US3525404A - Rotary drilling rig with direct power drive and simplified controls - Google Patents

Rotary drilling rig with direct power drive and simplified controls Download PDF

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Publication number
US3525404A
US3525404A US707820A US3525404DA US3525404A US 3525404 A US3525404 A US 3525404A US 707820 A US707820 A US 707820A US 3525404D A US3525404D A US 3525404DA US 3525404 A US3525404 A US 3525404A
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Prior art keywords
valve
cylinder
crowd
hydraulic
fluid
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US707820A
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Elmer F Newman
Hollis H Travis
Ross Mckee
Joseph L Kelly Jr
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Hughes Tool Co
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Hughes Tool Co
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B3/00—Rotary drilling
    • E21B3/02—Surface drives for rotary drilling
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
    • E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
    • E21B19/086—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods with a fluid-actuated cylinder
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B44/00—Automatic control systems specially adapted for drilling operations, i.e. self-operating systems which function to carry out or modify a drilling operation without intervention of a human operator, e.g. computer-controlled drilling systems; Systems specially adapted for monitoring a plurality of drilling variables or conditions
    • E21B44/02—Automatic control of the tool feed
    • E21B44/06—Automatic control of the tool feed in response to the flow or pressure of the motive fluid of the drive

Definitions

  • FIGURE 1 awwg l E Filed Feb. 25, 1968 Aug. 25, 1970 NEWMAN ETAL 3,525,404
  • a rotary rig for drilling shallow holes exemplified in a truck mounted hydraulic power auger used in drilling holes for electrical transmission and distribution pole lines, pilings, foundation footings, etc.
  • the invention lies in the direct coupling of a rotary power motor to the drill stem or kelly having a drill bit (auger) mounted on its lower end for supplying torque to rotate the kelly and auger.
  • the kelly is non-circular in cross section, and received in common rotary relationship in a congruent axial opening in the shaft of the motor, preferably hydraulic, using a sliding fit to permit axial movement of the kelly.
  • a direct coupling is also used for thrust, the kelly extending above the drive motor into the bore of a hydraulic crowd cylinder and terminating in a direct connection to the piston of this cylinder, so that as hydraulic pressure is applied on the upper face of the piston this pressure is transmitted directly through the kelly to the auger.
  • Another feature of the invention lies in the combination of two or more hydraulic power units, particularly the rotary motor and crowd cylinder, with a simplified hydraulic control system.
  • a simplified hydraulic control system may be used either with or without the direct power application mentioned above.
  • two valves are used, one for a fast movement of the crowd cylinder and the other for operating the rotary motor.
  • the flow lines of these two valves are connected so that no operating fluid flows to the motor or its valve when the fast crowd valve is actuated to circulate operating fluid through the crowd cylinder, and when the fast crowd valve is in its neutral position such circulation through the crowd cylinder is blocked and,
  • An optional hydraulic circuit improvement is also disclosed, utilizing a pilot operated relief valve bet-ween the flow lines connecting the crowd cylinder and a slow crowd valve used to apply thrust when the auger is on bottom and drilling.
  • This relief valve senses the fluid pressure in the pressurized end of the crowd cylinder, and when such pressure reaches a predetermined operating value or level the relief valve is actuated to dump the infiowing fluid into the tank line.
  • a check valve in the input line locks the pressurized fluid in the cylinder, and this valve may be equipped for pilot operated reverse opening to drain off such fluid when the slow crowd valve is actuated for reverse flow to lift the auger.
  • the present invention lies in the field of rotary drilling rigs, and is described herein primarily as applied to light weight, easily transportable rotary drilling rigs peculiarly suited for drilling relatively shallow holes, e.g., to a maximum depth below the earths surface of about 50 feet.
  • Such holes may be quite variable in diameter, from three 3,525,404 Patented Aug. 25, 1970 or four inches for exploration Work to six feet or larger for the auger type bits with which the invention is exemplified below.
  • Drilling rigs of this type penetrate earth formations by rotating an anger or other type bit fixed on the lower end of a drill stem or kelly while applying an axial load through the kelly to the bit, either intermittent or steady.
  • a kindred object is to improve on prior art rotary drilling rigs which include a drill stem adapted to receive a drilling bit on its lower end and a power means to rotate the drill stern and bit by coupling such power means to the drill stem without using any intervening mechanical members.
  • Another object is to provide a rotary drilling rig which includes a drill stem, means to rotate such drill stem and means to supply axial thrust to such drill stem, each of the rotary means and thrust means being coupled to the drill stem with a minimum of mechanical coupling members.
  • a kindred object is to provide hydraulic power sources for two or more functions of a rotary drilling rig together 3 with a control system for such power sources in which no operating hydraulic fluid will be supplied to one such power source during the time a second such power source is operating, and the manipulation of a single control will transfer the flow of all available operating fluid from the second power source to the first.
  • a related object is to provide an automatic valve means in the hydraulic crowd circuit to further simplify such circuit and minimize the number of manipulations required of an operator, such valve means functioning to limit the pressure available in the crowd cylinder during the drilling operation.
  • the central shaft of the motor is hollow, the opening having a polygonal or other non-circular cross section adapted to receive in sliding relationship a portion of the drill stem having a cross section of the same shape and virtually the same dimensions, differing from the shaft opening dimensions by only suflicient clearance to provide a close sliding fit.
  • the drill stem extends through this opening in the shaft and above the motor into the hydraulic cylinder, terminating at its upper end in a fixed connection to the axially slidable piston of the crowd cylinder.
  • This connection may either be one in which the drill stem and piston rotate together, which makes for a more diflicult sealing problem between the periphery of the piston and the inside of the cylinder barrel, or, preferably, one in which only the drill stem rotates-which requires a swivel or bearing and hence does not completely eliminate all mechanical coupling members.
  • the drill stem and bit are rotated at high efficiency and with no investment in mechanical components such as a rotary table and gear connections between the motor and the rotary table.
  • the only auxiliary equipment, assuming a hydraulic drive, is the pump and its associated prime mover, and the hydraulic lines and auxiliary equipment such as valves, gages and the like, but of course these are required for the hydraulic system whether mechanical couplings are used or not.
  • the direct connection between the top of the drill stem and the piston of the crowd cylinder avoids mechanical connections such as chains and sheaves, pulleys, etc.
  • the simplified control for fast crowd and motor rotation is achieved by running the supply flow line for the motor through a type of valve for the fast crowd (by which is meant rapid lowering and raising of the kelly and anger between a position at the top of a hole, out of contact with the earth, and a drilling position at the bottom of the hole) which has three positions: (1) neutral, (2) downward operating and (3) upward operating, or reverse.
  • a type of valve for the fast crowd by which is meant rapid lowering and raising of the kelly and anger between a position at the top of a hole, out of contact with the earth, and a drilling position at the bottom of the hole
  • the neutral position the flow lines connecting the fast crowd valve with the crowd cylinder are blocked to prevent any circulation, but the supply flow line to the rotary motor is open to allow fiow to a second valve also having three positions and primarily controlling the rotary motor.
  • the fast crowd valve In both of its operating positions the fast crowd valve is connected to the crowd cylinder and the flow line to the rotary motor is blocked.
  • One such operating position is furnished to run the auger rapidly down to the bottom of the hole being dug while the other is to raise it rapidly out of the hole, usually with a load of cuttings collected on the flights of the auger.
  • the rotary motor valve may be left in its operating position for clockwise rotation of the auger while only the fast crowd valve is manipulated.
  • the optional automatic valve means in the slow crowd circuit takes the form of a relief valve connected through a pilot line to measure or sense the pressure of the fluid above the piston of the crowd cylinder, together with a check valve in the flow line supplying such flow.
  • a relief valve connected through a pilot line to measure or sense the pressure of the fluid above the piston of the crowd cylinder, together with a check valve in the flow line supplying such flow.
  • the check valve prevents any backflow of fluid out of the pressurized end of the cylinder, trapping such fluid to maintain a steady thrust on the piston, kelly and auger until these interconnected members move downward and cause the pressure to drop.
  • this dropping pressure reaches a second predetermined level, it is sensed by the relief valve and such valve is actuated back to its blocking position to allow more fluid to flow into the crowd cylinder.
  • the check valve may also be actuable by the pressure sensed through a pilot line.
  • the pilot line is connected between the check valve and the opposite of the pair of flow lines to the crowd cylinder, so that the slow crowd control valve may be used for lifting the auger oif bottom by manipulating it to its reverse operating position.
  • the check valve senses through its pilot line the pressure above the crowd cylinder piston, and moves to its reverse open condition to permit the pressurized fluid above the piston to drain through the tank return line.
  • FIG. 1 is an overall perspective showing the drilling rig raised to its operative position at the rear end of a truck bed which carries the hydraulic pumps, gasoline engine prime mover, tanks for hydraulic fluid and gasoline, and all other auxiliary equipment, the kelly and auger being shown raised so that the auger just clears the surface of the earth,
  • FIGS. 2 and 3 together are a longitudinal section through the mast assembly of the rig as disposed for typically vertical digging, although it may be disposed for off-vertical drilling by the use of one or both of its associated raise cylinder and side level cylinder, FIG. 2 showing the bottom part of the mast and FIG. 3 the upper part,
  • FIG. 4 is a schematic of the hydraulic circuit and all of the devices controlled by it
  • FIG. 4A is an enlarged schematic showing only one of the control valves of FIG. 4, and
  • FIG. 5 is a schematic of the aforementioned automatic control system for the slow crowd hydraulic circuit.
  • the overall apparatus and carrier illustrated in FIG. 1 comprise the mast assembly 10, truck 11, gasoline engine prime mover 12, pump assembly or triple pump 13, hydraulic fluid tank 14, and the pair of jacks 16R and 16L raised to elevated the truck bed :17 and thus stabilize the digger, its auxiliary equipment and the drilling load, rather than letting this weight rest on the springs of truck 11.
  • the hydraulic cylinder 18 and its piston rod 19 used to move the mast 10 between operating and transport positions
  • the rest or headache rack 21 used to support the mast in its transport position
  • the bifurcated trunnion 22 used to pivotably support derrick 10
  • the side leveling hydraulic cylinder 23 used to tilt the derrick and trunnion for otf-verticle digging, and the operator 0 and his seat and station S.
  • the principal components of the mast assembly 10* are also visible in FIG. 1, specifically hydraulic motor 50, the drill stem or kelly 60, the auger 70 fixed to the lower end of the kelly, and the crowd cylinder 80.
  • Seen at the rear of the carrier are a pair of longitudinally disposed slide rails 20 supported by a bearing 15 built into the truck bed 17 and a carriage 29 which is movable longitudinally on such rails between a forward transport position and the rearward operating position illustrated.
  • the bearing functions as a positioning table rotatable through an arc of 240 degrees centered on the longitudinal axis of the truck bed, and is operated by a pair of hydraulic cylinders 24L and 24R (not visible except in the FIG.
  • the sliding platform or carriage 29 supports the trunnion 22 and through it supports all components of the mast assembly 10, and also supports all auxiliary equipment such as prime mover 12, triple pump 13 and hydraulic tank 14.
  • the carriage 29 is slid back and forth by the action of a single hydraulic cylinder 25 (FIG. 4) supported on positioning table 15 and disposed between rails 20.
  • the lowest extending member is the drill stem or kelly 60, a non-circular cross section member which is square in the illustrated embodiment but can have any feasible shape permitting a fit into the hollow shaft 51 of rotary motor 50 to insure common rotation therewith while permitting the kelly to slide within the motor shaft.
  • the lowermost portion 61 shown in FIGS. 1 and 2, having the transverse opening 62 to receive a cross pin 63 that also fits aligned openings in the hollow shank 71 of auger 70, may be of the conventional circular cross section.
  • a non-circular cross section is preferred for better torque trsnmission to the digging tool.
  • the auger shank 71 has an internal pocket (not shown) receiving the lower end of kelly 'bar 60 so that when the kelly is loaded the crowd force is transmitted through the shank rather than through pin 63.
  • kelly 60 first passes through a shock-absorbing spring 26 floating on the kelly below the motor, and then through a. seal and packing assembly 27 designed to prevent leakage lengthwise of the kelly, this assembly being secured to the lower extension 52 of the motor shaft 51 and rotating together with the shaft and kelly but being fixed to the shaft to prevent it from moving longitudinally with the kelly.
  • the kelly then passes longitudinally through the complete length of shaft 51, including its upper extension 53 passing through the fixed coupling or mast base 30, and into the crowd cylinder 80 through its open lower end 81.
  • Kelly bar 60 then passed upwardly through crowd cylinder 80 and terminates at its top with a rounded end portion 66 which is screw threaded into a pair of lock nuts 84 disposed within piston 83.
  • a portion 67 of the kelly of intermediate diameter is also being of circular cross section and fitting within the inner periphery of the inner race member of the tapered roller bearing 85.
  • the outer race rnember of bearing 85 is press fitted within the bore of the inverted annular U-shaped body 86 of the piston, and the assembly of kelly, bearing and lock nuts 84 is prevented from slipping downwardly out of the piston by a split retaining ring 87 partially underlying the outer race member of bearing 85 and partially received in the indicated groove in inner surface of the body 86 of the piston.
  • a cup member 88 received within the hollow of piston body 86 is disposed with its annular rim 89 contacting the upper surface of the outer race member of the bearing 85, while the base 90 of cup 88 lies between the upper end 66 of the kelly and the base 91 of piston body 86.
  • a pair of interlocking set screws 92 and 93 are threaded into the indicated tapped opening in base 91 so that the lowermost screw 92 bears against base of the cup 88 and thus forces rim 89 of the cup against hearing 85 to clamp such bearing and the kelly bar between cup 88 and retaining ring 87.
  • Appropriate seals and wear rings are provided between the outer diameter of the piston 83 and the inner surface of cylinder tube 82, as illustrated.
  • Crowd cylinder 80 is provided with the open lower end 81 because it is somewhat diflicult to provide a sealable entrance for the rotating kelly 60 of polygonal cross section, and for the same reason the lower portion of the cylinder barrel 82 is threaded on its outer periphery and engages interior threads in the upper end of the longitudinal passage 31 through mast base 30.
  • the upper extension 53 of hollow motor shaft 50, and the packing 32 provided around shaft extension 53 and within the longitudinal passage 31 of the mast base the kelly extends between the rotary motor and the crowd cylinder with a minimum of leakage of hydraulic fluid between these two main power units.
  • the mast base 30 also provides a firm support for crowd cylinder 80.
  • the lower end 81 of the cylinder could be provided with a member such as shaft extension 53 to rotate with kelly 60 but remaining fixed to the end 81 to permit sliding of the kelly bar, together with the packings necessary to prevent leakage between the circular outer surface of such special member and the end 81 of the cylinder.
  • the crowd cylinder 80 is provided with a sealed and threaded upper cap 95 which serves the additional function of providing a threaded coupling 96 for a hydraulic conduit C and a connecting passage 97 for the passage of hydraulic fluid to and from the upper end of the crowd cylinder, above piston 83.
  • a similar coupling 36 and connecting passage 37 are provided in derrick base 30 for the flow of hydraulic fluid to and from the lower end of crowd cylinder 80, below piston 83.
  • kelly bar 50 may alternatively be fixed to piston 83 so that these two members rotate together as well as moving axially as a unit.
  • This modification makes it possible to eliminate the mechanical coupling provided by bearing 85, as could be done, for instance, by eliminating all parts of the piston except body 86', making body 86 a solid block except for a longitudinal passage to accommodate the upper end of the kelly bar, and securing the kelly and piston together by a threaded engagement or suitable fasteners.
  • the problem of providing against leakage between the piston and the cylinder wall would be aggravated, but this can be minimized by the use of an adequate number of the proper type and size of suitably disposed rotary seals.
  • the crowd cylinder 80 is further braced and supported by support subassembly 38, this member comprising an out-turned base flange 41 and an annular L-shaped packing retainer top memer 42 connected by circumferentially spaced stiffening fins or gussets 46.
  • Such top 42 is external threaded to receive the cap 43 which aids in pressing down on the packing ring 44 and annular packings 45 disposed in the annulus between top member 42 and barrel 82 to compress the packings axially and thus expand them radially to make them grip the confining steel surfaces of the barrel and top member.
  • This packing is not designed to prevent leakage of hydraulic fluid, but is intended primarily to stabilize the mass assembly in such a way as to avoid distortion of the cylinder at the point of engagement with the top of the support subassembly 38.
  • Such support subassembly 38 is Welded at 39 at its base 41 to the mast base 30, and the base 30 is in turn welded at 40 to trunnion bearings 28. These trunnion bearings 28 are supported by trunion 22, which thus supports the entire mast assembly 10.
  • a series of circumferentially spaced capscrews 33 extending through flange 34 of the mast base 30 secure the motor 50 in position, with its shaft 51 coaxially aligned with crowd cylinder 80 and disposed below the same.
  • the hydraulic motor 50 (which can be replaced by an electric motor, air motor, etc., see below) is not shown in detail because the present invention does not include the motor considered by itself, and also because each manufacturer regards the details of his own motor as proprietary information at the present time. It is suflicient to observe here that for drilling purposes such motor should develop high torque under load over a range of rotary speeds from about 150 revolutions per minute (r.p.m) down to r.p.m. or virtually to stalling. It must also be provided with a shaft of sufficient cross section to be made with an opening therethrough to receive in axially sliding interfit a kelly or drill stern of non-circular cross section, as this is necessary to make the present invention operable.
  • a particular hydraulic motor that is commercially available and has been successfully used in an actual reduction to practice of the present invention is a Model MHT-250 Vane Motor made by Vickers Incorporated, a division of Sperry Rand Corporation. This motor has the following characteristics:
  • Torque 4500 lb.-ft. at 2000 p.s.i. pressure drop over motor, from 5 r.p.m. to 150 r.p.m. Efficiency:
  • the principal components of the hydraulic system include the usual fluid reservoir or tank 14, pumps 13a, 13b and 13c which are actually sections of the single shaft triple pump 13, valve bank assembly 102 and its associated supply 103 and tank return line 104, valve bank assembly 106 and its supply line 107, this bank also being connected to return line 104, and foot valve 109.
  • the bank 102 includes the valves 111, 112 and 113, for controlling the high flow rate devices of the system, respectively crowd cylinder 80 (for fast operation) rotary motor 50 and winch. motor 75.
  • Bank 106 includes the valves 121 through 129 for controlling the devices requiring a lower rate of flow, respectively from bottom to top side leveling cylinder 23, positioning cylinders 24L and 24R, raise cylinder 18, crowd cylinder 80 (slow crowd) slide cylinder 25, left and right jack cylinders 16L and 16R, pole extender cylinder 76 and pole grabber cylinder 77.
  • crowd cylinder 80- is connected for flow control through both the fast crowd cylinder 111 and slow crowd cylinder 124, the fast crowd being used to run the bit or anger into the hole and pull it out while the slow crowd is used to apply thrust to the auger during the digging operation.
  • valves 111 and 124 Normally only one of the valves 111 and 124 is actuated at any one time, but they are not interlocked to prevent simultaneous closing because no particular damage can result from such an occurrence.
  • the slow crowd valve is normally opearted intermittently, being actuated to its downward digging position (crossed arrows) for a few seconds and then returned to its illustrated neutral position to apply a steady thrust until the auger digs downwardly and reduces the pressure above the piston.
  • a special tank line 108 is provided for positioning table cylinders 24L and 24R to keep them filled with oil.
  • the operation of these two cylinders is somewhat unusual, as suggested by the symbolic sprocket 56 and the chain 57 passing around the sprocket and secured at its two ends to the piston rods 58 of cylinders 24L and 24R.
  • the piston of 24L moves to the right, for instance, to rotate the sprocket 56 and thus rotating positioning table 15 in the counterclockwise direction, the piston of the other cylinder 24R necessarily must move to the left.
  • the slow crowd valve 124 is the only valve in bank 106 which is more or less continuously operated.
  • the jacks 16L and 16R are operated only at the beginning and conclusion of the digging, and the same is true of raise cylinder 1-8, slide cylinder 25, turntable cylinders 24L and 24R, and if it is used at all, side level cylinder 23.
  • the pole extender and pole grabber cylinders 76 and 77 are only needed sporadically.
  • check valves 133 With respect to various elements in the flow lines, check valves 133, pressure snubbers (orifice type gage protectors) 134, pressure gages 136, pressure relief valves 137 and filters 138 are conventional, the filters being largely to protect operating components such as motor 50.
  • Motor 50 is provided with a special drain line 139 connected between its casing or housing and tank 14 to drain off the hydraulic fluid which leaks past the vanes of the motor and thus protect the seals against pressure build-up.
  • Low opening pressure (5 p.s.i.) check valve 141 is provided to insure that the motor case remains filled with fluid for proper lubrication.
  • tank 14 is also equipped with an externally visible fluid level and temperature gage 143.
  • Pump section 130 having a 58 gallons per minute (g.p.m.) capacity, is connected directly through branch supply line 103a to the truck line 103, whereas pump section 13b, having a g.p.m. capacity, is connected first to foot pedal operated valve 109.
  • This valve 109 is normally used only in pulling the loaded auger out of a hole and during the throw or cuttings disposal step, when the extra speed obtained in using the two pump sections in parallel results in high centrifugal forces on the cuttings carried on the auger flights and permits them to be thrown clear of the hole, and in returning the empty auger to the bottom of the hole.
  • the second feature of the invention discussed in the introduction lies in the interconnection of fast crowd valve 111 and its connections to both the crowd cylinder 80 and the continuation of supply line 103 leading to valve 112 for rotary motor 50.
  • each of these valves is in its neutral position and, assuming the pump to be operating, all fluid is circulated through supply line 103 and back to tank 14 through return line 104, since winch valve 113' is also in neutral position. (Because winch 75 is used only in special situations, it will not be further discussed).
  • valves 111 and 112 may be actuated to their forward positions (right in the figure) simultaneously. Since valve 112 has a detent 120 to keep it in the forward position, it will stay put and the operator can usually ignore the valve '112 until the hole is completed. The movement of fluid through valve 111 and crowd cylinder 80 will rapidly lower the auger to the bottom of the hole, at which time all that the operator need do is release the handle 130 linked to spool 114 of the fast crowd valve 111.
  • this spool Since this spool is spring biased to the neutral position at both ends, as symbolized by the spring symbols 135 depicted in the figure at each end of spool 114, it will return to the neutral position as soon as released. All fluid flow through valve 111 and crowd cylinder 80 will immediately stop, and all flow will be immediately diverted to valve 112 and through it tomotor 50-merely on the operators releasing a single valve control.
  • the forward position of the spool 114 of valve 112 is that appropriate for screwing the anger into the earth formation, it will automatically carry on this operation, and the operator will call forth the necessary slow crowd by manipulating the spool of slow crowd valve 124 between the forward and neutral positions, this being the only control he need lay a hand on during the entire angering operation.
  • FIG. 5 illustrating an optional improvement consisting of a pilot operated relief valve 147 and a check valve 148 connected in the portion of the hydraulic circuit which includes the flow lines 117 and 118 interconnecting crowd cylinder 80 and its fast crowd and slow crowd valves 111 and 124' (the latter differing from valve 124 of FIG. 4 only in that valve 124' includes a detent 140 for retaining the valve in the forward position, wherein line 117 is connected to supply line 107 and line 118 is connected to tank line 104).
  • valves 147 and 148 make for simplicity of control in that during the angering step the slow crowd valve 124' may be actuated to its forward or first position (fast crowd valve 111 being in its neutral position shown in the drawing) and left there for the balance of the angering operation. Without these valves 147 and 148 the operator will apply crowd to the auger by intermittently actuating slow crowd valve 124 to the forward position and back to the illustrated neutral position.
  • valves 147 and 148 The sequence of operation (automatic) of valves 147 and 148 is as follows. With valve 124' actuated to the forward (crossed arrows) position, hydraulic finid flows through such valve, line 117 and through check valve 148 into the piston end of crowd cylinder 80. The resistance of the earth formation being drilled causes the pressure of the fluid in line 117 and in the cylinder above the piston to increase. Pilot line 149 senses this pressure, and when such pressure reaches a value determined by a prior adjustment of valve 147, e.g., 500 p.s.i., valve 147 shifts from the blocking condition shown in the drawing to provide a straight through path between 117 and 118. Such a path is a direct short circuit, and no more fluid will flow into crowd cylinder until some further change occurs.
  • a prior adjustment of valve 147 e.g., 500 p.s.i.
  • check valve 148 remains closed to trap the fluid above the piston of the cylinder under the same 500 p.s.i. pressure to thus maintain a steady downward force on the angen.
  • this pressure drops because the formation being cut has been moved up on the auger flights and the piston moves down somewhat within the crowd cylinder.
  • the reduced level of this pressure being sensed by pilot line 149 and valve 147, causes valve 147 to return to its original blocking position shown in the drawing at a second preset operating pressure, e.g., 375 p.s.i. This removes the short circuit between lines 117 and 118 and permits more fluid to enter the piston end of crowd cylinder 80 for a further step in the angering cycle.
  • the check valve 148 may be selected for opening in the reverse direction (right to left in the drawing) when acted on by a pressure sensed through a pilot line 150 connected to sense the pressure in the rod end of crowd cylinder 80.
  • a pilot line 150 connected to sense the pressure in the rod end of crowd cylinder 80.
  • Fluid will flow into the rod end of crowd cylinder 80, and, assuming fluid to be trapped under pressure in the piston end of the crowd cylinder, the pressure in the rod end and its supply line 118 will build up rapidly. This buildup is sensed by valve 148 through pilot line 150 and it will open as soon as the pressure in 150 reaches its own characteristic reverse operating pressure, e.g., p.s.i.
  • the fluid trapped under pressure in the piston end of the crowd cylinder will flow out through line 117 and valve 148 to the tank until control valve 124' is returned to its neutral position.
  • Valve 147 is inactive during this reverse operation because it is of the type that permits flow in one direction only, here from 117 to 118.
  • check valve 148 enables the operator to both lift on the auger and rotate it in reverse, a choice sometimes desirable in freeing a stuck auger. It also permits him to give the auger a short burst of lifting power, sometimes all that is necessary to free the anger, without disturbing the normal drilling positions of fast crowd valve 111 (neutral) and rotary motor valve 112 (detented for clockwise rotation) and thus without delaying the angering operation.
  • Foot pedal valve 100 is also normally manipulated to the forward position at this same time, to provide extra flow by coupling pump section 1312 in tandem with 130 and thereby increase the speed at which the auger is raised. It should be noted that nothing has been done to valve 112 since starting the cycle, and it has remained detented in its initial forward position. The movement of the spool 114 of valve 111 to the rearward poistion blocks the flow of all fluid to the motor 50 and thus halts rotation of the auger by inserting a block 119 in supply line 103, just as in the forward position of valve 111.
  • valve 111 When the auger has been fully raised out of the hole, all that the operator is required to do is release the handle of valve 111, again permitting the spring acting on spool 114 to return the spool to the neutral position. All fluid flow is immediately diverted from valve 111 and crowd cylinder 80 to flow through valve 112, still in its forward position, and through rotary motor 50.
  • the foot valve 109 is still in its forward position to obtain extra speed from auxiliary pump section 13b, and the motor consequently accelerates rapidly, and with it kelly 60 and auger 70.
  • the cuttings collected on the auger flights 72 are rapidly thrown clear of the hole, and the operator prepares for another cycle by again manipulating the fast crowd valve 111 to its forward position. Foot pedal valve 109 is held in position to keep pump section 1311 connected to the supply line 103 until the auger again reaches the bottom of the hole.
  • valve 112 controlling rotary motor 50 may be left in its forward position.
  • the same direction of rotation used for angering into the earth is normally used for throwing the cuttings clear of the auger and hole.
  • the reverse direction is used only in the event the auger becomes stuck and has to be backed out, or when clearing the auger of collected cuttings having a sticky nature. In the latter case the auger is rapidly reversed over the hole to shake these cuttings loose.
  • the cross link 151 of valve 112 which ties together lines 154 and 155 running between the valve and the motor, is present only when the valve 112 is in the neutral position illustrated.
  • Any type motor may be mounted with its axis in a vertical (or otf-vertical) position in coaxial alignment with a kelly and crowd cylinder, so long as it provides high torque at low speeds and its shaft may be provided with a non-circular longitudinal passage to receive and rotate a similarly cross-sectioned kelly bar and permit the kelly to move axially through such opening.
  • Any suitable electrical motor which satisfies these requirements may be substituted, and also suitable motors powered by other circulating fluids such as air.
  • the crowd cylinder may be powered by other available fluids and means, just so the piston of the cylinder can be attached to the top of the kelly and exert a steady force on it, variable on demand. It is also within the invention to use any suitable crowd means when 21 directly coupled rotary motor is employed.
  • hydraulic controls and operating units is not limited to the direct coupling feature of the invention, although it finds its greatest utility therein.
  • Prior art systems utilizing a hydraulic power unit to rotate a drill stem or kelly and another hydraulic power unit to exert an axial thrust on the kelly may be advantageously combined with the interlocking valve controls of the present invention, even though such driving units are mechanically coupled to the driven devices.
  • the present invention is not necessarily limited to the described auger types of drill bit.
  • Rolling cutter bits and drag bits may also be used, providing a suitable circulation system to flush the cuttings out of the hole is added.
  • Such bits have the advantage of requiring no throwoif operation, as with an auger, but they are not as fast as augers in penetrating soft earth and find their greatest utility in cutting through rock formations.
  • valve means used to control the flows to the crowd cylinder and rotary motor may take other forms than the two valves 111 and 112 shown in FIG. 4.
  • valve 1112 could be eliminated entirely, as its chief purposes are to provide for reverse rotation and an independent neutral position to completely stop the motor when the fast crowd valve 112 is in neutral position. The latter function can be accomplished by shutting down the pumps, and reverse rotation can also be sacrificed.
  • a single valve to replace both valves 111 and 112 and yet accomplish all the functions of both may also be substituted, provided it is either equipped with more position so auxiliary valves and pilot lines are added which operate automatically in response to pressure changes. Specific circuits are not illustrated because many such circuits will now occur to those skilled in the art.
  • hydraulic fluids such as MS grade number engine oil (MS meaning motor usage, severe service) are preferred, it is within the contemplation of the invention to use any suitable fluid which is compatible with the materials of the power units and other elements of the system, whether liquid, gaseous or combinations.
  • MS grade number engine oil MS meaning motor usage, severe service
  • any suitable fluid which is compatible with the materials of the power units and other elements of the system, whether liquid, gaseous or combinations.
  • hydraulic fluid has this meaning and the adjective hydraulic" modifies a word implying a unit or element compatible with or capable of utilizing a fluid as thus broadly described.
  • a rotary drilling rig comprising (1) an elongated drill stem having a non-circular cross section along at least a portion of its length, an upper end, and a lower end adapted to have a rotary digging tool secured thereon,
  • a hydraulic rotary motor adapted to be secured above ground with its axis of rotation making an angle with the surface of the ground, said motor having a hollow shaft with a lengthwise opening therethrough of approximately the same non-circular cross section and receiving said portion of the drill stem in common rotary relationship and with a snug sliding fit to permit axial motion of the drill stem within the motor shaft, said drill stem as thus received, including a part of said non-circular cross section, extending above said motor in pre-drilling position,
  • a hydraulic crowd cylinder disposed above said motor in coaxial relationship therewith, said crowd cylinder receiving the part of said kelly extending above the motor and having a piston coupled to the upper end of the drill stem for at least common axial movement therewith between the ends of the cylinder to raise and lower the drill stem, and
  • said hydraulic system including valve means for simplified control of the rotation of said hydraulic motor and the up and down movements of the piston of the hydraulic crowd cylinder, said valve means including a manually controlled valve movable to at least a first position in which hydraulic fluid is circulated through the crowd cylinder in the piston-lowering direction and all flow through the rotary motor is blocked, and a second position in which hydraulic fluid is circulated through the rotary motor and not through the crowd cylinder, whereby when the valve is in its first position the drill stem and digging tool will be lowered without rotation until the digging tool contacts an earth formation, and, by manipulating said valve from its first to its second position the drill stem and digging tool will be rotated without supplying hydraulic fluid to the crowd cylinder through said valve.
  • the rotary drilling means of claim 1 in which said manually controlled valve also includes a third position in which hydraulic fluid is circulated to said crowd cyliner in the piston-raising direction and none is circulated to said rotary motor, whereby said digging tool may be raised from engagement with an earth formation without rotating it by manipulating said valve from its second position to said third position.
  • valve means consists of two separate valves, the first being said manually controlled valve having said first and second positions and the second being a valve having at least a first position providing a path for the flow of fluid from said first valve to said rotary motor to cause it to rotate the digging tool in its normal rotary direction, whereby when said first valve is in its first position and said second valve is in its first position said digging tool may be lowered without rotation from a raised position above the earth to an earth-contacting position, and said auger may then be rotated in contact with the earth solely by manipulating said first valve from its first to its second position to divert said fluid from the crowd cylinder to the rotary motor.
  • said hydraulic and control system further includes a second valve means actuated by an operator to control the circulation of fluid through said crowd cylinder and an automatic valve means to control and limit the pressure in the pressurized-digging end of said cylinder
  • said automatic valve means comprising both a normally blocking pilot operated relief valve connected between the flow lines linking said second valve means and the crowd cylinder and a check valve connected in the one of said flow lines connected to the pressurized-digging end of the cylinder to permit flow in said flow line only in the direction toward said end of the cylinder, the relief valve being connected through a pilot line to a point in the circuit sensing the pressure of the fluid in the pressurized-digging end of the cylinder and being actuable to an open position when the pressure in said end reaches a predetermined level for which the relief valve is set.
  • a drilling rig which includes an elongated drill stem adapted to support a drill bit on its lower end, a first hydraulic power means coupled to said drill stem to rotate the drill stem while permitting it to move longitudinally, and a second hydraulic power 15 means coupled to the drill stem to move it longitudinally,
  • a hydraulic circulation and control system which includes a valve means furnishing a simplified control of said first and second hydraulic power means, said valve means including a manually controlled valve having at least a first position in which hydraulic fluid is circulated through said second power means in the direction to lower said drill stern and bit, and the flow of fluid through said first power means is blocked, and a second position in which hydraulic fluid is circulated through the first power means but not through the second.
  • a drilling rig which includes a drill stem having a portion of its length of non-circular cross section adapted to support a drill bit pendent from its lower end, a rotary member adapted to be supported above the earth with its axis of rotation oriented at an angle to the earths surface and having a similarly oriented opening therethrough centered on said axis, said opening having a cross section of similar non-circular shape receiving said portion of the drill stem with a close sliding fit for common rotation therewith, hydraulic thrust means connected to said drill stem to move it axially with respect to said rotary member, and hydraulic power means coupled to said rotary member to rotate it and the drill stem and bit when said bit is in contact with an earth formation to be drilled:
  • a hydraulic circulation and control system which includes a hydraulic valve means furnishing a simplified control of the operation of said hydraulic thrust means and said hydraulic power means, said valve means including a manually controlled valve having at least a first position in which hydraulic fluid is circulated through said thrust means in the direction to lower said drill stem and bit, and the flow of fluid through said hydraulic power means is blocked, and a second position in which hydraulic fluid is circulated through the power means but not through the thrust means, whereby when the drill stem and drill bit are above ground said valve may be set in its first position to lower the drill bit without rotating it into contact with the ground, and said bit may then be caused to rotate solely by manipulating said valve from its first to its second position.
  • the improvement drilling rig of claim further improved by the addition of a second hydraulic valve means, such additional valve means 'being actuable to increase the rate of flow of the hydraulic fluid circulated by the first valve to said hydraulic thrust means and hydraulic power means to thereby increase the speed with which said drill stem is rotated and moved axially.
  • said manually controlled valve includes a third position wherein hydraulic fluid is circulated through said hydraulic thrust means in the direction to raise said drill stem and bit and none is circulated through the hydraulic power means coupled to said rotary member, whereby said drilling operation of rotating the drill stem and bit may be stopped and these members may be raised from the hole being dug solely by manipulating said valve means from its second position to its third position.
  • the improved drilling rig of claim 12 further improved by the addition of a second hydraulic valve means, such additional valve means being actuable to increase the rate of flow of the hydraulic fluid circulated by the first valve to said hydraulic thrust means and hydraulic power means to thereby increase the speed with which said drill stem is rotated and moved axially.
  • An earth penetrating rotary drilling rig comprising a drill stem adapted to be disposed to intersect the surface of the earth with a drill bit fixed to its lower end and mounted for rotary movement and movement along its own longitudinal axis, a hydraulic motor coupled to said drill stem to rotate it, and a hydraulic crowd cylinder also coupled to the drill stem to lower and raise such drill stem and drill bit into and from contact with earth formations to be drilled, and further comprising a synchronized pair of hydraulic valves to control the sequential operation of said motor and crowd cylinder connected in the hydraulic lines which supply said motor and crowd cylinder with operating fluid,
  • the first of said valves being a manually controlled valve having a first position permitting the flow of operating fluid to the crowd cylinder and blocking the flow of such fluid to the second valve, and also having a second position blocking the flow of operating fluid to said crowd cylinder and permitting such flow to the second valve,
  • a cycle of lowering the bit to contact said bottom and then rotating it may be completed by preliminarily placing the first valve in its first position and the second valve in its first position to lower the drill bit into contact with the bottom of the hole and then shifting the first valve to its second position.
  • the drilling rig of claim 14 which includes a third valve connected in separate hydraulic lines to said crowd cylinder to supply operating fluid thereto independently of said first and second valves, said third valve having at least a first position blocking all flow to the crowd cylinder through the separate hydraulic lines and a second position permitting such flow.
  • a drilling rig which includes a drill stem adapted to be mounted at an angle to the earths surface with a I drilling bit secured on its lower end, rotary means coupled to the drill stem for common rotation but permitting axial movement of the drill stem toward and away from the earth, and a hydraulic crowd cylinder coupled to said drill stem for forcing it into the earth, the opposite ends of said cylinder being connected to a pair of hydraulic flow lines for supplying fluid to one said end and returning it to a reservoir from the other, the improvement comprising automatic valve means to limit the thrust applied through said drill stem and bit, said automatic valve means comprising:
  • a pilot operated relief valve between said pair of flow lines and connected by a pilot line to sense the pressure in the pressurized-digging end of the cylinder, said valve having a normally closed position in which it blocks all flow between said pair of flow lines and an open position to which it is actuated by the pressure of the fluid in said pilot line when such pressure reaches a first predetermined level, said re lief valve in such open position permitting the flow of fluid only in the direction from the one of said pair of flow lines connected to the pressurized-digging end of the crowd cylinder to the other flow line, said relief Valve being adapted to be returned to its closed position when the pressure of the fluid in said pilot line reaches a second and smaller predetermined level, and

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  • Fluid Mechanics (AREA)
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  • Geochemistry & Mineralogy (AREA)
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US707820A 1968-02-23 1968-02-23 Rotary drilling rig with direct power drive and simplified controls Expired - Lifetime US3525404A (en)

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US3674098A (en) * 1969-11-03 1972-07-04 British Steel Piling Co Ltd Drilling rigs
US3705634A (en) * 1969-08-14 1972-12-12 Antonio Casagrande Universal machine for foundations
US3768578A (en) * 1971-11-12 1973-10-30 W Russell Rotary & linear driven double-acting cylinder
US3817337A (en) * 1972-09-08 1974-06-18 P Panak Machine for making holes in putting greens
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US4474249A (en) * 1982-09-29 1984-10-02 Hughes Tool Company Kelly seal
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US5062490A (en) * 1989-12-22 1991-11-05 Central Mine Equipment Kelly bar coupling
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US20040173383A1 (en) * 2001-06-04 2004-09-09 Hollingsworth John R. Apparatus and method for rotary bored drilling
WO2008134896A1 (en) * 2007-05-08 2008-11-13 Utilicor Technologies Inc. Excavating method and apparatus
WO2009082322A1 (en) * 2007-12-21 2009-07-02 Atlas Copco Rock Drills Ab A pulse generating device and a rock drilling rig comprising such a device
US20110108324A1 (en) * 2009-11-11 2011-05-12 Flanders Electric, Ltd. Methods and systems for drilling boreholes
US20120181234A1 (en) * 2009-11-24 2012-07-19 Anders Nydahl Filter and method for filtration of hydraulic oil in a return line to a hydraulic tank, and a drilling rig comprising the filter
US8327950B2 (en) 2010-08-06 2012-12-11 Utilicor Technologies Inc. Excavation apparatus
CN102937018A (zh) * 2012-10-31 2013-02-20 中联重科股份有限公司 全摩阻式钻杆的加压控制方法、设备和旋挖钻机
CN103912222A (zh) * 2014-01-03 2014-07-09 上海中联重科桩工机械有限公司 滑动组件、旋挖钻机及其桅杆装置组件、旋挖钻机桅杆的加压油缸的免拆卸运输方法
CN105019882A (zh) * 2015-08-14 2015-11-04 郑州宇通重工有限公司 一种旋挖钻机回转对中操作控制装置
CN106351900A (zh) * 2016-09-27 2017-01-25 桂林航天工业学院 一种防偏斜凿岩控制系统
CN107269259A (zh) * 2016-04-04 2017-10-20 包尔机械有限公司 用于土方加工的设备和方法
US9856698B2 (en) 2015-09-25 2018-01-02 Utilicor Technologies Inc. Self-propelled, towable coring apparatus
CN107795279A (zh) * 2017-12-06 2018-03-13 徐工集团工程机械有限公司 钻井机和工程车辆
US20180363437A1 (en) * 2011-04-07 2018-12-20 Evolution Well Services, Llc Dual pump vfd controlled motor electric fracturing system
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US11585204B2 (en) * 2020-05-26 2023-02-21 Heath Poulson Crowding avoidance apparatus and method
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US3705634A (en) * 1969-08-14 1972-12-12 Antonio Casagrande Universal machine for foundations
US3674098A (en) * 1969-11-03 1972-07-04 British Steel Piling Co Ltd Drilling rigs
US3768578A (en) * 1971-11-12 1973-10-30 W Russell Rotary & linear driven double-acting cylinder
US3817337A (en) * 1972-09-08 1974-06-18 P Panak Machine for making holes in putting greens
US4050526A (en) * 1975-05-07 1977-09-27 Foresight Industries Post driving machine
US4261251A (en) * 1979-10-04 1981-04-14 Hughes Tool Company Kelly head for hydraulic mast digger
US4474249A (en) * 1982-09-29 1984-10-02 Hughes Tool Company Kelly seal
US4971158A (en) * 1987-12-21 1990-11-20 Oy Tampella Ab Method in rotary drilling and rotary drilling apparatus
US5062490A (en) * 1989-12-22 1991-11-05 Central Mine Equipment Kelly bar coupling
US5158146A (en) * 1991-03-08 1992-10-27 Fuller Frank E Mobile foxhole excavator
US20040173383A1 (en) * 2001-06-04 2004-09-09 Hollingsworth John R. Apparatus and method for rotary bored drilling
US20040112613A1 (en) * 2002-12-13 2004-06-17 Mcgivery John W. Excavation system and method
US7128165B2 (en) * 2002-12-13 2006-10-31 Enbridge Technology Inc. Excavation system and method
US20070012463A1 (en) * 2002-12-13 2007-01-18 Enbridge Technology Inc. Excavation system and method
US8096367B2 (en) 2002-12-13 2012-01-17 Enbridge Technology Inc. Excavation system and method
WO2008134896A1 (en) * 2007-05-08 2008-11-13 Utilicor Technologies Inc. Excavating method and apparatus
US20080277131A1 (en) * 2007-05-08 2008-11-13 Edward Marshall Pollock Excavating method and apparatus
US7757780B2 (en) 2007-05-08 2010-07-20 Utilicor Technologies Inc. Excavating method and apparatus
WO2009082322A1 (en) * 2007-12-21 2009-07-02 Atlas Copco Rock Drills Ab A pulse generating device and a rock drilling rig comprising such a device
US20110000695A1 (en) * 2007-12-21 2011-01-06 Fredrik Saf Pulse generating device and a rock drilling rig comprising such a device
CN101842194B (zh) * 2007-12-21 2013-04-24 阿特拉斯·科普柯凿岩设备有限公司 脉冲发生装置以及包括该装置的岩石钻机
US8720602B2 (en) 2007-12-21 2014-05-13 Atlas Copco Rock Drills Ab Pulse generating device and a rock drilling rig comprising such a device
US9316053B2 (en) 2009-11-11 2016-04-19 Flanders Electric Motor Service, Inc. Methods and systems for drilling boreholes
US9194183B2 (en) 2009-11-11 2015-11-24 Flanders Electric Motor Services, Inc. Methods and systems for drilling boreholes
US20120253519A1 (en) * 2009-11-11 2012-10-04 Flanders Electric, Ltd. Methods and systems for drilling boreholes
US8261856B1 (en) * 2009-11-11 2012-09-11 Flanders Electric, Ltd. Methods and systems for drilling boreholes
US8261855B2 (en) * 2009-11-11 2012-09-11 Flanders Electric, Ltd. Methods and systems for drilling boreholes
US8567523B2 (en) 2009-11-11 2013-10-29 Flanders Electric Motor Service, Inc. Methods and systems for drilling boreholes
US10494868B2 (en) 2009-11-11 2019-12-03 Flanders Electric Motor Service, Inc. Methods and systems for drilling boreholes
US20110108324A1 (en) * 2009-11-11 2011-05-12 Flanders Electric, Ltd. Methods and systems for drilling boreholes
US20120181234A1 (en) * 2009-11-24 2012-07-19 Anders Nydahl Filter and method for filtration of hydraulic oil in a return line to a hydraulic tank, and a drilling rig comprising the filter
US9776110B2 (en) * 2009-11-24 2017-10-03 Atlas Copco Rock Drills Ab Filter and method for filtration of hydraulic oil in a return line to a hydraulic tank, and a drilling rig comprising the filter
US8327950B2 (en) 2010-08-06 2012-12-11 Utilicor Technologies Inc. Excavation apparatus
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CN102937018A (zh) * 2012-10-31 2013-02-20 中联重科股份有限公司 全摩阻式钻杆的加压控制方法、设备和旋挖钻机
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US10167685B2 (en) * 2016-04-04 2019-01-01 Bauer Maschinen Gmbh Machine and method for earth-working
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DE1900210A1 (de) 1970-01-29
FR1598524A (de) 1970-07-06
GB1246290A (en) 1971-09-15

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