US3926265A - Drill steel for percussive drilling devices - Google Patents

Drill steel for percussive drilling devices Download PDF

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Publication number
US3926265A
US3926265A US477738A US47773874A US3926265A US 3926265 A US3926265 A US 3926265A US 477738 A US477738 A US 477738A US 47773874 A US47773874 A US 47773874A US 3926265 A US3926265 A US 3926265A
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United States
Prior art keywords
sheathing
core
set forth
coupling member
sleeve
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US477738A
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English (en)
Inventor
John V Bouyoucos
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JPMorgan Chase Bank NA
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Hydroacoustics Inc
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Priority to US477738A priority Critical patent/US3926265A/en
Priority to GB23836/75A priority patent/GB1494276A/en
Priority to SE7506473A priority patent/SE429572B/xx
Priority to JP50069215A priority patent/JPS518101A/ja
Priority to CA229,009A priority patent/CA1025432A/fr
Application granted granted Critical
Publication of US3926265A publication Critical patent/US3926265A/en
Priority to CA278,527A priority patent/CA1028685A/fr
Assigned to CHEMICAL BANK reassignment CHEMICAL BANK ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: HYDROACOUTICS, INC.
Assigned to HYDROACOUSTICS, INC., A CORP OF NY. reassignment HYDROACOUSTICS, INC., A CORP OF NY. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: CHEMICAL BANK
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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
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • E21B17/0426—Threaded with a threaded cylindrical portion, e.g. for percussion rods
    • 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
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • 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
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/10—Wear protectors; Centralising devices, e.g. stabilisers
    • E21B17/1042—Elastomer protector or centering means
    • 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
    • E21B21/00—Methods or apparatus for flushing boreholes, e.g. by use of exhaust air from motor

Definitions

  • the drill string has sections of drill steel in which a steel core, which acts as a transmission line for the force pulses generated by the hammer of the drill, is protected from scoring (as from rocks or adjacent metal objects) by sheathing which is attached to the core by resilient members to define a mass spring system in which the sheathing and pulse transmission member are dynamically isolated from each other at the repetition frequency of the force pulses.
  • the sections are connected by coupling joints of the drill string.
  • a breakout mechanism may be incorporated into each section to break out the joints, in which lugs extending from the core engage the sheathing during breakout to protect the resilient member during breakout.
  • the resilient members are constructed so as to be provided with sufficient longitudinal and torsional stiffness such that during normal drilling the lugs are isolated from the sheathing and do not produce galling or other damage.
  • the present invention relates to an improved drill steel for use with a percussive or impact type drilling device and to drill strings which may be made up of successive sections of such drill steel.
  • drill steel as used herein is meant rods or pipe which transmit forces for drilling or boring to an earth formation.
  • the drill string provided by this invention is suitable for all types of percussive drills, whether pneumatic or hydraulic, and also to those rigs in which the percussive forces are transmitted to a drill bit with rotation.
  • Scoring can be a significant source of failures of drill steels for transmitting percussive force pulses. It is presently believed that such failures are a function of the repetitive frequency of the stress cycles (compressive followed by tensile stress during each cycle) which cause cracks in the steel to grow and cause the steel to fail. More specifically the phenomenon of scoring involves the generation of transient increases in temperature which are localized in the steel. Cracks are formed in the surface of the steel where the temperature gradient develops. Surrounding these cracks, regions of trapped tensile stresses may result. When percussive forces are repetitively applied to the steel, the resulting stress cycles cause these cracks to grow and ultimately the steel fails. Thus the failure is a function of the repetitive percussive forces.
  • drill steel embodying the invention which may be included as a section of a drill string, includes a force pulse transmission member for conveying force pulses from, a percussive tool to a load.
  • a sheathing which may be in the form of a tough steel sleeve, is mounted on the transmission member by a resilient member in a manner such that the sheathing is isolated dynamically from the force pulse transmission member.
  • the sheathing may be arranged in segments separated from each other along the drill string.
  • the percussive tool provides repetitive impacts, as on a shank which is connected to the force pulse transmission member and which in turn applies the percussive forces to a drill bit, with or without rotation.
  • the sheathing is so sized (viz., is provided with mass) in relation to the compliance presented by the resilient members attached between the drill steel and the sheathing, that the sheathing and the resilient member exhibit a mass and compliance (their mass-spring characteristic) such as to place their resonant frequency below the force pulse repetition frequency.
  • the sheath is dynamically isolated from the force pulse transmission member so that the sheathing does not follow the cyclical movements of the force pulse trans mission member.
  • the cyclical stresses in the sheathing are substantially below the corresponding stresses in the pulse transmission member.
  • the force pulses are also decoupled from the wall of the hole; thus increasing the drilling forces at the bit.
  • the sheathing affords protection of the force pulse transmission member against abrasion and scoring. Since the axial motion of the sheath is substantially less than the motion of the force pulse transmission member, the sheath is subject to reduced abrasion effects.
  • a mechanism may be provided also, according to the invention, to allow torque for breakout purposes to be applied to the force pulse transmission member rather than to the exterior sheathing.
  • Lugs may project from the transmission member through openings in the sheathing to enable torque to be applied directly or via the sheathing to that member for breakout.
  • the rotation of the sheathing is limited, as by the lugs, thus protecting the resilient member from damage.
  • the resilient member has sufficient stiffness such that during normal drilling the displacement of the sheathing is limited and it does not contact the lugs.
  • the drill string may be comprised of a plurality of drill steel sections each having a sheathing separate from its force pulse transmission member.
  • the force pulse transmission members are connected directly to each other by being screwed together as through a coupling.
  • the sheathing for each section does not extend the full longitudinal length of that section and need not be connected to the sheathing of the next section or to the coupling, since the sheathing is dynamically isolated and does not interfere with the transmission of force pulses.
  • FIG. I is a longitudinal section view of a drill string embodying the invention.
  • FIG. 2 is a cross sectional view of the steel shown in FIG. 1, the section taken along the line 22 in FIG. 1;
  • FIG. 3 is a longitudinal sectional view of a drill string pipe, a coupling or joint and breakout mechanisms of different types
  • FIG. 4 is a cross sectional view of the steel shown in FIG. 3, the section being taken along the line 4-4 in FIG. 3;
  • FIG. 5 is a fragmentary sectional view of the end of the section of drill steel illustrating another embodiment of a breakout mechanism in accordance with the invention
  • FIG. 6 is a fragementary sectional view of the end of a section of drill steel illustrating still another embodiment of a breakout mechanism in accordance with the invention
  • FIG. 7 is a fragmentary sectional view of the end of a section of drill steel embodying the invention having the capability of using the chamber between the force pulse transmission member and the sheathing as a conduit for air or fluid through the drill steel;
  • FIG. 8 is a cross-sectional view of the steel shown in FIG. 7, the section being taken along the line 88 in FIG. 7 and;
  • FIG. 9 is a plan view of a drilling rig using a drill string embodying the invention.
  • FIG. 9 a drilling rig, 10, is shown, having a drill string 11 which is adapted to be connected to tool 12.
  • The'tool ' may have a mechanism for rotating the drill string 11.
  • This tool 12 may be a hydraulically driven hammer or a pneumatically driven hammer.
  • a drill bit 14 is secured to the end of the drill string 11 and is shown in operative position for drilling holes in an earth formation.
  • the hammer, drill string and bit may be carried by a tractor 16.
  • the tractor may also carry apump for hydraulic fluid or a compressor which provides compressed air.
  • the pump or compressor may, however, be carried on an associated vehicle.
  • the drill string 11 and the hammer 12 are mounted on a boom which extends from the tractor 16. The entire apparatus constitutes a drilling rig.
  • the drill string 11 is made up of successive sections 18 of drill steel which are assembled together by couplings or joints 20.
  • FIG. 1 One section 22 of the drill steel which is provided in accordance with the invention is illustrated in FIG. 1.
  • the drill steel section 22 has a core member 24 which provides .a force .pulse transmission line for the force pulses generated by the; hammer 12 (FIG. 9).
  • This core 24 is made out of hexagonal steeLCircular or pins are provided with threads 28 which are engaged by I the box section 30 of the joints 25.
  • Sheathing 32 in the form of a tubular member or sleeve of a diameter greater than the hexagonal core, 24 is disposed around the core, to form a chamber 34 defined between the core 24 and the sheathing 32.
  • the sheating 32 extends partially over the flared regions at the end of the core 34 and thus is out of contact with both the pin and the box section 26 and 30 of the coupling 25.
  • a resilient material is disposed in the chamber 34 and defines a body of resilient material by means of which the sheathing 32 is attached to the core 24.
  • the resilient material of the body 35 is preferably an elastomer which is poured or injected into the chamber 34 and allowed to cure in place.
  • the surfaces of the sheathing 32 and core 24 which contact the body 35 are desirably treated so as to provide for bonding between the elasto mer of the body 35, the sheathing and the core.
  • the core 24 has a central hole or passage 36 which extends also through the pin section 26. Air or other cleansing fluid may be passed through this passage 36 for hole cleaning purposes.
  • Air or other cleansing fluid may be passed through this passage 36 for hole cleaning purposes.
  • the box section 30 of the joint 25 is provided with longitudinal grooves 38.
  • a breakout wrench may be engaged with these grooves for the purpose of assembling and disassembling the sections 22 and 23 of the drill steel as drilling proceeds to greater depths into the formation or as the drill string 1 l is withdrawn from the hole (see FIG. 10).
  • the sheathing 22 is also provided with similar longitudinal slots 40 for breakout wrench engagement.
  • the core 24 may be hexagonal in shape and since the elastomer body 35 fills the chamber 34, and is bonded to the walls, the torque may be transferred to the core for breakout purposes without damaging the elastomer body 35.
  • the lower and upper ends of the sheathing may be swaged inwardly to conform to the hexagonal core shape, but to be spaced from the core 24, in a manner similar to that shown in FIG. 3.
  • the elastomer 35 is preferably absent in the swaged region.
  • forcepulses are repetitively transmitted along the transmission line provided by the core member 24. These force pulses cause cycles of compressive and tensile stresses in the core member. Without the sheathing 32, any scoring of the core member, as by rocks in the hole in the formation or by steel guiding members, is likely to giverise to cracks in the core member and result eventually in the failing thereof.
  • the sheathing 32 is dynamically iso lated from the core member. Such isolation is provided by the mass spring characteristics of the system made up of the sheathing and the resilient body 35.
  • the mass (weight) of the sheathing and the compliance of the resilient body 35 defines a mass spring system having a resonant frequency which is different from and preferably below the repetition frequency of the force pulses which are transmitted along the core member 24. Accordingly, the dynamics of the system provides for a longitudinal dynamic motion of the sheathing which is a small fraction of the dynamic motion of the core in response to the force pulses which are transmitted therethrough. Since the ends of the sheathing are spaced from the core 24 and the coupling box section 30, the sheathing will not impact the core or box section thus preventing end damage to the sheathing.
  • the sheathing is subject to bending stresses during rotation as, for example, in a crooked hole, at normal rotation frequencies the number of rotational cycles per unit of time is several orders of magnitude lower than the number of percussive force pulse induced cycles per unit of time. For example, one million stress cycles at the rotation frequency may take between 100 and 200 operating hours whereas one million stress cycles in the longitudinal direction at frequencies of about 6000 force pulses per minute may take only 2 to 3 hours. Fatigue due to repetitive stress cycles is therefore more likely to occur from the longitudinal cycling rather than the rotational cycling. Since the sheath is protected from the longitudinal induced stresses, its life is significantly enhanced.
  • Appropriate design parameters for the sheathing 32 and the resilient body 35 for a 3 inch O.D. member, feet long, may be that the mass of the sheathing 32 could be in the range of 80 pounds while the compliance of the body 35 should be in the range of 17,000 pounds per inch. These parameters will provide a resonant frequency of about Hz which is below the repetition frequency of 75 Hz whhich is generated by certain high performance percussive hammers.
  • the sheathing 32 and elastomer body 35 provide for sound isolation. Noise generated in the course of force pulse transmission or from the bit region is suppressed by the sound isolation structure provided by the sheathing and elastomer body.
  • the section modulus of the sheathing is preferably sufficiently high to reduce bending of the drill steel and thus is effective in supporting the core in the presence of high pulldown forces which may produce bending. This feature aids in the drilling of straight holes.
  • FIG. 3 there is shown a section 40 of sheathed drill steel in accordance with another embodiment of the invention.
  • FIG. 3 also depicts alternative breakout mechanisms 42 and 44 at the opposite end of the drill steel section 40.
  • a coupling or joint 46 which is sheathed to protect the coupling from scoring failures is also illustrated.
  • a core 48 which may be a cylindrical rod made of steel provides a force pulse transmission line or member.
  • a threaded pin section 50 provided at the end of the core 48 (only one end being shown in detail to simplify the illustration) is assembled to the pin section 52 of a successive drill steel section 54 by the coupling 46.
  • a central passage 56 is provided through the core 48 for air or other cleansing fluid. (See FIG. 4).
  • a sheathing 58 in the form of a generally cylindrical tube of steel is disposed around and radially spaced from the core 48.
  • the opposite end of the sheathing 58 may be swaged down towards the core 48 in the course of assembly. Nevertheless, clearance 60 (see FIG. 4) is provided between the core and the sheathing, even at the end of the sheathing so as to facilitate relative movement between the core 48 and the sheathing 58.
  • a plurality of annuluses 62 of resilient material which is preferably an elastomer are disposed in the chamber 64 between the outer periphery of the core 48 and the inner periphery of the sheathing 58.
  • annuluses may be formed by injecting elastomeric material into successive regions of the chamber 64 which are longitudinally spaced from each other and allowing the material to cure in place.
  • the annuluses 62 may be bonded to the inner periphery of the sheathing 58 prior to the insertion of the core 48 into the sheathing.
  • the annuluses 62 may be toroidal or hollow cylindrical bodies of elastomeric material which are preformed. Each annulus may be compressed much in the same manner as a piston ring and inserted in place in the chamber 64.
  • the upper end 42 of the sheathing 58 is formed with a plurality, say four, longitudinal slots through which four lugs 72 individually extend when the ends of the sheathing are swaged down toward the core 48.
  • the slots are sufficiently wide so as to provide clearance on all sides of the lugs such that the lugs do not engage the sheathing during normal drilling operations.
  • the opposite or lower end of the core 48 in FIG. 3 shows an alternate configuration.
  • the core 48 has four lugs 74 which extend through rectangular holes 76 in the sheathing 58 (see also FIG. 4). Sufficient clearance is provided between the lugs and the walls of the hole 76, such that the lugs remain out of contact with the sheathing during normal drilling operations.
  • the couplings 46 at the opposite ends of the section 40 cooperate with the arrangement of lugs and slots in providing the breakout mechanisms 42 and 44.
  • the couplings 46 are similar. In addition to the pin sections 50 and 52, the couplings 46 have a box section 78. A cylindrical sleeve 80 of inner diameter greater than the outer diameter of the box section 78 is shown separated from the box section 78 by a plurality of annuluses 82 in the form of rings of resilient material. The material may be an elastomer of the same type used in providing the annuluses 62 and may be assembled in a cylindrical chamber 84 between the sleeve 80 and the box section 78 in the same manner described above in connection with the annuluses 62.
  • the central section of the chamber 84 may be filled with a body of resilient, say elastomeric material, as was discussed above in connection with the elastomer body 35 shown in FIG. 1.
  • the sleeve 80 has a plurality of holes, say four holes 86, ninety degrees apart at the upper end of the sleeve 80 and a similar arrangement of four holes 88 near the bottom of the sleeve, screws which are screwed into the box section 78 extend into these holes 86 and 88; there being sufficient clearance between the heads of the screws 90 and the walls of the holes. These screws 90 operate in the same manner as the lugs 72 and 74.
  • a plurality of longitudinal grooves 92 for engagement with a breakout wrench are provided in the outer surface of the sleeve 80.
  • the arrangement of these grooves may be similar to the arrangement of the grooves 38 (FIG. 1).
  • Similar arrangements of grooves 94 and 96 are also provided in the sheathing 58.
  • the tough steel sheathing 58 and the annuluses 62 of resilient material provide for dynamic isolation of the sheathing 58 from the core or force pulse transmission line 48.
  • the longitudinal dynamic motion of the sheathing 58 is a small fraction of the dynamic motion of the core 48 in transmitting force pulses therethrough at the repetition frequency of these force pulses.
  • the resonant frequency of the mass spring system defined by the mass of the sheathing 58 and the compliance of the annuluses 62 is different from the force pulse repetition frequency and preferably well below the force pulse repetition frequency.
  • the clearance in a longitudinal direction between the lugs 74 and the slots, or in case the breakout arrangement 42 is used between the lugs 72 and the slots 70, is sufficient such that the lugs do not engage or rub on the walls of the slots. Galling or other damage to the core 48 is therefore prevented.
  • the torsional stiffness of the annuluses 62 is sufficiently high such that rotational torque transferred to the sheathing is not large enough to cause contact of the slots 70 or 76 with the lugs, even though the drill steel is rotated.
  • the sleeve 80 and its rings 82 also defines a system which dynamically isolates the sleeve from the box section 78 of the coupling 46. Sufficient clearance is also provided between the walls of the holes 86 and the projecting heads of the screws 90 such that engagement therebetween is minimized during normal drilling operations.
  • the lugs 72 or 74 and the screws 90 provide protective stops which prevents excessive force from being transferred to the annuluses 62 or the rings 82 which might cause damage thereto.
  • breakout torque is transferred from the wrench directly to the box section 78 of the coupling by way of the screws 90 and through the sheathing 58 through the lugs 72 or 74 to the core 48.
  • the considerable torque which is needed in breakout can be applied without damaging the resilient material of the annuluses 62 or the rings 82 which afford isolation of the sheathing and sleeve during normal drilling operations.
  • the lugs preferably do not extend beyond the sheathing 58 and are disposed well within the slot 76. The possibility of the lugs engaging any obstacle in the hole is therefore reduced.
  • the annuluses 62 may be an elastomer material such as natural rubber, each having a longitudinal shear stiffness of 3400 pounds per inch.
  • the sheathing is of tough steel having a mass of 80 pounds for a sheathing length of 20 feet and diameter of 3 inches. With the use of five annuluses, each one inch in length the resonant frequency of the sheathing is about 40 Hz.
  • the number of annuluses 62, the compliance of the material used therefor, and the mass of the sheathing will vary in accordance with the pulse repetition frequency and the length of the drill steel section 40 and may be selected to provide the requisite resonant frequency below the frequency of repetition of the force pulses for dynamically isolating the sheathing 58 from the core 48. Similar considerations may be used in selecting the sleeve 92 and rings 82 of the joint 46.
  • the sheathed drill steel shown in FIGS. 3 and 4 also has the features discussed in connection with the steel shown in FIG. 1 of drilling straighter holes by virtue of the restraint on bending of the core 48 imposed by the sheathing 58.
  • the sleeve 80 around the joint 46 as well as the sheathing 58 together with their rings 82 and annuluses 62 also provide acoustic isolation which affords muffling of noises generated in percussive drilling operations.
  • FIG. 5 illustrates another sheathed drill steel in accordance with the invention having a force pulse transmitting core and a tubular sheathing 102 assembled on the core 100 by means of annuluses 104 of resilient material, as was discussed in connection with FIG. 3.
  • a threaded pin 106 is shown for coupling purposes.
  • the breakout mechanism may include a joint similar to the joint 46 and pins or rods 108 which are assembled as by being force fit into holes in the core 100.
  • the length of the pin is greater than the diameter of the core 100 but less than the outer diameter of the sheathing 102.
  • the pin extends into holes 110 which are diametrically opposite each other in the sheathing 100.
  • FIG. 6 there is shown a force pulse transmission core member 114 which is formed at its end with flats 116, four or six of which may be provided.
  • the flats are arranged much like a nut and may be engaged by a wrench for breakout purposes.
  • a sheathing 118 around the core 114 is separated from the core by annuluses 120 for dynamic isolation purposes as was discussed in connection with FIGS. 1 and 3.
  • Another annulus 122 is disposed between the end section of the core which is formed with the flat 1 l6 and the lower end of the sheathing 118. This annulus 122 extends outwardly so as to provide a bumper for protecting the lower end of the sheathing.
  • the section of the core 114 may also be formed with serrations for breakout wrench engagement purposes.
  • the sheathed steel embodiment as shown in FIGS. 5 and 6 may also be completely filled with resilient material or the annuluses 120, as shown, may be used.
  • the section 124 is a sheathed steel section having a force pulse transmission core 128 separated from a tubular sheathing 130 by several longitudinally spaced annuluses 132 of resilient material.
  • the bottom one, 134 of these annuluses has a lip which extends between the box 136 of the coupling 126.
  • the box 126 engages the threaded pin 138 at the end of the core 128 and assembles it to the pin 140 of the next core section.
  • the annulus 134 and the upper end of the box 126 have aligned axial holes 140, several of which are spaced from each other along the circumference of a circular pin (see FIG. 8).
  • the holes in the upper end of the box 126 may be relieved or a groove between these holes may be used to provide tolerance in alignment. Similar arrangements of holes 142 are provided in the annuluses 132. Cleansing fluid such as compressed air may flow through these holes and to the chambers 144 and 146 in the sheathed steel section 124 and the joint 126. This cleansing fluid may be used for purposes of hole cleaning and removal of chips at the bottom of the hole.
  • the arrangement of resilient annuluses 132 and 134 and sheathing 130 provide for dynamic isolation of the core as was explained above in connection with FIGS. 1 and 3.
  • Drill steel for use with percussive tools which generate force pulses at a certain repetition frequency comprising:
  • said means comprising a resilient member of elastic material located in said chamber and connecting said sheathing and said transmission member, said sheathing having a certain mass and said resilient member having a certain compliance related to the mass of said sheathing together to constitute a mass spring system which is resonant at said'resonant frequency.
  • said resilient member includes a plurality of annuluses of said material, spaced from each other in a longitudinal direction, along said core.
  • annuluses each have a plurality of openings extending axially therebetween and providing channels for the flow of cleansing fluid through said chamber.
  • the invention as set forth in claim 2 further comprising a joint for interconnecting successive sections of said drill steel into a drill string, said joint including a coupling member for engaging the ends of said successive sections, a sleeve around said coupling member, and a resilient member disposed between said sleeve and coupling member, holding said sleeve and coupling member in assembled relationship and dynamically isolating said sleeve from said coupling member at said force pulse repetition frequency.
  • said resilient member which is disposed between said coupling member and its sleeve is comprised of a plurality of rings of elastomeric material spaced from eachother in a direction longitudinally of said coupling member.
  • said sleeve around said coupling member has first and second pluralities of holes, said first plurality of holes being spaced around said sleeve near one end thereof, said second plurality of holes being spaced around said coupling member sleeve near the end thereof opposite to said one end, and lug means extending laterally from said coupling member sleeve into said holes, said lug means being smaller than the holes through which they extend so that clearance is provided between said coupling member sleeve and said lug means.
  • a drill steel for use with a percussive tool comprising:
  • annular member of elastomeric material disposed between said sheathing and said core member, said annular member holding said sheathing spaced from said core member and in assembled relationship therewith, and
  • breakout means for separating said steel from a coupling member, said breakout means including members projecting from said core member and spaced from said sheathing.
  • said breakout means includes a plurality of said projecting members, said sheathing having openings through which said projecting members extend, said openings being larger than said projecting members to provide clearance therebetween.
  • the invention as set forth in claim 19 further comprising a joint having a coupling member for securing the cores of successive sections of said drill steel to form a drill string, said annular member comprises a plurality of annuluses longitudinally spaced from each other along said core member and wherein one of said plurality of annuluses is disposed at the end of said sheathing, said one annulus having a lip extending radially outward to form a bumper between said coupling member and the end of said sheathing.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
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US477738A 1974-06-10 1974-06-10 Drill steel for percussive drilling devices Expired - Lifetime US3926265A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US477738A US3926265A (en) 1974-06-10 1974-06-10 Drill steel for percussive drilling devices
GB23836/75A GB1494276A (en) 1974-06-10 1975-06-02 Drill steel for use with percussive tools
SE7506473A SE429572B (sv) 1974-06-10 1975-06-06 Borrstal for anvendning vid slagverktyg
CA229,009A CA1025432A (fr) 1974-06-10 1975-06-10 Acier a forets pour l'usage avec un outil a percussion
JP50069215A JPS518101A (en) 1974-06-10 1975-06-10 Shogekikogutoheiyosurudoriruko
CA278,527A CA1028685A (fr) 1974-06-10 1977-05-16 Acier a forets utilise pour outils a percussion

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US477738A US3926265A (en) 1974-06-10 1974-06-10 Drill steel for percussive drilling devices

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US3926265A true US3926265A (en) 1975-12-16

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US477738A Expired - Lifetime US3926265A (en) 1974-06-10 1974-06-10 Drill steel for percussive drilling devices

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US (1) US3926265A (fr)
JP (1) JPS518101A (fr)
CA (1) CA1025432A (fr)
GB (1) GB1494276A (fr)
SE (1) SE429572B (fr)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4146060A (en) * 1977-07-25 1979-03-27 Smith International, Inc. Drill pipe wear belt assembly
FR2442110A1 (fr) * 1978-11-25 1980-06-20 Wacker Werke Kg Dispositif pour la reduction du bruit cause par les marteaux perforateurs-piqueurs
US4215763A (en) * 1978-08-21 1980-08-05 General Electric Company Resonant sound attenuator for transformers
DE2920139A1 (de) * 1979-05-18 1980-11-20 Ruhrkohle Ag Schlagbohrstange
US4348672A (en) * 1981-03-04 1982-09-07 Tele-Drill, Inc. Insulated drill collar gap sub assembly for a toroidal coupled telemetry system
EP0066891A2 (fr) * 1981-06-10 1982-12-15 Ruhrkohle Aktiengesellschaft Tige de forage à amortissement de bruit
FR2553697A1 (fr) * 1983-10-24 1985-04-26 Charbonnages De France Dispositif d'insonorisation d'un fleuret de foration
US4560012A (en) * 1984-06-20 1985-12-24 Mcneely Jr Branch M Drill collar structure for use in deviated well bore drilling
US4823125A (en) * 1987-06-30 1989-04-18 Develco, Inc. Method and apparatus for stabilizing a communication sensor in a borehole
US5064002A (en) * 1987-04-23 1991-11-12 Patterson William N Concentric drill rod assemblies for percussion rock drills
US5425428A (en) * 1993-07-22 1995-06-20 Fugro-Mcclelland Marine Geosciences, Inc. Slimhole coring system
US5713423A (en) * 1992-07-24 1998-02-03 The Charles Machine Works, Inc. Drill pipe
US6736224B2 (en) * 2001-12-06 2004-05-18 Corion Diamond Products Ltd. Drilling system and method suitable for coring and other purposes
US20050167098A1 (en) * 2004-01-29 2005-08-04 Schlumberger Technology Corporation [wellbore communication system]
US20060000665A1 (en) * 2004-06-30 2006-01-05 Shah Vimal V Low frequency acoustic attenuator for use in downhole applications
US20070033811A1 (en) * 2002-01-18 2007-02-15 Max Co., Ltd. Concrete drill
US20110011644A1 (en) * 2006-09-20 2011-01-20 Schlumberger Technology Corporation Methods and apparatus for attenuating drillstring vibrations
WO2011025431A1 (fr) 2009-08-28 2011-03-03 Atlas Copco Secoroc Ab Composant de train de tiges de forage pour contrôle du bruit lors d'un forage à percussion
US20120037427A1 (en) * 2010-08-10 2012-02-16 QCS Technologies Inc. Drilling System for Enhanced Coring and Method
US8689930B2 (en) * 2012-03-29 2014-04-08 Westerngeco L.L.C. Seismic vibrator having airwave suppression
CN104499958A (zh) * 2014-10-16 2015-04-08 中国石油大学(华东) 多点激励钻柱减摩阻方法及装置
US10077615B2 (en) 2015-07-31 2018-09-18 ASDR Canada Inc. Sound absorber for a drilling apparatus
US10260287B2 (en) * 2015-02-24 2019-04-16 The Charles Machine Works, Inc. Dual-member pipe assembly
US10920570B2 (en) * 2019-07-12 2021-02-16 Halliburton Energy Services, Inc. Measurement of torque with shear stress sensors
US10920571B2 (en) * 2019-07-12 2021-02-16 Halliburton Energy Services, Inc. Measurement of torque with shear stress sensors

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JPS53113725A (en) * 1977-03-17 1978-10-04 Nippon Steel Corp Surface finishing method for one-side molten zinc plated steel plate
CN103475972B (zh) * 2013-09-24 2017-01-25 小米科技有限责任公司 一种用于耳机插头的连接部件、耳机插孔及终端
CN106050154B (zh) * 2016-06-03 2018-01-02 西南石油大学 基于柔性杆的防滞动工具
CN109736749A (zh) * 2019-01-15 2019-05-10 洛阳风动工具有限公司 一种套筒式防石块喷溅手持式凿岩机

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US3274798A (en) * 1964-06-17 1966-09-27 Exxon Production Research Co Vibration isolator
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Cited By (42)

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US4146060A (en) * 1977-07-25 1979-03-27 Smith International, Inc. Drill pipe wear belt assembly
US4215763A (en) * 1978-08-21 1980-08-05 General Electric Company Resonant sound attenuator for transformers
FR2442110A1 (fr) * 1978-11-25 1980-06-20 Wacker Werke Kg Dispositif pour la reduction du bruit cause par les marteaux perforateurs-piqueurs
DE2920139A1 (de) * 1979-05-18 1980-11-20 Ruhrkohle Ag Schlagbohrstange
US4348672A (en) * 1981-03-04 1982-09-07 Tele-Drill, Inc. Insulated drill collar gap sub assembly for a toroidal coupled telemetry system
EP0066891A2 (fr) * 1981-06-10 1982-12-15 Ruhrkohle Aktiengesellschaft Tige de forage à amortissement de bruit
EP0066891A3 (en) * 1981-06-10 1984-01-18 Ruhrkohle Aktiengesellschaft Noise damping means for drilling rods
EP0141728A2 (fr) * 1983-10-24 1985-05-15 CHARBONNAGES DE FRANCE, Etablissement public dit: Dispositif d'insonorisation d'un fleuret de foration
FR2553697A1 (fr) * 1983-10-24 1985-04-26 Charbonnages De France Dispositif d'insonorisation d'un fleuret de foration
EP0141728A3 (en) * 1983-10-24 1985-06-19 Etablissement Public Dit: Charbonnages De France Device for sound attenuation of drills
US4591009A (en) * 1983-10-24 1986-05-27 Charbonnages De France Drill soundproofing device
US4560012A (en) * 1984-06-20 1985-12-24 Mcneely Jr Branch M Drill collar structure for use in deviated well bore drilling
US5064002A (en) * 1987-04-23 1991-11-12 Patterson William N Concentric drill rod assemblies for percussion rock drills
US4823125A (en) * 1987-06-30 1989-04-18 Develco, Inc. Method and apparatus for stabilizing a communication sensor in a borehole
US5713423A (en) * 1992-07-24 1998-02-03 The Charles Machine Works, Inc. Drill pipe
US5425428A (en) * 1993-07-22 1995-06-20 Fugro-Mcclelland Marine Geosciences, Inc. Slimhole coring system
US6736224B2 (en) * 2001-12-06 2004-05-18 Corion Diamond Products Ltd. Drilling system and method suitable for coring and other purposes
US7308949B2 (en) * 2002-01-18 2007-12-18 Max Co., Ltd. Concrete drill
US20070033811A1 (en) * 2002-01-18 2007-02-15 Max Co., Ltd. Concrete drill
US20060220650A1 (en) * 2004-01-29 2006-10-05 John Lovell Wellbore communication system
US20050167098A1 (en) * 2004-01-29 2005-08-04 Schlumberger Technology Corporation [wellbore communication system]
US7880640B2 (en) 2004-01-29 2011-02-01 Schlumberger Technology Corporation Wellbore communication system
US7080699B2 (en) 2004-01-29 2006-07-25 Schlumberger Technology Corporation Wellbore communication system
US20060000665A1 (en) * 2004-06-30 2006-01-05 Shah Vimal V Low frequency acoustic attenuator for use in downhole applications
US7210555B2 (en) * 2004-06-30 2007-05-01 Halliburton Energy Services, Inc. Low frequency acoustic attenuator for use in downhole applications
US7984771B2 (en) * 2006-09-20 2011-07-26 Schlumberger Technology Corporation Methods and apparatus for attenuating drillstring vibrations
US20110011644A1 (en) * 2006-09-20 2011-01-20 Schlumberger Technology Corporation Methods and apparatus for attenuating drillstring vibrations
WO2011025431A1 (fr) 2009-08-28 2011-03-03 Atlas Copco Secoroc Ab Composant de train de tiges de forage pour contrôle du bruit lors d'un forage à percussion
US9109397B2 (en) 2009-08-28 2015-08-18 Atlas Copco Secoroc Ab Drill string component for noise control during percussion drilling
EA023318B1 (ru) * 2009-08-28 2016-05-31 Атлас Копко Секорок Аб Устройство для борьбы с шумом во время ударного бурения
AP3254A (en) * 2009-08-28 2015-05-31 Atlas Copco Secoroc Ab Drill string component for noise control during percussion drilling
US20120037427A1 (en) * 2010-08-10 2012-02-16 QCS Technologies Inc. Drilling System for Enhanced Coring and Method
US8579049B2 (en) * 2010-08-10 2013-11-12 Corpro Technologies Canada Ltd. Drilling system for enhanced coring and method
US8689930B2 (en) * 2012-03-29 2014-04-08 Westerngeco L.L.C. Seismic vibrator having airwave suppression
CN104499958A (zh) * 2014-10-16 2015-04-08 中国石油大学(华东) 多点激励钻柱减摩阻方法及装置
US10260287B2 (en) * 2015-02-24 2019-04-16 The Charles Machine Works, Inc. Dual-member pipe assembly
US11002076B2 (en) 2015-02-24 2021-05-11 The Charles Machine Works, Inc. Dual-member pipe assembly
US11828176B2 (en) 2015-02-24 2023-11-28 The Charles Machine Works, Inc. Dual-member pipe assembly
US10077615B2 (en) 2015-07-31 2018-09-18 ASDR Canada Inc. Sound absorber for a drilling apparatus
US10920570B2 (en) * 2019-07-12 2021-02-16 Halliburton Energy Services, Inc. Measurement of torque with shear stress sensors
US10920571B2 (en) * 2019-07-12 2021-02-16 Halliburton Energy Services, Inc. Measurement of torque with shear stress sensors
US11149536B2 (en) 2019-07-12 2021-10-19 Halliburton Energy Services, Inc. Measurement of torque with shear stress sensors

Also Published As

Publication number Publication date
SE7506473L (sv) 1975-12-11
CA1025432A (fr) 1978-01-31
GB1494276A (en) 1977-12-07
JPS5527953B2 (fr) 1980-07-24
SE429572B (sv) 1983-09-12
JPS518101A (en) 1976-01-22

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