is operative at all times with motor 15.
The percussion tool assembly of the present invention is mounted upon the powered vehicle described above by longitudinally extending frame members 52 and 53 pivotally secured in spaced parallel relationship to the opposite frame members 10 and 10' of the motor vehicle by means of brackets 54 and 55, note FIGURE 2, which are rigidly provided on the frame. The frame members 52 and 53 extend outwardly of the carriage for the motor vehicle and project beyond the end of the frame adjacent the axle 14. In the upper and outer ends of the frame members 52 and 53 are fixedly mounted aligned bearings 52, for example, see FIGURE 3, within which a shaft 56 is journaled. Shaft 56 spans the frame members 52 and 53 transversely of the vehicle at their outer ends, Brackets 58 which are journaled on shaft 56 pivotally support the frame assembly of the percussion tool assembly, generally indicated by numeral 60, on this shaft.
The frame assembly 60 includes a vertical guide tower or frame 61 for the percussion tool the frame being slidably supported for horizontal movement on the two angle irons 62 arranged one above the other and forming tracks for displacement of the frame 61 transversely of the vehicle. The angle irons 62 are secured in spaced relationship by the brackets 58 and by additional brackets 64. End pieces 66 also aid in securing the angle irons 62 in spaced relationship and provide limit stops for the transverse movement of the vertical frame 61 along the tracks formed by the angle irons.
The vertical frame 61 is supported on the angle irons 62 by a rigid box-like frame member 102 which partially surrounds the angle irons 62 and has rollers 104 and 105 journaled therein and engaging the angle iron tracks. The frame member 102 is adapted to be moved along the tracks formed by members 62 by a hydraulic motor means 210 as described in detail hereinafter. A rigid plate 106 is pivotally secured to the frame 102 by a pivot means 108. This plate 106 pivotally supports the vertical frame 61 which includes two U-shaped arms 109 and 110, which are secured to plate 106, and spaced upright vertical posts 112 which form the guide means for the tool and its weight 114 and are secured to arms 109 and 110. The percussion tool includes heavy weight 114 which slides along the upright posts 112 and a tool 120 removably secured to the weight. A lower U-shaped arm member 118 secures the bottom ends of the two posts 112 together and protects the weight 114 and the tool 120.
The weight 114 together with the tool 120, is raised and lowered along a path determined by the position of the upright posts 112 by means of a pulley and cable system including pulley 154 secured to the upper end of the post 112 and a multiple sheave arrangement 156, 156'. The multiple sheave arrangement is used to raise and lower the weight by means of cable 152 through the action of a main piston-cylinder assembly including cylinder and piston rod 176 which is described in detail hereinbelow with reference to FIGURES 5, 6, 7, and 8. The cylinder 175 and the pulley system are secured to and supported by the plate 106 by conventional bracket means as illustrated in FIGURE 2. The weight 114 has guide grooves formed therein which partially surround posts 112 to maintain the same in proper position.
As mentioned above, the tool assembly 61 may be adjusted with respect to the motor vehicle in various manners. For instance, the tool assembly may be moved transversely of the motor vehicle along tracks 62; the percussion tool assembly may be laid back over the motor vehicle by pivoting about axis 56 as indicated in dotted lines in FIGURE 2 in order to place the same in position for travel along roads and highways; the percussion tool may be tilted about a longitudinal axis 108' of the vehicle as illustrated in FIGURE 4; and the entire percussion tool assembly may also be raised and lowered with respect to the horizontal by pivoting about the axis where frame member 52 and member 53 are joined to the brackets 54 and 55 as illustrated by dotted lines in FIGURE 2. The various movements allow many uses of the tool without moving the vehicle.
The lay-back of the percussion tool assembly over the motor vehicle for travel which is illustrated by the dotted lines in FIGURE 2 is accomplished by piston-cylinder assembly 220 which is pivotally secured to the frame member 52 by a bracket 222 and to one of the members 58 separating the angle irons 62 by brackets 224. Hydraulic fluid is supplied to a respective side of the piston to expand or retract the same and pivot the support assembly 60 about axis 56 of the shaft 56. Hydraulic pressure fluid is supplied the cylinder-piston assembly 220 from a hydraulic system including the pump 30f} operated by motor 15 as desc ib d in detail ftstz Hydraulic motor 210 propels the vertical frame 61 transversely of the vehicle by means of the rollers 104 and 105' which track along angle irons 62. The hydraulic motor 210 drives a gearing system 212 which meshes with gear rack 214 secured to the frame members 58 and 64. This hydraulic motor 210 also is controlled by the above mentioned hydraulic system described in detail hereinafter.
Tilting of the percussion tool assembly about a longitudinal axis of the vehicle, as illustrated in FIGURE 4, is accomplished by piston-cylinder assembly 230, which is pivotally secured to the box frame 102 and to the arm member 110. Expansion of the hydraulic cylinder-piston assembly pivots the plate 106, and therewith vertical frame 61 which is supported thereby, about the axis 108 of journal 108. Pins 111 projecting forwardly from the plate 106 limit the degree of pivoting.
Raising and lowering of the percussion tool assembly 60 vertically with respect to the ground is accomplished by pivoting the frame members 52 and 53 about the pivot points of their respective supporting brackets 54 and 55. Pivoting of the frame members 52 and 53 is accomplished by a pair of piston- cylinder assemblies 250 and 251 which are pivotally connected to the vehicle frame by brackets 254 and 255, respectively. Each assembly 250 and 251 is also pivotally secured, respectively, to one of the frame members 52 and 53 by brackets 252 and 253. Actuation of the piston-cylinder assemblies likewise is controlled by the hydraulic control system described in detail hereinafter. This actuation raises and lowers the tool assembly 60 vertically with respect to the ground in an arc determined by the length of the frame members 52 and 53 and their pivot points at the brackets 54 and 55, respectively. The vertical frame 61, however, may be maintained in its vertical position by a corresponding compensating actuation of piston-cylinder assembly 220.
The hydraulic system for operating the various pistoncylinder units of the percussion tool assembly and for operating the main lift cylinder 175 is illustrated in detail by FIGURE 5. The system as illustrated in FIGURE includes three main valves including a selector valve 320, a dump valve 350 and a sensing valve 380 including accumulator 395 and an auxiliary valve bank 200 including six auxiliary valves 201-206. Auxiliary valves 201 through 204, respectively, control operation of the pistoncylinder assemblies 251, 250, 230, and 220 for the positioning of the tool assembly 60 as described hereinabove. Auxiliary valves 205 and 206, respectively, control operation of the hydraulic motors 30 and 210 for the purposes described hereinabove.
The valves 201-206 are conventional Vickers spool valves having a central, neutral position and two outlets. The first four double throw valves, which are used to supply hydraulic fluid under pressure from the pump system 300 to either side of the pistons of each piston- cylinder assembly 220, 230, 250 and 251, operate by extending or retracting the selected pistons and the last two valves are for supplying fluid to the hydraulic motors 30 and 210 for operation thereof in either direction in a conventional manner. Operation of the individual cylinder-piston assemblies for positioning of the percussion tool assembly 60 is a manual operation. The engine driven pump assembly 300 includes a low pressure pump 301 and a high pressure pump 302 operating, respectively, at approximately gallons per minute and 25 gallons per minute. Operation of the hydraulic motor and piston-cylinder units is accomplished by the low pressure pump 301. The high pressure pump 302 is used to operate the main lift cylinder assembly.
The operation of the several auxiliary valves is identical. Assuming for purposes of illustration, it is desired to extend the piston of cylinder-piston assembly 251, it is necessary to supply hydraulic fluid from pump 301 through auxiliary valve 201 of the valve bank 200 and line 207 to the lower side of the piston. This hydraulic fluid raises or extends the piston, forcing the fluid above the piston through line 208, the auxiliary valve bank 200 and thence through return line 310, line 311 or line 313 and relief valve 312 and line 314 to the sump 315 for the pump system 300. This fluid in flowing to the sump 315 may be passed through a filter 316.
The main lift cylinder 175 may be operated either manually or automatically by hydraulic fluid from high pressure pump 302 controlled by the system illustrated in FIGURE 5. As shown, the selector valve 320 which determines the type of operation is in its neutral position. In this position, the oil is trapped behind the piston of the lift cylinder to hold the tool in a fixed position while the oil from the high pressure pump 302 is bypassed by selector valve 320 from line 321 through chamher. 322 to line 322 which is, in turn, connected to the sump tank 315 for the pump system 300. When the selector valve 320is in the neutral position, the oil trapped in the lift cylinder is blocked by four valves. The valves are (a) the selector valve 320 where the oil in chamber 323 cannot escape into line 322' unless the selector valve spool 330 is purposely shifted; (b) check valve 340; (c) the main relief valve 345 which only will open ifthe main lift cylinder pressure exceeds a preset value greater than that required to hold the weight 114 and tool 120 in a fixed position; and (d) the dump valve 350 which only opens on automatic cycle.
In order to lower the tool 120 at a controlled rate, the selector valve spool 330 is shifted to the left, as illustrated in FIGURE 5; by the throw-arm assembly 325: This opens chamber 323 to line 322 closing the valve mentioned under (a) above. In order to raise the tool 120 at a controlled rate, the selector spool 330 is moved to the right to block passage of oil from line 321 to line 322. The flow path is then through lines 326, 352 and 400. Control of the raising speed can be achieved over a portion of the stroke of spool 330 since the flow from the high pressure pump 302 can be split by the degree of orificing between line 321 and line 322. The flow not passing from line 321 to line 322 will, of course, pass through check valve 340, line 326, across the main relief valve 345 to the sensing valve 380, and through lines 352, 391 and check valve 390 into the supply line 400 for the main lift cylinder 175. Timing valve 410 would be closed during manual operation.
Manual lowering of the lift cylinder piston is accomplished by shifting the selector valve to allow dum ing from line 323' to line 322'. The flow of fluid from the main lift cylinder 175 through line 400, forcing spool 406 to the left, line 352, line 323', chamber 323 and line 322 to sump 315.
The hydraulic system may also be operated on an automatic cycle which is initiated by moving the selector valve spool 330 to the right to completely block line 321. This movement also blocks line 311 and exhaust flow from the low pressure pump 301 in line 310 is forced back through line 313, back passage pressure relief valve 312 and line 381' creating a pilot pressure in passages 381 and 334 of the sensing valve 380. It is noted that the back pressure relief valve 312 is by-passed by line 311 in all other selector valve spool positions. This is done to insure against inadvertent opening of the dump valve 350 when not on automatic cycle.
During the up-stroke of the main lift piston rod 17 6 on automatic cycle, all of the oil from the main pump 302 passes through check valve 340 across the relief valve 345 to the sensing valve 380, through check valve 390 and into supply line 400 for the lift cylinder. A small portion of this oil will pass through line 411 to the timing valve 410, check valve 420, and line 388 to the cavity 404 above the spring-biased accumulator spool 405. This means that the accumulator spool 405 will be moving downward during the up-stroke of the lift cylinder piston rod 176. The speed of spool 405 will be determined by the setting of the timing valve 410, which is a flow control needle valve adjustable from approximately to 1 gallons per minute.
During the first portion of the accumulator spool travel, line 353 leading to the chamber behind the dump valve spool 360 is open to the sump tank for the pump system 300 because the passage between chambers 396 and 389 of the accumulator 395 remains open and because chamber 389 is in turn connected to line 385 which is in turn open to line 386 which is always open to the sump tank through the drain 402. After the accumulator spool 405 moves this first portion of its travel, chamber 389 is blocked and the oil in line 353 between chamber 396 and the damp valve spool 360 is trapped. When the accumulator spool 405 has moved further, chamber 396 is opened to chamber 397 so that pilot pressure fluid is admitted behind the dump valve spool 360. This in turn starts the dump valve spool 360 moving to the right at a controlled rate of speed determined by the size of the orifice at the entrance to chamber 397. As the dump valve 350 opens, a continuously increasing portion of the high pressure fluid is diverted from line 352 to line 351 and the pressure in the lift cylinder 175 is reduced at a controlled rate. Drain 354 removes fluid from behind spool 360.
If the pressure behind the lift cylinder piston rod 176 is released almost instantaneously the following sequence of events occur. The lift cylinder reverses instantaneously and retracts a short distance where it will pause momentarily. The weight 114, however, continues to move upward for a short time before coming to rest. At this time, there is slack in the cable supporting the weight 114. The tool then falls and takes up the slack in the cable with a high impact on the cylinder. This sequence of events happens very fast so that the slack in the cable is actually not apparent, but the situation occurs and creates severe structural loads during release. This is similar to the loads that result when a large press is decompressed without proper valving. The arrangement of the hydraulic control system described herein eliminates this situation by controlling the rate of decompression and by keeping the lift cylinder moving during the time that the weights and tools are deaccelerating.
Until the weight 114 comes to rest and starts to fall, the reset spool 406 remains in its spring offset position, as shown. As soon as the weights begin to fall, however, oil will begin to flow out of the lift cylinder. Since this oil cannot flow through check valve 390, it will push the reset spool 406 back against spring 416. Before line 400 is fully open to line 352, line 385 becomes blocked and subsequently open to line 384. This means that there will be unrestricted pilot pressure at chamber 389 as long as there is an opening between lines 400 and 352.
Line 387 opens to line 386 when chamber 389 becomes pressurized. The accumulator spool 405 then begins to return. Note that the accumulator spool 405 cannot begin to reset prior to this time because check valve 420 prevents a back-flow to the main lift cylinder line 400 when the pressure in that line falls during acceleration. The accumulator spool 405 takes a very short time to reset after line 387 opens to line 386. This means that chamber 396 will open to chamber 389 is an extremely short time since chamber 389 is now open to unrestricted pilot pressure. This, in turn, will move the dump valve spool 360 to the wide-open position in this short time at which time oil is flowing out of the lift cylinder 175 as the tool 120 is accelerating downwardly.
During the downward stroke of the tool 120, the reset spool 406 will move continuously due to the ever-increasing rate of flow passing out of the lift cylinder 175. However, as soon as the tool 120 hits bottom and the flow from the lift cylinder stops, the reset spool 406 will immediately return to its spring offset position where the oil behind the dump valve spool 360 in line 353 is released due to the fact that chamber 389 is reopened to drain through e 386. Re easing the oil from line 353 will, of course, allow the dump valve 350 to close and start the cycle over again by starting the up-stroke of the piston rod 176 for the main lift cylinder 175.
As mentioned heretofore, in order to control the vertical shock forces of the tool at the point of working, an adjustable hydraulic dampening arrester has been incorporated into the main lift cylinder 175 to bring the impact forces and the movement of the tool to a complete stop as soon after entering the point of impact as the operator may determine to use. This hydraulic dampening arrester is illustrated in detail by FIGURES, 6, 7, and 8.
The arrester is incorporated into the lower end of the main lift cylinder and includes the extended lower end 192 of the cylinder which has a cross-sectional area smaller than that of the main cylinder 175. The reduced lower end 192 is provided with a restricted by-passage channel 177 which due to its restricted area cushions the fall of the piston. Piston rod 176 has an enlarged main piston area 180 which corresponds essentially to the diameter of the main portion of the cylinder 17 5 and is sealed with respect thereto. The lower reduced end of the piston, which is secured to the area 180, however, corresponds essentially in diameter to the extended end portion 192 of reduced area in the cylinder 17 5 and is sealed with respect thereto at the bottom end of the down-stroke for the piston rod 176. As the piston rod 176 passes downwardly in the cylinder 175, hydraulic fluid is forced out of opening 178 in the lower reduced end 192 thereof and into line 400 of the hydraulic system, as previously explained with reference to FIGURE 5. The opening 178 is of relatively large cross-sectional area and provides a rapid flow of hydraulic fluid from the cylinder into the hydraulic system of FIGURE 5. As the piston approaches the end of its stroke, however, the lower reduced end 190 of the piston passes into the cylinder portion 192 which is of reduced area and thus gradually cuts off the direct outward flow of the exhausting fluid. Hydraulic fluid is thereby trapped in the annulus 191 defined between the reduced end of the piston 190 and the outer wall of cylinder 175. This trapped hydraulic fluid is utilized to cushion the downstroke of the piston 176. The hydraulic fluid trapped in annulus 191 is removed through restricted passage 177 which communicates through other passages with opening 173.
In order to provide for adjustment of the cushioning means, an adjustable needle valve 199 is incorporated in the restricted escape passage leading from the annulus 191. As shown in FIGS. 6, 7 and 8 of the drawing, the restricted escape passage 177 extends vertically downward to a horizontal passage 181 that leads outward to the needle valve 199. The escaping fluid flowing in these passages passes through an orifice 194 that cooperates with and is controlled by the needle valve 199. From the controlled orifice 194, the fluid flows through horizontal passages 179 and 183 into the reduced end portion 192 of the cylinder 175 from whence it escapes through the opening 178 into the line 400 of the hydraulic system. -By adjusting the needle valve 199 in or out of the orifice 194, the effective area of the restricted passage may be varied and consequently the rate of the return flow of the hydraulic fluid trapped beneath the piston 180 may be regulated to control the timing of the stroke cushioning action.
At the start of the next upstroke of the piston 176, hydraulic pressure fluid is admitted through the line 400 and the opening 178 into the reduced lower end 192 of the cylinder 175 to exert force upward upon the reduced end of the piston 190. While the reduced end of the piston 190 remains in the reduced cylinder end portion 192, some of the hydraulic pressure fluid flows through the restricted passage into the annulus 191. In order that this return flow of the fluid may not be unnecessarily restricted by the needle valve 199, a check valve 195 is arranged in P e circuit relationship with the needle valve 199 to bypass it. By reason of this by-pass, the fluid may flow through the passages 183 and 179 and then directly through the check valve 195 and the passages 181 and 177 into the annulus 191. In this manner the annulus 191 is quickly filled with hydraulic fiuid bypassed through the check valve 195 as the piston end 190 is pushed upward out of the lower reduced cylinder portion 192 by action of the fluid pressure.
By this arrangement of the hydraulic system, the downward movement of the impact tool may be arrested at any predetermined distance below the point of impact that may be appropriate to prevent damage to underlying structures and the like. This is accomplished by adjusting the length of the cable 152 to cause the checking action of the reduced cylinder end 192 to occur at a selected position of the impact tool relative to the guide tower 61 and then positioning the tower at the proper elevation to provide for the desired impact While limiting further movement or follow-through of the tool by the arresting action.
From the foregoing description and explanation of the operation of an improved self-propelled percussion tool apparatus constituting the presently preferred embodiment of the invention, it will be readily apparent that there has been provided an improved power driven percussion tool of the type used in the tarnping of fills, cutting and breaking of pavements, driving of posts and piles, and the like which is characterized by high operative adaptability and improved practical advantages.
While a single embodiment of apparatus illustrative of the invention has been set forth in detail by way of a full disclosure of a practical operating machine constructed in accordance with the invention, it is to be understood that the invention is not limited to this particular embodying structure which is susceptible of many changes and modifications by persons skilled in the art within the spirit of the invention and therefore the invention is not to be limited to the details of construct-ion shown and described herein but covers all such changes and modificatrons as are emcompassed within the scope of the subjoined claims.
The invention having now been fully set forth and explained, I claim as my invention:
1. In a percussion tool unit comprising a powered, selfpropelled carriage adapted for operation in two speed ranges, respectively, for travel on highways at moderate speeds and for creep travel when the units is in operation, and percussion tool means carried by said self-propelled carriage, the improvement comprising a frame assembly for supporting said tool means on said carriage including vertical frame means for guiding said tool means in vertical movements and horizontal movements transversely of said carriage and for tilting thereof about a first axis extending transversely of said carriage, said vertical frame means including vertical support means for guiding said tool means during vertical movements thereof,
track means extending transversely of said carriage, and means for securing said vertical support means to said track means for movement thereof along said track meansand for pivoting about a second axis extending longitudinally of said carriage, said frame asembly further including means securing said vertical frame means to said carriage, said last-mentioned means being pivotally secured to said carriage for pivoting about a third axis extending transversely of said carriage whereby said vertical frame means may be raised and lowered with respect to said carriage and also being pivotally secured to said vertical frame means to form said first axis ex- 10 tending transversely of said carriage whereby said vertical frame means may be laid back over said carriage, and
hydraulic means for adjusting said tool means and vertical frame means in the various positions thereof with respect to said carriage including a source of hydraulic pressure fluid,
first hydraulic means for moving said vertical support means along said track means, second hydraulic means for pivoting said vertical frame means about said first axis, third hydraulic means for pivoting said vertical frame means about said third axis, and fourth hydraulic means for pivoting said vertical support means about said second axis, said first, second, third, and fourth hydraulic means being operatively connected to said hydraulic pressure fluid source,
a main lift piston-cylinder hydraulic unit for raising-and lowering said tool means in said vertical support means during each working stroke thereof, a hydraulic damping arrestor and buffer means in one end of said main lift piston-cylinder hydraulic unit for controlling the impact forces of said tool means at the impact end of a stroke of said tool means,
means operatively connecting said main lift unit to said hydraulic pressure fluid source, and
control means in said last-mentioned means for controlling operation of said main lift unit to perform said working strokes thereof 2. A unit as defined in claim 1, wherein said track means includes a pair of angle irons extending transversely of said carriage and spaced a distance in front thereof, and wherein said means for securing said vertical support means to said track means includes roller means adapted to track along said angle irons, and wherein said first hydraulic means includes a reversible hydraulic motor secured to said means for securing said vertical support means and said track means and operatively connected to said hydraulic pressure fluid source, gear means operated by said motor and gear rack means secured to said track means, said gear means meshing with said gear rack means.
3. A unit as definedin claim 2, wherein said means for securing said vertical support means to said track means further includes a frame partially surrounding said roller means and a plate secured thereto for pivoting about an axis constituting said second axis, said vertical support means being secured to said plate, and wherein said fourth hydraulic meansincludes a hydraulic pistoncylinder unit pivotally secured to both said frame and said plate and operatively connected with said hydraulic pressure fiuid source forpivoting said plate relative to said frame about said second axis.
4. In a self-powered percussion tool unit comprising a powered, self-propelled carriage adapted for operation in two speed ranges, respectively, for travel on highways atmoderate speeds and for creep travel when the unit is in operation, and percussion tool means carried by said self-propelled carriage, the improvement comprising a frame assembly for supporting said tool means on said carriage including a vertical frame means for guiding said tool means in vertical movements and horizontal movements transversely of said carriage and for tilting thereof about a first axis extending transversely of said carriage, and means securing said vertical frame means to send carriage for pivotal movement about a second axis extending transversely of said carriage whereby said vertical frame means may be raised and lowered with respect to said carriage, said securing means being pivotally connected to said vertical frame means to form said first axis extending transversely of said carriage whereby said vertical frame means may be laid back over said carriage, said vertical frame means including vertical support means for guiding said tool means during vertical movement thereof, said means securing said vertical frame means including means for supporting said vertical support means for horizontal movement thereof transversely of said carriage and for pivotal movement thereof about a third axis extending longitudinally of said carriage, and hydraulic means for adjusting said tool means and vertical frame means in the various positions about said pivot axes and transversely of said carriage, a main lift piston-cylinder hydraulic unit for raising and lowering said tool means in said vertical support means during each working stroke thereof, a hydraulic damping arrestor included in one end of said main lift pistoncylinder hydraulic unit and including a variable control means to allow the impact forces and movements of the tool means to come to a complete stop at a control point after the point of impact, and control means for operating said main lift unit to perform said working strokes thereof.
5. A unit as difined in claim 4, wherein said hydraulic means for adjusting said tool means and vertical frame means in the various positions thereof includes a source of hydraulic pressure fluid, separate hydraulically operated means operatively connected to said source for moving said vertical support means horizontally transversely of said carriage, for pivoting said vertical frame means about said first axis, for pivoting of said vertical frame means about said second axis, and for pivoting said vertical support means about said third axis, and first means for operatively connecting said main lift unit to said source of pressure fluid.
6. A unit as defined in claim 5, wherein said means for operating said main lift unit includes a selector valve arranged in said first means for controlling the connection of said main lift unit to said source, said selector valve having three basic valve positions corresponding to manual exhaust of said main lift unit, manual lift of said main lift unit and automatic operation of said main lift unit, said selector valve including means for varying the speed of manual lifting and exhausting of said main lift unit, a dump valve controlled by a pilot pressure drawn from said source, said dump valve being operative only during automatic operation of said main lift unit to allow exhausting thereof, control means for said dump valve including second means operatively connecting said dump valve to said pilot pressure when said selector valve is in the automatic valve position thereof, and sensing valve means including a first valve operatively arranged in said first means for sensing exhaust flow from said main lift unit, means for by-passing pressure fluid through said first valve from said source to said main lift unit during lift thereof, an accumulator valve in said second means, and third means operatively connecting said accumulator valve to said first means for applying pressure from said first means against said accumulator valve to control the position of the same and thereby control the application of said pilot pressure against said dump valve and exhaust of said main lift unit, and wherein said means for adjusting the rate of said strokes includes timing valve means in said third means for regulating the pressure applied against said accumulator valve from said first means and thereby the speed at which said accumulator valve adjusts and the rate of the stroke of said main lift unit.
7. In a percussion tool apparatus for impacting a surface being worked, a vehicle chassis, a source of power mounted on said vehicle chassis, a generally vertical guide tower adjustably carried by said chassis, a percussion tool slidably mounted in said vertical guide tower in manner adapted to impact upon the surface being worked in performing a tamping operation or the like, a hydraulic actuator mounted on said guide tower, power transmitting apparatus operatively interconnecting said hydraulic actuator on said tower with said percussion tool slidably mounted in said tower in manner to effect reciprocation by said actuator of said tool in said tower through a stroke of predetermined length, a hydraulic buffer incorporated in said hydraulic actuator and operative thereon in manner to check and cushion the downward stroke of said tool at the lower end of its sliding movement in said guide tower, a hydraulic power system operatively connected to said source of power in manner to be driven thereby and connected to said hydraulic actuator to drive it, and means to adjust the vertical position of said adjustably carried tower relative to said vehicle chassis, whereby said tower may be positioned vertically at an elevation to cause said tool to impact upon the surface being worked prior to reaching the cushioned lower end of its stroke, said tool being checked and cushioned in its downward movement by said hydraulic buffer upon penetrating below the surface being worked at the point of impact thereon.
8. In a mobile percussion tool apparatus, a vehicle chassis including a source of power, a generally vertical guide tower movably carried by said chassis for adjustment relative thereto in positioning its lower end in desired operative relationship with a surface to be worked upon by said percussion tool apparatus, a weighted percussion tool slidably mounted in said vertical guide tower in manner adapted to impinge upon the surface being worked, a hydraulic cylinder mounted on said guide tower for adjusting movement therewith, a piston and piston rod operating in said hydraulic cylinder on said tower, a pulley and cable power transmitting apparatus operatively interconnecting said piston rod and said slidably mounted percussion tool in such manner that when said piston rod is extended from said cylinder said percussion tool is raised in said vertical guide tower, a hydraulic power and control system operatively interconnecting said source of power and said hydraulic cylinder in manner to provide for controlled actuation of said piston rod, a hydraulic buffer system incoporated in said hydraulic cylinder and operating to check and cushion the retracting movement of said piston in said cylinder as said percussion tool drops to the lower end of said guide tower, and power operated adjusting means connected to said source of power in manner to be driven thereby and connecting to said movably mounted guide tower in manner to adjust the position of the lower end of said tower relative to the surface being worked, the arrangement being such that said guide tower may be positioned vertically in such manner that said percussion tool will impinge upon the surface being worked prior to dropping to the lower point at which the retracting movement of said piston rod is checked and cushioned, whereby immediately after said percussion tool impinges upon the surface being worked further downward movement or penetration of said tool will be checked and cushioned by operation of said hydraulic buffer system to prevent excessive follow-through and undesired penetration of said tool below the surface being worked.
9. A mobile percussion tool apparatus comprising a vehicle chassis including a source of power and a hydraulic actuating and control system operatively connected to and driven by said source of power, a percussion tool carrying structure mounted on said vehicle chassis including a pair of spaced parallel supporting arms extending longitudinally of and projecting at one end of said chassis, means pivotally connecting the proximal ends of said arms to said chassis for pivotal movement in vertical planes, a generally vertical tool guiding tower adjustably connected to the projecting distal ends of said pivotally mounted arms for vertical movement therewith when said arms are pivoted, a weighted percussion tool slidably mounted in said vertical guide tower and operatively connected to a main lift piston-cylinder hydraulic unit of said hydraulic actuating and control system for lifting and dropping thereby, a hydraulic damping arrestor and buffer means in said main lift piston-cylinder hydraulic unit for controlling the impact forces of said percussion tool at the impact end of a stroke of said tool, hydraulically actuated lifting means connected to said pivotally mounted arms and operatively connected to said actuating and control system in manner to provide for controlled raising and lowering of said tool guiding tower, and means to adjust the position of said tower on the ends of said vertically movable arms to direct said percussion tool in dropping upon a surface being worked.
10. In a mobile percussion tool apparatus, a power driven carriage, a transverse horizontal trackway movably mounted at one end of said carriage, power driven means operatively connected to raise or lower said horizontal trackway bodily relative to said carriage, a frame member slidably mounted on said movable trackway for movement therealong transversely of said carriage, a vertically disposed guideway pivotally mounted on said frame member for tilting movement about an axis disposed longitudinally of said carriage, and a percussion tool slidably mounted in said vertically disposed guideway for reciprocatory impacting operation therein, the arrangement being such that said tool guideway may be raised or lowered relative to said carriage by operation of said power driven trackway raising or lowering means and may be traversed transversely of said carriage and tilted in its transverse plane to position it for guiding said percussion tool in impacting a surface being worked, a hydraulic actuator for said percussion tool, and a variably controlled hydraulic buffer at one end of said actuator to control movement of said percussion tool after impactv References Cited by the Examiner UNITED STATES PATENTS OTHER REFERENCES Arrow: Side-Action Mobile Hydraulic Hammer, Advertising Circular of Arrow Mfg. Co., 4 pp., received in United States Patent Ofiice, October 29, 1962.
BROUGHTON G, DURHAM, Primary Examiner,
D. FAULCONER, LAWRENCE P. KESSLER,
Assistant Examiners.

Claims (1)

10. IN A MOBILE PERCUSSION TOOL APPARATUS, A POWER DRIVEN CARRIAGE, A TRANSVERSE HORIZONTAL TRACKWAY MOVABLY MOUNTED AT ONE END OF SAID CARRIAGE, POWER DRIVEN MEANS OPERATIVELY CONNECTD TO RAISE OR LOWER SAID HORIZONTAL TRACKWAY BODILY RELATIVE TO SAID CARRIAGE, A FRAME MEMBER SLIDABLY MOUNTED ON SAID MOVABLE TRACKWAY FOR MOVEMENT THEREALONG TRANSVERSELY OF SAID CARRIAGE, A VERTICALLY DISPOSED GUIDEWAY PIVOTALLY MOUNTED ON SAID FRAME MEMBER FOR TILTING MOVEMENT AOBUT AN AXIS DISPOSED LONGITUDINALLY OF SAID CARRIAGE, AND A PERCUSSION TOOL SLIDABLY MOUNTED IN SAID VERTICALLY DISPOSED GUIDEWAY FOR RECIPROCATORY IMPACING OPERATION THEREIN, THE ARRANGE-
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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3298447A (en) * 1964-04-15 1967-01-17 Raymond Int Inc Control of variable-stroke power hammers
US3333646A (en) * 1964-11-18 1967-08-01 Kenneth H Hoen Mobile hammer unit and position control apparatus therefor
US3384186A (en) * 1966-01-24 1968-05-21 R O Products Inc Mobile hydraulic hammer
US3395766A (en) * 1965-03-09 1968-08-06 United States Steel Corp Posthole digger
US3490548A (en) * 1968-07-24 1970-01-20 Frank W Lake Adjustably positioned vehicle mounted tool and tool support structure
US3767147A (en) * 1971-10-21 1973-10-23 J Fero Drilling rig
US3917005A (en) * 1974-03-20 1975-11-04 Cannon & Associates Underground blast hole drilling machine
US3919816A (en) * 1974-05-01 1975-11-18 Raymond Int Inc Mast supporting adjustability device
DE2913438A1 (en) * 1979-04-04 1980-10-16 Salzgitter Maschinen Ag DRILLING CAR WITH A SLEDWAY
DE3013569A1 (en) * 1980-04-09 1981-10-15 Karl 6407 Schlitz Lindner Road deck stripping machine assembly support frame - has cutter, motor, pump and oil tank on frame swivelling on plate
US4619551A (en) * 1984-03-27 1986-10-28 Atlas Copco Aktiebolag Device for removing degraded concrete
DE19524389C1 (en) * 1995-07-04 1996-10-02 Georg Koehler Self-propelled vertical and horizontal drilling equipment
US10314383B2 (en) 2015-03-30 2019-06-11 Gary McClellan Thompson Wearable sports equipment carrier with personal flotation device

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US845827A (en) * 1905-12-04 1907-03-05 George F Steedman Fluid-actuated regulated cushioned hoist.
US2004146A (en) * 1932-05-20 1935-06-11 Sullivan Machinery Co Motor for pumping mechanisms
US2642845A (en) * 1950-12-20 1953-06-23 Westinghouse Air Brake Co Piston cushioning apparatus
US2651292A (en) * 1952-01-25 1953-09-08 Walter V Cornett Pneumatic cylinder hammer and control therefor
US2659584A (en) * 1950-08-23 1953-11-17 Ottawa Steel Products Inc Self-propelled hydraulic hammer
US2659583A (en) * 1950-01-16 1953-11-17 Ottawa Steel Products Inc Drop hammer and carriage therefor
US2832567A (en) * 1956-02-08 1958-04-29 J H Fletcher And Company Mobile roof drill
US2892499A (en) * 1955-09-29 1959-06-30 Anglo Paper Prod Ltd Paper machine headbox
US2928322A (en) * 1955-08-22 1960-03-15 Lawrence K Spitzer Self-propelled multi-purpose percussion unit
US3089550A (en) * 1959-05-08 1963-05-14 Watson Foundation Company Inc Excavating or drilling device
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Publication number Priority date Publication date Assignee Title
US845827A (en) * 1905-12-04 1907-03-05 George F Steedman Fluid-actuated regulated cushioned hoist.
US2004146A (en) * 1932-05-20 1935-06-11 Sullivan Machinery Co Motor for pumping mechanisms
US2659583A (en) * 1950-01-16 1953-11-17 Ottawa Steel Products Inc Drop hammer and carriage therefor
US2659584A (en) * 1950-08-23 1953-11-17 Ottawa Steel Products Inc Self-propelled hydraulic hammer
US2642845A (en) * 1950-12-20 1953-06-23 Westinghouse Air Brake Co Piston cushioning apparatus
US2651292A (en) * 1952-01-25 1953-09-08 Walter V Cornett Pneumatic cylinder hammer and control therefor
US2928322A (en) * 1955-08-22 1960-03-15 Lawrence K Spitzer Self-propelled multi-purpose percussion unit
US2892499A (en) * 1955-09-29 1959-06-30 Anglo Paper Prod Ltd Paper machine headbox
US2832567A (en) * 1956-02-08 1958-04-29 J H Fletcher And Company Mobile roof drill
US3089550A (en) * 1959-05-08 1963-05-14 Watson Foundation Company Inc Excavating or drilling device
US3172483A (en) * 1961-06-26 1965-03-09 Arrow Mfg Company Self-propelled multi-purpose percussion unit

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3298447A (en) * 1964-04-15 1967-01-17 Raymond Int Inc Control of variable-stroke power hammers
US3333646A (en) * 1964-11-18 1967-08-01 Kenneth H Hoen Mobile hammer unit and position control apparatus therefor
US3395766A (en) * 1965-03-09 1968-08-06 United States Steel Corp Posthole digger
US3384186A (en) * 1966-01-24 1968-05-21 R O Products Inc Mobile hydraulic hammer
US3490548A (en) * 1968-07-24 1970-01-20 Frank W Lake Adjustably positioned vehicle mounted tool and tool support structure
US3767147A (en) * 1971-10-21 1973-10-23 J Fero Drilling rig
US3917005A (en) * 1974-03-20 1975-11-04 Cannon & Associates Underground blast hole drilling machine
US3919816A (en) * 1974-05-01 1975-11-18 Raymond Int Inc Mast supporting adjustability device
DE2913438A1 (en) * 1979-04-04 1980-10-16 Salzgitter Maschinen Ag DRILLING CAR WITH A SLEDWAY
US4346766A (en) * 1979-04-04 1982-08-31 Salzgitter Maschinen Und Anlagen Aktiengesellschaft Drill cradle with elongated slide track
DE3013569A1 (en) * 1980-04-09 1981-10-15 Karl 6407 Schlitz Lindner Road deck stripping machine assembly support frame - has cutter, motor, pump and oil tank on frame swivelling on plate
US4619551A (en) * 1984-03-27 1986-10-28 Atlas Copco Aktiebolag Device for removing degraded concrete
DE19524389C1 (en) * 1995-07-04 1996-10-02 Georg Koehler Self-propelled vertical and horizontal drilling equipment
US10314383B2 (en) 2015-03-30 2019-06-11 Gary McClellan Thompson Wearable sports equipment carrier with personal flotation device

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