EP0202013B1 - Führungs- und Steuerungssystem für Schlagbohrwerkzeuge - Google Patents

Führungs- und Steuerungssystem für Schlagbohrwerkzeuge Download PDF

Info

Publication number
EP0202013B1
EP0202013B1 EP86302534A EP86302534A EP0202013B1 EP 0202013 B1 EP0202013 B1 EP 0202013B1 EP 86302534 A EP86302534 A EP 86302534A EP 86302534 A EP86302534 A EP 86302534A EP 0202013 B1 EP0202013 B1 EP 0202013B1
Authority
EP
European Patent Office
Prior art keywords
housing
sleeve
tool according
fin
percussion tool
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP86302534A
Other languages
English (en)
French (fr)
Other versions
EP0202013A3 (en
EP0202013A2 (de
Inventor
Gerard T. Pittard
William C. Maurer
Joseph O. Enk
Gregory C. Givler
William J. Mcdonald
Jack E. Bridges
John H. Cohen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gas Technology Institute
Original Assignee
Gas Research Institute
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US06/720,582 external-priority patent/US4632191A/en
Priority claimed from US06/722,807 external-priority patent/US4646277A/en
Priority claimed from US06/723,792 external-priority patent/US4621698A/en
Priority to EP90122531A priority Critical patent/EP0428181B1/de
Priority to EP90122530A priority patent/EP0428180B1/de
Application filed by Gas Research Institute filed Critical Gas Research Institute
Priority to AT86302534T priority patent/ATE86355T1/de
Publication of EP0202013A2 publication Critical patent/EP0202013A2/de
Publication of EP0202013A3 publication Critical patent/EP0202013A3/en
Publication of EP0202013B1 publication Critical patent/EP0202013B1/de
Application granted granted Critical
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/26—Drilling without earth removal, e.g. with self-propelled burrowing devices
    • E21B7/267—Drilling devices with senders, e.g. radio-transmitters for position of drilling tool
    • 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
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers
    • E21B4/145—Fluid operated hammers of the self propelled-type, e.g. with a reverse mode to retract the device from the hole
    • 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
    • E21B47/00—Survey of boreholes or wells
    • E21B47/02—Determining slope or direction
    • E21B47/022—Determining slope or direction of the borehole, e.g. using geomagnetism
    • E21B47/0228—Determining slope or direction of the borehole, e.g. using geomagnetism using electromagnetic energy or detectors therefor
    • 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
    • E21B47/00—Survey of boreholes or wells
    • E21B47/12—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling
    • E21B47/13—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling by electromagnetic energy, e.g. radio frequency
    • 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
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/04—Directional drilling
    • E21B7/06—Deflecting the direction of boreholes
    • E21B7/068—Deflecting the direction of boreholes drilled by a down-hole drilling motor

Definitions

  • This invention relates generally to percussion boring tools, and more particularly to percussion boring tools for drilling holes in the soil.
  • Utility Companies often find it necessary to install or replace piping beneath different types of surfaces such as streets, driveways, railroad tracks, etc. To reduce costs and public inconvenience by eliminating unnecessary excavation and restoration, utilities sometimes use underground boring tools to install the new or replacement pipes.
  • Existing boring tools are suitable for boring short distances (up to 60 ft.), but are not sufficiently advanced to provide directional control for longer distances. This lack of control, coupled with the inability of these tools to detect and steer around obstacles, has limited their use to about 20% of all excavations, with the majority of the remaining excavations being performed by open-cut trenching methods.
  • Conventional pneumatic and hydraulic percussion moles are designed to pierce and compact compressible soils for the installation of underground utilities without the necessity of digging large launching and retrieval pits, open cutting of pavement or reclamation of large areas of land.
  • An internal striker or hammer reciprocates under the action of compressed air or hydraulic fluid to deliver high energy blows to the inner face of the body. These blows propel the tool through the soil to form an earthen casing within the soil that remains open to allow laying of cable or conduit. From early 1970 to 1972, Bell Laboratories, in Chester, New Jersey, conducted research trying to develop a method of steering and tracking moles.
  • a 10.2 cm Schramm Pneumagopher was fitted with two steering fins and three mutually orthogonal coils which were used in conjunction with a surface antenna to track the position of the tool.
  • One of these fins was fixed and inclined from the tool's longitudinal axis while the other fin was rotatable.
  • Two boring modes could be obtained with this system by changing the position of the rotatable fin relative to the fixed fin. These were (1) a roll mode in which the mole was caused to rotate about its longitudinal center line as it advanced into the soil and (2) a steering mode in which the mole was directed to bore in a curved path.
  • the roll mode was used for both straight boring and as a means for selectively positioning the angular orientation of the fins for subsequent changes in the bore path.
  • Rotation of the mole was induced by bringing the rotatable fin into an anti-parallel alignment with the fixed fin. This positioning results in the generation of a force couple which initiates and maintains rotation.
  • the steering mode was actuated by locating the rotatable fin parallel to the fixed fin. As the mole penetrates the soil, the outer surfaces of the oncoming fins are brought into contact with the soil and a "slipping wedge” mechanism created. This motion caused the mole to veer in the same direction as the fins point when viewed from the back of the tool.
  • Coyne et al US Patent 3, 525, 405 discloses a steering system which uses a beveled planar anvil that can be continuously rotated or rigidly locked into a given steering orientation through a clutch assembly. It is to be used particularly for burrowing out relatively shallow ground depths.
  • the planar beveled front face of the mole provides free axial rotation with respect to the mole body. Spiral flutes are mounted on the nose of the mole causing the nose to rotate.
  • the mole is steered, by locking, or unlocking the rotating part of the tool, with respect to the beveled face part of the tool, using a remotely controlled clutch which is located within the tool.
  • This device achieves an improved steering tool by reducing the size of the forces needed to steer a mole; by reducing turning radius of the mole; by simplifying the process of mole planting; and preventing the mole edging upwards towards the soil surface during use.
  • Chepurnoi et al U.S. Patent 3, 952, 813 discloses an off-axis or eccentric hammer steering system in which the striking position of the hammer is controlled by a transmission and motor assembly.
  • Gagen et al, U.S. Patent 3, 794, 128 discloses a steering system employing one fixed and one rotatable tail fin, each fin being diametrically opposite to the other.
  • the two fins are cited at the rear of the mole and the rear portion of the mole is tapered.
  • the rotatable fin is controlled by a mechanism located inside the mole.
  • the steering system can have either curvilinear motion or move in a forward direction, the direction of movement being dependent on the relative positions of the fins.
  • the device achieves an improved steering system by using a mole which is smaller and shorter than those already known, whilst providing an equivalent turning radius.
  • the further advantages of the system are the provision of extra internal space, the reapportion being tapered allows for smaller fins and/or a smaller turning radius for a given length of mole.
  • Typical well surveying equipment utilizes magnetometers, inclinometers and inertial guidance systems which are complex and expensive.
  • the wells drilled are substantially vertical.
  • utilities e.g., electric or telephone lines, TV cable, gas distribution piping, or the like
  • Another object of this invention is to provide a steering system which will enable a horizontal boring tool to travel over great distances and reliably hit a small target.
  • Another object of this invention is to provide boring tool which will produce a guided borehole to avoid obstacles and to correct for deviations from the planned boring path.
  • Another object of this invention is to provide a boring tool immune to adverse environmental conditions and which allows the boring operation to be conducted by typical field service crews.
  • a still further object of this invention is to provide a guided horizontal boring tool which requires a minimal amount of excavation for launching and retrieval and thereby reducing the disturbance of trees, shrubs or environmentally sensitive ecosystems.
  • a guided horizontal boring tool constructed in accordance with the present invention will benefit utilities and rate payers by significantly reducing installation and maintenance costs of underground utilities by reducing the use of expensive, open-cut trenching methods.
  • a controllable percussion tool for drilling holes in the soil using an asymmetric boring force characterised in that the tool comprises a cylindrical housing with a tapered front end, a first means on said front end for applying a boring force to the soil, a second means in said housing for applying a percussive force to said boring force applying means, said first and second means being cooperable to apply the asymmetric boring force, at least one guide fin comprising a fin assembly positioned on the exterior of said housing at the rear end thereof and having a first position permitting non-rotative movement of said housing through the soil and a second position causing said housing to rotate about its longitudinal axis on movement through the soil, and means for moving the fin assembly between the said first and second positions; whereby said housing has a curved path through the soil when prevented from rotating and a substantially straight path when caused to rotate.
  • Fig. 1 is a schematic view and partial vertical section through the earth showing a guided horizontal boring tool illustrating the present invention used with a magnetic attitude sensing system.
  • Figs. 2 and 3 are schematic views, in elevation, of a fixed/lockable tail fin steering system.
  • Figs. 4 through 7 are schematic views, in elevation, of a movable tail fin system.
  • Fig. 8 is a schematic view, in elevation, of a movable fin system in combination with an eccentric hammer.
  • Figs. 9A, 9B, and 9C are segments in longitudinal cross section of a typical boring tool having a slanted nose member and fixed/lockable fin arrangement in the unlocked position.
  • Fig. 10 is a vertical cross sectional view of the slanted nose member taken along the line 10 - 10 of Fig. 9A.
  • Fig. 11 is a longitudinal cross section of the fixed/lockable tail fin assembly of Fig. 9C in the locked position.
  • Fig. 12 is a view, in side elevation, of the fixed/lockable tail fin assembly of Fig. 9C in the locked position.
  • Fig. 13 is a partial elevation of the drive teeth assembly of the fixed/lockable tail fin assembly.
  • Figs. 14 and 15 are schematic views in longitudinal cross section showing the operation of a typical percussion boring tool according to this invention.
  • Figs. 16 through 19 are partial longitudinal cross sections of a variations of the fixed/lockable fin assembly in the locked or unlocked positions.
  • Figs. 20 and 21 are longitudinal cross sections of an alternate embodiment of the fixed/lockable fin assembly using a drive pin arrangement.
  • Fig. 22 is a partial elevation of the dowel pin and drive teeth of the fixed/lockable tail fin assembly.
  • Figs. 23, 24, 27, 28, 33 and 34 are partial longitudinal cross sections of variations of the fixed/lockable fin assembly using a dowel pin and drive teeth drive, while Figs. 25 and 26 illustrate a splined connection, and Figs 29 - 32 show a spline and drive teeth connection.
  • Fig. 35 is a longitudinal cross section of a movable tail fin assembly.
  • Fig. 36 is a vertical cross section of the movable tail fin assembly of Fig. 35 taken along line 36 - 36 of Fig. 35.
  • Figs. 37 and 38 are partial longitudinal cross sections of the movable tail fin assembly of Fig. 35 showing the operation.
  • Fig. 39 is an end view of the movable tail fin assembly showing the fins in the non-parallel position.
  • Figs. 40 and 41 are longitudinal cross sections of a portion of a boring tool including an eccentric hammer arrangement.
  • a preferred guided horizontal boring tool 10 The boring tool 10 may be used with various sensing systems, and a magnetic attitude sensing system is depicted generally as one example.
  • the usual procedure to using percussion moles is to first locate and prepare the launching and retrieval pits.
  • the launching pit should be dug slightly deeper than the planned boring depth and large enough to provide sufficient movement for the operator.
  • the mole or boring tool 10 is connected to a pneumatic or hydraulic source 11, is then started in the soil, stopped and properly aligned, preferably with a sighting frame and level.
  • the tool is then restarted and boring continued until the tool exits into the retrieval pit (not shown).
  • the boring tool 10 may have a pair of coils 12 at the back end, one of which produces a magnetic field parallel to the axis of the tool, and the other produces a magnetic field transverse to the axis of the tool. These coils are intermittently excited by a low frequency generator 13. To sense the attitude of the tool, two coils 14 and 15 are positioned in the pit P, the axes of which are perpendicular to the desired path of the tool. The line perpendicular to the axes of these coils at the coil intersection determines the boresite axis.
  • Outputs of these coils can be processed to develop the angle of the tool in both the horizontal and vertical directions with respect to the boresite axis.
  • the same set of coils can be utilized to determine the angular rotation of the tool to provide suffiicient control for certain types of steering systems. For these systems, the angular rotation of the tool is displayed along with the plane in which the tool is expected to steer upon actuation of the guidance control system.
  • the mechanical guidance of the tool can also be controlled at a display panel 16. From controls located at display panel 16, both the operation of the tool 10 and the pneumatic or hydraulic actuation of the fins 17 can be accomplished as described hereinafter.
  • the boring tool 10 includes a steering system with a slanted-face nose member 18 attached to the anvil 33 of the tool to produce a turning force on the tool and tail fins 17 on a rotary housing 19 on the trailing end of the tool adapted to be selectively positioned relative to the body of the tool to negate the turning force.
  • Turning force may also be imparted to the tool by an internal eccentric hammer (Fig. 41) described hereinafter which delivers an off-axis impact to the tool anvil.
  • the tail fins 17 are moved into a position where they may spin about the longitudinal axis of the tool 10 and the slanted nose member 18 or eccentric hammer will deflect the tool in a given direction.
  • the rotation will negate the turning effect of the nose member 18 or eccentric hammer as well as provide a means for orienting the nose piece into any given plane for subsequent turning or direction change.
  • an eccentric hammer or anvil will produce the desired turning force, since the only requirement is that the axis of the impact does not pass through the frontal center of pressure.
  • the steering system of the present invention will allow the operator to avoid damaging other underground services (such as power cables) or to avoid placing underground utilities where they may be damaged.
  • Figs. 2 through 7 illustrate various combinations and implementations of the combination slanted nose member and tail fins steering system schematically and illustrates the basic operation of each design.
  • the function of the tail fins is to provide a method of executing controlled changes to the boring direction.
  • a fixed/lockable tail fin steering system 17 is illustated in Figs 2 and 3.
  • the tool is allowed to rotate about the longitudinal axis due to the turning force of the tail fins when in the locked position until the proper tool face orientation is obtained (Fig. 2).
  • the housing 19 is then unlocked and spins freely, whereby the tool moves in a curved path by the turning force of the slanted face nose member 18.
  • Straight boring by the tool 10 is accomplished by locking tail fin housing 19 to the main body 20 of the tool 10 (Fig. 3), to rotate the tool body and thus negate the turning action of the slanted nose member 18.
  • a boring tool 21 having a movable tail fin system is illustrated in Figs. 4 - 7.
  • the tail fins 22 are activated to a parallel position relative to the longitudinal axis of the tool body 20 and the tool 21 is allowed to turn relative to the longitudinal axis due to the turning force of the nose member 18 or the eccentric hammer.
  • Proper tool face orientation is obtained (Figs. 4 and 5) by use of the tail fins in a skewed inclined position.
  • Straight boring of the tool is accomplished by activating the fins 22 to an inclined position relative to the mole axis (Figs. 6 and 7) to rotate the tool body and thus negate the turning action of the slanted nose member 18.
  • Fig. 8 illustrates a boring tool 23 with a movable tail fin system in combination with an eccentric hammer 24.
  • the eccentric hammer may be used in combination with either the fixed/lockable fin system or the movable fin system and with or without the slanted nose member, depending upon the particular application. Either an eccentric hammer or anvil will produce the desired result, since the only requirement is that the axis of the impact does not pass through the frontal center of pressure. Unless negated by one of the previously described fin systems, the eccentric hammer 24 provides the side force required to turn the tool.
  • the eccentric hammer 24 is keyed to the main body 25 of the tool 23 by a pin 26 or other suitable means to maintain the larger mass of the hammer on one side of the longitudinal axis of the tool.
  • Turning of the tool 23 is accomplished by unlocking the tail fin housing of the fixed/lockable embodiment from the main mole body or turning the fins of the movable fin embodiment to a position parallel to the body axis.
  • the parallel fins or unlocked housing position eliminates the fins ability to negate the eccentric hammer force.
  • the tail fin housing is unlocked or the fins are activated to a skewed inclined position relative to the tool body axis and the tool is turned by the eccentric hammer force until the proper tool face orientation is obtained.
  • Straight boring is accomplished in all of the previously described implementations by continuously rotating the tool. This distributes the turning force over 360° and causes the tool to bore a helical (nearly straight) hole.
  • Figs. 9A, 9B, 9C, and 10 illustrate a typical boring tool 27 having a slanted nose member and fixed/lockable fin arrangement as described generally in reference to Figs. 1 and 2.
  • the boring tool 10 comprises an elongated hollow cylindrical outer housing or body 28.
  • the outer front end of the body 28 tapers inwardly forming a conical portion 29.
  • the internal diameter of the body 28 tapers inwardly near the front end forming a conical surface 30 which terminates in a reduced diameter 31 extending longitudinally inward from the front end.
  • the rear end of the body 28 has internal threads 32 for receiving a tail fin assembly (see Fig. 9C).
  • An anvil 33 having a conical back portion 34 and an elongated cylindrical front portion 35 is positioned in the front end of body 28.
  • the conical back portion 34 of anvil 33 forms an interference fit on the conical surface 30 of the body 28, and the elongated cylindrical portion 35 extends outwardly a predetermined distance beyond the front end of the body.
  • a flat transverse surface 36 at the back end of anvil 33 receives the impact of a reciprocating hammer 37.
  • Reciprocating hammer 37 is an elongated cylindrical member slidably received within the cylindrical recess 38 of the body 28. A substantial portion of the outer diameter of the hammer 37 is smaller in diameter than the recess 38 of the body 28, forming an annular cavity 39 therebetween. A relatively shorter portion 40 at the back end of the hammer 37 is of larger diameter to provide a sliding fit against the interior wall of recess 38 of the body 28.
  • a central cavity 41 extends longitudinally inward a distance from the back end of the hammer 37.
  • a cylindrical bushing 42 is slidably disposed within the hammer cavity 41, the circumference of which provides a sliding fit against the inner surface of the central cavity 41.
  • the front surface 43 of the front end of the hammer 37 is shaped to provide an impact centrally on the flat surface 36 of the anvil 33. As described hereinafter, the hammer configuration may also be adapted to deliver an eccentric impact force on the anvil.
  • An air distribution tube 45 extends centrally through the bushing 42 and has a back end 46 extending outwardly of the body 28 connected by fittings 47 to a flexible hose 48.
  • the air distribution tube 45 is in permanent communication with a compressed air source 11 (Fig. 1).
  • the arrangement of the passages 44 and the bushing 42 is such that, during reciprocation of the hammer 37, the air distribution tube 45 alternately communicates via the passages 44, the annular cavity 39 with either the central cavity 41 or atmosphere at regular intervals.
  • a cylindrical stop member 49 is secured within the recess 38 in the body 28 near the back end and has a series of longitudinally-extending, circumferentially-spaced passageways 50 for exhausting the interior of the body 28 to atmosphere and a central passage through which the air distribution tube 45 extends.
  • a slant-end nose member 18 has a cylindrically recessed portion 52 with a central cylindrical bore 53 therein which is received on the cylindrical portion 35 of the anvil 33 (Figs. 9A and 10).
  • a slot 54 through the sidewall of the cylindrical portion 52 extends longitudinally substantially the length of the central bore 53 and a transverse slot extends radially from the bore 53 to the outer circumference of the cylindrical portion, providing flexibility to the cylindrical portion for clamping the nose member to the anvil.
  • a flat 56 is provided on one side of cylindrical portion 52 and longitudinally spaced holes 57 are drilled therethrough in alignment with threaded bores 58 on the other side. Screws 59 are received in the holes 57 and bores 58 and tightened to secure the nose member 18 to the anvil 33.
  • the sidewall of the nose member 18 extends forward from the cylindrical portion 52 and one side is milled to form a flat inclined surface 60 which tapers to a point at the extended end.
  • the length and degree of inclination may vary depending upon the particular application.
  • the nose member 18 may optionally have a flat rectangular fin 61 (shown in dotted line) secured to the sidewall of the cylindrical portion 52 to extend substantially the length thereof and radially outward therefrom in a radially opposed position to the inclined surface 60.
  • Slanted nose members 18 of 6.4 cm and 8.9 cm diameter with angles from 10° to 40° have been tested and show the nose member to be highly effective in turning the tool with a minimum turning radius of 8.4 metres being achieved with a 8.9 cm 15 degree nose member. Testing also demonstrated that the turning effect of the nose member was highly repeatable with deviations among tests of any nose member seldom varying by more than a few fives-of-centimetres in 10.5 metres of bore. Additionally, the slanted nose members were shown to have no adverse effect on penetration rate and in some cases, actually increased it.
  • the turning radius varies linerly with the angle of inclination. For a given nose angle, the turning radius will decrease in direct proportion to an increase in area.
  • a tail fin assembly 62 is secured in the back end of the body 28 (Fig. 9C).
  • a fixed/lockable tail fin assembly 62 is illustrated in the example and other variations will be described hereinafter.
  • the tail fin assembly 62 comprises a cylindrical connecting sub 63 having external threads 64 at the front end which are received within the internal threads 32 at the back end of the body 28.
  • Sub 63 has a short reduced outside diameter portion 65 forming shoulder 66 therebetween and a second reduced diameter 67 adjacent the short portion 65 forms a second shoulder 68.
  • An O-ring seal 69 is located on the reduced diameter 65 intermediate the shoulders 66 and 68.
  • the rear portion 70 of the sub 63 is smaller in diameter than the second reduced diameter 67 forming a third shoulder 71 therebetween and provided with a circumferential O-ring seal 72 and an internal O-ring seal 73.
  • Internal threads 74 are provided in the rear portion 70 inwardly of the seal 73.
  • a circumferential bushing 75 of suitable bearing material such as bronze is provided on the second reduced diameter 67.
  • a series of longitudinal circumferentially spaced grooves or keyways 76 are formed on the circumference of the rear portion 70 of the sub 63.
  • a hollow cylindrical piston 77 is slidably received on the circumference of the rear portion 70.
  • a series of longitudinal circumferentially spaced grooves or keyways 78 are formed on the interior surface at the front portion of the piston 77 in opposed relation to the sub keyways 76.
  • a series of keys or dowel pins 79 are received within the keyways 76 and 78 to prevent rotary motion between the sub 63 and the piston 77.
  • a first internal cavity 80 extends inwardly from the keyway 78 terminating in a short reduced diameter portion 81 which forms a shoulder 82 therebetween.
  • a second cavity 83 extends inwardly from the back end 84 of the piston 77 terminating at the reduced diameter portion 81.
  • An internal annular O-ring seal 85 is provided on the reduced diameter portion 81.
  • a series of drive teeth 86 are formed on the back end of the piston 77.
  • the teeth 86 comprise a series of circumferentially spaced raised surfaces 87 having a straight side 88 and an angularly sloping side 89 forming a one-way ratchet configuration.
  • a compression spring 90 is received within the first cavity 80 of the piston 77 and is compressed between the back end 70 of the sub 63 and the shoulder 82 of the piston 77 to urge the piston outwardly from the sub.
  • An elongated, hollow cylindrical rotating fin sleeve 91 is slidably and rotatably received on the outer periphery of sub 63.
  • the fin sleeve 91 has a central longitudinal bore 92 and a short counterbore 93 of larger diameter extending inwardly from the front end and defining an annular shoulder 94 therebetween.
  • the counterbore 93 fits over the short reduced diameter 65 of the sub 63 with the O-ring 69 providing a rotary seal therebetween.
  • a flat annular bushing 95 of suitable bearing material such as bronze is disposed between the shoulders 68 and 94 to reduce friction therebetween.
  • a second counterbore 96 extends inwardly from the back end of the fin sleeve 91.
  • a hollow cylindrical sleeve 97 is secured within the second counterbore 96 by suitable means such as welding.
  • the sleeeve 97 has a central bore 98 substantially the same diameter as the second cavity 83 of the piston 77 and a counterbore 99 extending inwardly from the back end defining shoulder 100 therebetween.
  • a series of drive teeth 101 are formed on the front end of the sleeve 97.
  • the teeth 101 comprise a series of circumferentially spaced raised surfaces 102 having a straight side 103 and an angularly sloping side 104 forming a one-way ratchet configuration.
  • the teeth correspond in opposed relationship to the teeth 86 of the piston 77 for operative engagement therewith.
  • a series of flat radially and angularly opposed fins 105 are secured to the exterior of the fin sleeve 91 to extend radially outward therefrom. (Figs. 9C, 11 and 12)
  • the fins 105 are secured at opposing angles relative to the longitudinal axis of the sleeve 91 to impart a rotational force on the sleeve.
  • An elongated hollow cap sleeve 106 having external threads 107 at the front end is slidably received within the sliding piston 77 and the sleeve 97 and threadedly secured in the internal threads 74 at the rear portion 70 of the sub 63.
  • the cap sleeve 106 extends rearwardly from the threads 107 and an enlarged diameter portion 108 forms a first shoulder 109 spaced from the threaded portion and a second enlarged diameter 110 forms a second shoulder 111 spaced from the first shoulder.
  • An O-ring seal 112 is provided on the enlarged diameter 108 near the shoulder 109 and a second O-ring seal 113 is provided on the second enlarged diameter 110 near the second shoulder 111.
  • the O-ring 112 forms a reciprocating seal on the interior of the second cavity 83 of the piston 77 and the O-ring 113 forms a rotary seal on the counterbore 99 of the sleeve 97.
  • the O-ring 85 in the piston 77 forms a reciprocating seal on the extended sidewall of the cap 106.
  • An annular chamber 114 is formed between the exterior of the sidewall of the cap 106 and the second counterbore 83 which is sealed at each end by the O-rings 85 and 112.
  • a circumferential bushing 115 is provided on the first enlarged diameter 108 and an annular bushing 116 on the second enlarged diameter 110 is captured between the shoulders 100 and 111 to reduce friction between the sleeve 97 and the cap 106.
  • the rear portion of the cap 106 has small bores 117 arranged to receive a spanner wrench for effecting the threaded connection.
  • a threaded bore 118 at the back end of the cap 106 receives a hose fitting (not shown) and a small passageway 119 extends inwardly from the threaded bore 118 to communicate the annular chamber 114 with a fluid or air source (not shown).
  • a flexible hose extends outwardly of the cap 106 and is connected to the fluid or air source for effecting reciprocation of the piston 77.
  • a second small passageway 120 communicates the first cavity 80 with atmosphere to relieve pressure which might otherwise become trapped therein. Passage 120 may also be used for application of pressure to the forward end of the piston 77 for return movement.
  • Figs. 14 and 15 The operation of the percussion boring tool 27 is illustrated schematically in Figs. 14 and 15. Under action of compressed air or hydraulic fluid in the central cavity 41, the hammer 37 moves toward the front of the body 28. At the foremost position, the hammer imparts an impact on the flat surface 36 of the anvil 33.
  • the hammer 37 continues its movement by the expansion of the the air in the annular cavity 39 until the passages 44 are displaced beyond the ends of the bushing 42, and the annular cavity exhausts to atmosphere through the holes 50 in the stop member 49. In this position, the air is exhausted from the annular cavity 39 through the passages 44 now above the trailing edge of the bushing 42 and the holes 50 in the stop member 49. Then the cycle is repeated.
  • the operation of the tail fin assembly 62 is best seen with reference to Figs. 9C and 11.
  • the compressed air or fluid in the annular cavity 114 moves the piston 77 against the force of the spring 90 and toward the front of the sub 63.
  • the front end of the piston 77 contacts the shoulder 71 and the drive teeth 86 and 101 become dis-engaged.
  • compressed air or fluid is admitted through the passage 119 from the source into the annular chamber 114.
  • the fin sleeve 91 is then free to rotate relative to the tool body.
  • the force of the spring 90 moves the piston 77 in the opposite direction (Fig. 11).
  • the drive teeth 86 and 101 become engaged once again and the fin sleeve 91 becomes locked against rotational movement relative to the tool body.
  • Pressure which may otherwise become trapped in the first cavity 80 and hinder reciprocation is exhausted through the pressure relief passage 120 to atmosphere.
  • the cycle may be selectively repeated as necessary for proper alignment the slanted nose member 18 and attitude adjustment of the tool.
  • the passage 120 may also be connected to a fluid, i.e. liquid or air, source for moving the piston to the rearward position.
  • the tail fin assembly 119 comprises a cylindrical connecting sub 163 having external threads 164 at the front end which are received within the internal threads 32 at the back end of the body 28.
  • Sub 163 has a short reduced outside diameter portion 165 forming a shoulder 166.
  • the rear portion 170 of the sub 163 is smaller in diameter than the reduced diameter 165 forming a third shoulder 171 therebetween and provided with a circumferential O-ring seal 172.
  • a series of longitudinal circumferentially-spaced grooves or keyways 176 are formed on the rear portion 170 of the sub 163.
  • a hollow cylindrical piston 177 is slidably received on the circumference of the rear portion 170.
  • a series of longitudinal circumferentially spaced grooves or keyways 178 are formed on the interior surface at the front portion of the piston 177 in opposed relation to the sub keyways 176.
  • a series of keys or dowel pins 179 are received within the keyways 176 and 178 to prevent rotary motion between the sub 163 and the piston 177.
  • a first internal cavity 180 extends inwardly from the keyway 178 terminating in a short reduced diameter portion 181 which forms a shoulder 182 therebetween.
  • a second cavity 183 smaller than the first extends inwardly from the back end 184 of the piston 77 terminating at the reduced diameter portion 181.
  • O-ring seals 173 and 185 are provided on the interior of the first cavity 180 and reduced diameter portion 181 respectively.
  • a series of drive teeth 86 are formed on the back end of the piston 177.
  • the teeth 86 comprise a series of circumferentially spaced raised surfaces 87 having a straight side 88 and an angularly sloping side 89 forming a one-way ratchet configuration.
  • An elongated hollow cylindrical rotating fin sleeve 191 is rotatably received on the outer periphery of the sub 163.
  • the fin sleeve 191 has a central longitudinal bore 192.
  • the bore 192 is rotatably received on the reduced diameter 165 of the sub 163 with the O-ring 169 providing a rotary seal therebetween.
  • a flat annular bushing 195 of suitable material such as bronze is disposed between the shoulder 168 and the front of the fin sleeve 191 to reduce friction.
  • a hollow cylindrical sleeve 197 is secured within the rear portion of the fin sleeve bore 192 by suitable means such as welding.
  • the sleeeve 197 has a central bore 198 substantially the same diameter as the second cavity 183 of the piston 177.
  • a series of drive teeth 101 are formed on the front end of the sleeve 197.
  • the teeth 101 comprise a series of circumferentially spaced raised surfaces 102 having a straight side 103 and an angularly sloping side 104 forming a one-way ratchet configuration.
  • the teeth correspond in opposed relationship to the teeth 86 of the piston 177 for operative engagement therewith.
  • An O-ring 213 and a bushing 215 are provided in the central bore 198.
  • a series of flat, radially and angularly opposed fins 205 are secured to the exterior of the fin sleeve 191 to extend radially outward therefrom.
  • the fins 205 are secured at opposing angles relative to the longitudinal axis of the sleeve 191 to impart a rotational force on the sleeve.
  • An elongated hollow cylindrical cylinder cap 206 having external threads 207 at the front end is slidably received within the sliding piston 177 and the sleeve 197 and threadedly secured in the internal threads 174 at the rear portion 170 of the sub 163.
  • the circumference of the cap 206 extends rearwardly from the threads 207 and an enlarged diameter portion 208 forms first shoulder 209 spaced from the threaded portion and a second enlarged diameter 210 forms second shoulder 211 spaced from the first shoulder.
  • An O-ring seal 212 is provided on the enlarged diameter 208 near the shoulder 209.
  • the O-ring 212 forms a reciprocating seal on the interior of the second cavity 183 of the piston 177 and the O-ring 213 forms a rotary seal on the central bore 198 of the sleeve 197.
  • the O-ring 185 in the piston 177 forms a reciprocating seal on the extended sidewall of the cap 206.
  • An annular rear chamber 214 is formed between the exterior of the sidewall of the cap 206 and the second smaller bore 183 which is sealed at each end by the O-rings 185 and 212.
  • An annular front chamber 216 is formed between the sidewall of the cap 206, the cavity 180, and the back end of, the sub 163, which is sealed by the O-rings 172, 173, and 185.
  • the side wall of the sub 163 has small bores 217 arranged to receive a suitable wrench for effecting the threaded connection.
  • a threaded bore 218 at the back end of the cap 206 receives a hose fitting (not shown) and a small passageway 219 extends inwardly from the threaded bore 218 to communicate the rear chamber 214 with a fluid or air source (not shown).
  • Another similar threaded bore at the back end of the cap receives a hose fitting (not shown) and a small passageway 220 extends inwardly from the threaded bore to communicate the front chamber 216 with a fluid or air source (not shown).
  • Flexible hoses extend outwardly of the cap 206 and are connected to the fluid or air source for effecting reciprocation of the piston 177.
  • the operation of the tail fin assembly 119 is illustrated schematically in Figs. 16 and 17.
  • the piston 177 moves toward the front of the sub 163.
  • the drive teeth 86 and 101 are disengaged and the fin sleeve 191 is free to rotate about the longitudinal axis of the tool body.
  • compressed air or fluid in the front chamber 216 has been exhausted.
  • compressed air or fluid is admitted through the passage 220 into the front chamber 216 and exhausted from the rear chamber 214 to move the piston 177 in the opposite direction.
  • the drive teeth 86 and 101 are once again engaged preventing rotational movement.
  • the cycle may be selectively repeated as necessary for proper alignment the slanted nose member and attitude adjustment of the tool.
  • FIG. 18 Another variation of the fixed/lockable tail fin assembly having drive teeth is illustrated in Figs. 18 and 19. To avoid repetition, some of the components, details, and reference numerals previously shown and described with reference to Figs. 9C and 11 will not be repeated here. Other components previously described will carry the same numerals of reference.
  • the tail fin assembly 219 comprises a cylindrical connecting sub 263 having external threads at the front end which are received within the internal threads at the back end of the body.
  • the sub 263 has a short reduced diameter portion forming a first shoulder and a second reduced diameter adjacent the short portion forms a second shoulder.
  • An annular O-ring seal is provided on the first reduced diameter intermediate the first and second shoulders.
  • the sidewall of the sub 263 extends rearwardly from the second shoulder.
  • the rear portion 270 of the sub 263 is smaller in diameter than the second reduced diameter forming a third shoulder 268 and a fourth reduced diameter defines a fourth shoulder 271.
  • a circumferential O-ring seal 272 is provided at back end of the sub 263. External threads 274 are provided in the rear portion 270 inwardly of the seal 272.
  • a series of circumferentially spaced spherical apertures 276 are formed on the circumference of the sidewall of the sub 263 near the third shoulder 271 and carry a series of balls 279.
  • a hollow cylindrical piston 277 is slidably received on the circumference of the rear portion 270.
  • a series of longitudinal circumferentially spaced grooves or keyways 278 are formed on the interior surface at the front portion of the piston 277 in opposed relation to the balls 279. The balls 279 within apertures 276 and keyways 278 prevent rotary motion between sub 263 and piston 277.
  • a first cavity 280 extends inwardly from the front end of the piston 277 and terminates in a short reduced diameter portion 281 which forms a shoulder 282.
  • a second cavity 283 extends inwardly from the back end of the piston 277 terminating at the reduced diameter portion 281.
  • An O-ring seal 285 is provided on the reduced diameter portion 281.
  • a series of drive teeth 86 are formed on the back end of the piston 277.
  • the teeth 86 comprise a series of circumferentially spaced raised surfaces 87 having a straight side 88 and an angularly sloping side 89 forming a one-way ratchet configuration.
  • a compression spring 290 surrounds the sidewall of the sub 263 and the ends of the spring are biased against the shoulder 268 of the sub 270 and the front end of the piston 277 to urge the piston outwardly from the sub.
  • a hollow cylindrical rotating fin sleeve 291 having a rear counterbore 296 is slidably and rotatably received on the outer periphery of sub 263.
  • a hollow cylindrical sleeve 297 is secured within the second counterbore 296 by suitable means such as welding.
  • the sleeve 297 has a central bore substantially the same diameter as the second cavity 283 of the piston 277.
  • a series of drive teeth 101 are formed on the front end of the sleeve 297.
  • the teeth 101 comprise a series of circumferentially spaced raised surfaces 102 having a straight side 103 and an angularly sloping side 104 forming a one-way ratchet configuration.
  • the teeth correspond in opposed relationship to the teeth 86 of the piston 277 for operative engagement therewith.
  • a series of flat radially and angularly opposed fins as previously described are secured to the exterior of the fin sleeve to extend radially outward therefrom.
  • An elongated hollow cylindrical cylinder cap 306 having internal threads 307 at the front end is slidably received within the sliding piston 277 and the sleeve 297 and threadedly secured on the external threads 274 at the rear portion 270 of the sub 263.
  • An O-ring seal 312 is provided on the outer front portion of cap 306 and a second O-ring seal 313 is provided on the rear portion.
  • the O-ring 312 forms a reciprocating seal on the interior of cavity 283 of piston 277 and O-ring 313 forms a rotary seal on the counterbore of fin sleeve 291.
  • the O-ring 285 in piston 277 forms a reciprocating seal on the sidewall of cap 306.
  • An annular chamber 314 is formed between the exterior of the sidewall of the cap 306 and the counterbore 283 which is sealed at each end by the O-rings 285 and 312. Bushings as previously described are provided on the sub 263 and cylinder cap 306 to reduce friction therebeween.
  • the rear portion of the cap has a threaded bore 318 at the back end of the cap 306 which receives a hose fitting (not shown) and a small passageway 319 extends inwardly from the threaded bore 318 to communicate the annular chamber 314 with a fluid or air source (not shown).
  • a flexible hose extends outwardly of the cap 306 and is connected to the fluid or air source for effecting reciprocation of the piston 277.
  • the operation of the tail fin assembly 219 is best seen with reference to Figs. 18 and 19.
  • Compressed air or fluid in the annular cavity 314 moves the piston 277 to overcome the force of the spring 290 and move toward the front of sub 263.
  • the drive teeth 86 and 101 become disengaged.
  • compressed air or fluid is admitted through the, passage 319 from the source into the annular chamber 314.
  • the fin sleeve 281 is then free to rotate relative to the tool body.
  • Figs. 20 and 21 are longitudinal cross sections of an alternate embodiment of the fixed/lockable fin assembly which incorporates a drive pin arrangement in place of one of the drive teeth members previously described. It will be noted that the drive pin arrangement necessitates moving the fin sleeve along the longitudinal axis to effect fin positioning.
  • the tall fin assembly 400 comprises a cylindrical connecting sub 401 having external threads 402 at the front end which are received within the internal threads 32 at the rear portion of the body 28.
  • the sub 401 has a first reduced diameter portion 403 forming a first shoulder 404 and a second reduced diameter 405 adjacent the first forms a second shoulder 406 which receives an annular seal 407.
  • the rear portion 408 of sub 401 is smaller in diameter than the second reduced diameter 405 and extends longitudinally therefrom.
  • a thin cylindrical retainer ring 409 is secured on the first reduced diameter 403 of the sub 401 by screws 410 and a small annular rib 411 on the interior surface of the ring captures the seal 407 within the second shoulder 406.
  • the rear end of ring 409 extends a short distance beyond seal 407 to surround the forward end of the rear portion 408 of the sub 401.
  • An elongated, hollow cylindrical rotating fin sleeve 412 is slidably and rotatably received within the extended portion of ring 409 and surrounds the rear portion 408 of sub 401.
  • the fin sleeve 412 has a central longitudinal bore 413 and a counterbore 414 of larger diameter extending inwardly from the back end and defining an annular shoulder 415 therebetween.
  • An O-ring seal 416 on fin sleeve 412 provides a rotary and reciprocating seal on the inner surface of ring 409.
  • a plurality of circumferentially spaced dowel pins 417 extend radially inwardly through the side wall of the fin sleeve 412 and terminate a short distance from the circumference of the rear portion 408 of the sub 401.
  • An annular O-ring seal 418 and a bushing 419 is provided on the interior surface of the fin sleeve 412 intermediate the dowel pins 417 and shoulder 415.
  • a series of radially and angularly opposed fins 420 are secured to the exterior of the rotating fin sleeve 412 to extend radially outward therefrom.
  • the fins are secured at opposing angles relative to the longitudinal axis of the sleeve 412 to impart a rotational force on the sleeve.
  • An elongated hollow cylindrical cap 421 is slidably received on the sub rear portion 408 within fin sleeve 412 and secured to sub 401 by means of a screw 422 at the rear portion thereof.
  • the cap 421 has a reduced diameter front portion 423 and an enlarged diameter rear portion 424 forming a shoulder 425.
  • a pair of longitudinally spaced O-rings 426 are positioned on the rear portion 424 and a bushing 427 is provided intermediate the O-rings 426.
  • the enlarged diameter rear portion 424 of the cap 421 is rotatably received within counterbore 414 with the O-rings 426 providing a rotary seal therebetween.
  • a series of drive teeth 428 are formed on the front end of the cap 421.
  • the drive teeth 428 comprise a series of circumferentially spaced raised surfaces 429, each having a generally straight side 430 and an angularly sloping side 431 forming a one-way ratchet configuration.
  • the spacing of the drive teeth 428 relative to the dowel pins 417 is such that the pins will be retained by the teeth in the locked position to prevent rotary motion between the fin sleeve 412 and cap 421 as described hereinafter.
  • annular chamber 432 When properly positioned, an annular chamber 432 is formed between the shoulder 415 of the fin sleeve and the shoulder 425 of the cap and sealed at each end by the O-rings 418 and 426.
  • a threaded bore 433 at the back end of the cap 421 receives a hose fitting (not shown) and a small passageway 434 extends inwardly from the threaded bore to communicate the annular chamber 432 with a fluid or air source (not shown) for reciprocatiing fin sleeve 412.
  • the driving force of the tool hammer carries the tool including the cap 421 forward (Fig. 21).
  • drive teeth 428 and dowel pins 417 become engaged once again and fin sleeve 412 becomes locked against rotational movement relative to the tool body.
  • the cycle may be selectively repeated as necessary for proper alignment of the slanted nose member and attitude adjustment of the tool.
  • Figs. 23 and 24 are partial longitudinal cross sections of variations of the fixed/lockable fin assembly using a drive pin.
  • the tail fin assembly 500 comprises a cylindrical connecting sub 501 having external threads 502 at the front end which are received within the internal threads 32 at the rear portion of the body 28.
  • the sub 501 has a first reduced diameter portion 503 forming a shoulder 504.
  • the rear portion 505 of the sub 501 is smaller in diameter than the first reduced diameter 503 forming a second shoulder 506.
  • the rear portion 505 extends longitudinally from shoulder 506 and has exterior threads 507 at the back end.
  • a thin cylindrical retainer ring 508 is received on the reduced diameter 503 of sub 501 by screws 509.
  • the rear end of ring 508 extends a short distance beyond the shoulder 506 to surround the forward end of the rear portion 505 of the sub 501.
  • An elongated hollow cylindrical rotating fin sleeve is slidably and rotatably received within the extended portion of ring 508 and surrounds the rear portion 505 of sub 501.
  • the fin sleeve 510 has a central longitudinal bore 511 and a counterbore 512 of larger diameter extending inwardly from the back end and defining an annular shoulder 513.
  • An O-ring seal 514 on the fin sleeve 510 provides a rotary and reciprocating seal on the inner surface of the ring 508.
  • a plurality of circumferentially spaced dowel pins 515 extend radially inwardly through the side wall of the fin sleeve 510 and terminate a short distance from the circumference of the rear portion 505 of the sub 501.
  • An O-ring seal 516 and a bushing 517 are positioned on the interior surface of fin sleeve 410 intermediate the dowel pins 515 and shoulder 513.
  • a plurality of radially and angularly opposed fins 518 are secured to the exterior of the rotating fin sleeve 510 and extend radially outward therefrom.
  • the fins 518 are secured at opposing angles relative to the longitudinal axis of the sleeve 510 to impart a rotational force on the sleeve.
  • a tubular cap 519 having a central bore 520 and a threaded counterbore 521 extending inwardly from the front end is slidably received on the air distribution tube 46 and the sub rear portion 505 within the fin sleeve 510.
  • the cap 519 is threadedly received and secured on the threads 507 at the end of the sub 501.
  • the cap 519 has a reduced diameter front portion 522 and an enlarged diameter rear portion 523 forming a shoulder 524 therebetween.
  • a pair of longitudinally spaced O-rings 525 are provided on the rear portion 523 and a bushing 526 is provided intermediate the O-rings 525.
  • the enlarged diameter rear portion 523 of cap 519 in rotatably received within the counterbore 512 with O-rings 525 providing a rotary seal.
  • a plurality of drive tooth 428 are formed on the front end of the cap 519.
  • the rear portion 523 of the cap 519 has a reduced diameter portion 527 which removably receives a conical cover member 528.
  • a plurality of circumferentially spaced longitudinal bores 529 extend through the rear portion of the cap 519 for communicating the interior of the body 28 with atmosphere.
  • the drive teeth are constructed and operate an previously described for the other embodiments.
  • annular chamber 530 in formed between the shoulder 513 of the fin sleeve and the shoulder 524 of the cap and sealed at each end by the O-rings 516 and 524.
  • a threaded bore 433 at the back end of the cap 519 receives a hose fitting (not shown) and a small passageway 434 extends inwardly from the threaded bore to communicate the annular chamber 530 with a fluid or air source (not shown) for effecting reciprocation of the fin sleeve 510.
  • Figs. 23 and 24 Compressed air or fluid in the annular chamber 530 moves the fin sleeve 510 toward the front of the sub 501. In its foremost position, the front end of the sleeve 510 contacts the shoulder 506 and the dowel pins 515 disengage from the drive teeth 428. In this position (Fig. 23), compressed air or fluid is admitted through the passage 434 from the source into the annular chamber 530. The fin sleeve 510 is then free to rotate relative to the tool body.
  • the driving force of the tool hammer carries the tool including the cap 519 forward (Fig. 24).
  • the drive teeth 428 and dowel pins 515 engage once again and the fin sleeve 510 is locked against rotational movement relative to the tool body.
  • the cycle may be selectively repeated as necessary for proper alignment of the slanted nose member and attitude adjustment of the tool.
  • Figs. 25 and 26 are partial longitudinal cross sectional views of a variation of the fixed/lockable fin assembly using an interlocking lug arrangement to prevent rotational movement.
  • the tail fin assembly 600 comprises a cylindrical connecting sub 601 having external threads at the front end which are received within the internal threads at the rear portion of the body (not shown).
  • the circumference of the sub 601 has a first reduced diameter portion 602 forming a first shoulder 603.
  • the rear portion 604 of the sub 661 is smaller in diameter than the first reduced diameter 602 forming a second shoulder 605.
  • An annular raised surface 606 on the rear portion 604 is spaced rearwardly from the shoulder 605 and provided with a series of circumferentially spaced slots 607 forming a series of raised lugs or splines 608.
  • the rear portion 604 extends longitudinally from the lugs 608 and is provided with exterior threads 609 at the back end.
  • An annular O-ring seal 610 is provided on the rear portion 604 inwardly of
  • a thin cylindrical retainer ring 508 is received on the first reduced diameter 602 of the sub 601 by screws 509.
  • the rear end of the ring 508 extends a short distance beyond the shoulder 605 to surround the forward end of the rear portion 604 of the sub 601.
  • An elongated hollow cylindrical rotating fin sleeve 611 is slidably and rotatably received within the extended portion of the ring 508 and surrounds the rear portion 604 of the sub 601.
  • the fin sleeve 611 has a central longitudinal bore 612, a front and rear counterbore 613 and 614 respectively of larger diameter extending inwardly from each end and defining annular shoulders 615 and 616 therebetween.
  • An annular O-ring seal 617 and annular bushing 618 are disposed on central bore 612 intermediate the shoulders 615 and 616.
  • a reduced diameter 619 is provided on the inner diameter of the front counterbore 613 near the front end and provided with a series of circumferentially spaced slots 620 forming a series of raised lugs or splines 621.
  • An O-ring seal 622 on the outer circumference of the fin sleeve 611 provides a rotary and reciprocating seal on the inner surface of the ring 508.
  • a plurality of radially and angularly opposed fins 518 are secured to the exterior of the rotating fin sleeve 611 to extend radially outward therefrom.
  • the fins 518 are secured at opposing angles relative to the longitudinal axis of the sleeve 611 to impart a rotational force on the sleeve.
  • An elongated hollow cylindrical cap 623 having a central bore 624 and a larger threaded bore 625 extending inwardly from the front end is slidably received on the air distribution tube 46 and threadedly secured on the threads 609 at the end of the sub 601.
  • the outer circumference of the cap 623 is received within the rear counterbore 614 of the fin sleeve 611.
  • a pair of longitudinally spaced annular O-rings 626 are provided on the outer circumference of the cap 623 and a bushing 627 is provided intermediate O-rings 626.
  • the outer circumference of the cap 623 is rotatably received within the counterbore 614 with the O-rings 626 providing a rotary seal therebetween.
  • the rear portion of the cap 623 has a reduced diameter portion 628 which removably receives a conical cover member 629.
  • a plurality of circumferentially spaced longitudinal bores 630 extend through the rear portion of the cap for communicating the interior of the tool body with atmosphere.
  • annular chamber 631 is formed between the shoulder 616 of the fin sleeve and the forward end of the cap 623 and sealed at each end by the O-rings 610, 617, and 626.
  • a threaded bore 433 at the back end of the cap 623 receives a hose fitting (not shown) and a small passageway 434 extends inwardly from the threaded bore to communicate the annular chamber 631 with a fluid or air source (not shown) for effecting reciprocation of the fin sleeve.
  • the operation of the tail fin assembly 600 is best seen with reference to Figs. 25 and 26.
  • the fin sleeve 611 Under action of compressed air or fluid in the annular chamber 631 the fin sleeve 611 begins to move toward the front of the sub 601. When in its foremost position, the front end of the sleeve 611 contacts the shoulder 605 and the lugs 608 and 621 become disengaged. In this position (Fig. 25), compressed air or fluid is admitted through the passage 434 from the source into the annular chamber 631. The fin sleeve 611 is then free to rotate relative to the tool body.
  • the driving force of the tool hammer carries the tool including the cap 623 forward (Fig. 26).
  • the drive lugs or splines 608 and 621 become engaged once again and the fin sleeve 611 becomes locked against rotational movement relative to the tool body.
  • the cycle may be selectively repeated as necessary for proper alignment or the slanted nose member and attitude adjustment of the tool.
  • Figs. 27 and 28 are partial longitudinal cross sections of another variation of the fixed/lockable fin assembly using a drive pin.
  • the tail fin assembly 650 comprises a cylindrical connecting sub 651 having external threads 652 at the front end which are received within the internal threads 32 at the rear portion of the body 28.
  • the rear portion 653 of the sub 651 is smaller in diameter than the front portion forming a shoulder 654.
  • the rear portion 653 extends longitudinally from the shoulder 654 and has interior threads 655 at the back end.
  • a thin cylindrical retainer ring 656 is received on the front portion of the sub 651 between a raised shoulder 657 and the back end of the body 28.
  • the rear end of the ring 656 extends a short distance beyond the raised shoulder 657 to surround the forward end of the rear portion 653 of the sub 651.
  • a plurality of circumferentially spaced dowel pins 417 extend radially outward through the side wall of the rear portion 653 and terminate a short distance from the interior surface of the ring 656.
  • An elongated hollow cylindrical rotating fin sleeve 659 is slidably and rotatably received within the extended portion of the ring 656 and surrounds the rear portion 653 of the sub 651 including the dowel pins 417.
  • the fin sleeve 659 has a central longitudinal bore 660 and a counterbore 661 of larger diameter extending inwardly from the back end and defining an annular shoulder 662 therebetween.
  • An O-ring seal 663 on the outer circumference of the fin sleeve 659 provides a rotary and reciprocating seal on the inner surface of the ring 656.
  • An annular O-ring seal 664 and a pair of bushings 665 are provided on the interior surface of the fin sleeve 659.
  • a plurality of drive teeth 428 (as previously shown and described) are formed on the front end of the fin sleeve 659.
  • a plurality of radially and angularly opposed fins 666 are secured to the exterior of the rotating fin sleeve 659 to extend radially outward therefrom.
  • the fins 666 are secured at opposing angles relative to the longitudinal axis of the sleeve 659 to impart a rotational force on the sleeve.
  • An elongated hollow cylindrical cap 667 having a central bore 668 and a counterbore 669 extending inwardly from the front end is slidably received on the air distribution tube 46 within the fin sleeve 659. Exterior threads 670 are provided on the front portion of the cap 667 which are received on the threads 655 at the back end of the sub 651. The rear portion of the cap 667 is larger in diameter than the threaded front portion forming a shoulder 671 therebetween.
  • a pair of longitudinally spaced annular O-rings 672 are provided on the outer circumference of the rear portion and a bushing 673 is provided intermediate the O-rings.
  • the enlarged diameter rear portion of the cap 667 is rotatably received within the counterbore 661 with the O-rings 672 providing a rotary seal therebetween.
  • the rear portion of the cap 667 removably receives a conical cover member 674.
  • annular chamber 675 is formed between the shoulder 662 of the fin sleeve and the shoulder 671 of the cap and sealed at each end by the O-rings 663 and 672.
  • a threaded bore 433 at the back end of the cap 667 receives a hose fitting (not shown) and a small passageway 434 extends inwardly from the threaded bore to communicate the annular chamber 675 with a fluid or air source (not shown) for effecting reciprocation of the fin sleeve 659.
  • Fig. 28 shows the locked position, and since the operation of the tail fin assembly has been previously shown and explained, it will not be repeated here.
  • Figs. 29 and 30 are partial longitudinal cross sections of another variation of the fixed/lockable fin assembly using a series of slots or splines and dowel pins to prevent rotational movement.
  • the tail fin assembly 700 comprises a cylindrical connecting sub 701 having external threads 702 at the front end which are received within the internal threads 32 at the rear portion of the body 28.
  • the circumference of the sub 701 has a first reduced diameter portion 703 forming a first shoulder 704 therebetween.
  • a second reduced diameter 705 forms a second shoulder 706.
  • a third reduced diameter 707 forms a third reduced diameter 708.
  • An enlarged diameter 709 approximately the same diameter as the second is spaced therefrom and provided with a series of circumferentially spaced slots 710 defining a series of raised lugs or splines 711 on the third reduced diameter 707.
  • a fourth diameter 712 smaller than the third forms a fourth shoulder 714 therebetween.
  • the fourth diameter 712 extends longitudinally from the shoulder 714 and is provided with exterior threads 715 at the back end.
  • a thin cylindrical retainer ring 716 is received on the first reduced diameter 703 of the sub 701 by screws 717.
  • the rear end of the ring 716 extends a short distance beyond the shoulder 706 to surround the forward end of the reduced diameter 705.
  • a rod wiper 718 is contained on the interior of the rear end of the ring 716.
  • An elongated hollow cylindrical rotating fin sleeve 719 is slidably and rotatably received within the extended portion of the ring 716 and surrounds the rear portion of the sub 701.
  • the fin sleeve 719 has a central longitudinal bore 720, a front and rear counterbore 721 and 722 respectively of larger diameter extending inwardly from each end and defining annular shoulders 823 and 724 therebetween.
  • An annular bushing 725 is disposed on the inner diameter of the counterbore 721 and a rod wiper 726 is provided on the inner diameter of the counterbore 722.
  • a plurality of circumferentially spaced dowel pins 727 extend radially inwardly through the side wall of the fin sleeve 719 and terminate a short distance from the circumference of the third reduced diameter 707 of the sub 701.
  • An annular bushing 728 is provided on the central bore 720 intermediate the shoulders 723 and 724.
  • a plurality of radially and angularly opposed fins 729 are secured to the exterior of the rotating fin sleeve 719 to extend radially outward therefrom.
  • the fins 729 are secured at opposing angles relative to the longitudinal axis of the sleeve 719 to impart a rotational force on the sleeve.
  • An elongated hollow cylindrical cap 730 having a central bore 731 provided with interior threads 732 and a counterbore 733 extending inwardly from the front end is received on the threads 715 of the sub 701 and within the counterbore 722 of the fin sleeve 719.
  • An annular O-ring 734 on the bore 731 provides a seal on the fourth reduced diameter 712 of the sub 701.
  • a cylindrical reciprocating piston 735 is slidably reeived on the fourth reduced diameter 712 of the sub 701 and within the counterbore 733 of the cap 730.
  • Annular O-rings 736 and 737 are provided on the inner and outer diameters respectively of the piston 735.
  • annular chamber 736 is formed between the fourth reduced diameter 712 and the counterbore 733 and sealed at each end by the O-rings 734, 736 and 737.
  • a threaded bore 433 at the back end of the cap 730 receives a hose fitting (not shown) and a small passageway 434 extends inwardly from the threaded bore to communicate the annular chamber 736 with a fluid or air source (not shown) for effecting reciprocation of the piston 735 and fin sleeve 719.
  • the operation of the tail fin assembly 700 is best seen with reference to Figs. 29 and 30.
  • the piston 735 Under action of compressed air or fluid in the annular chamber 736 the piston 735 begins to move toward the front of the sub 701 and contacts the shoulder 724 of the fin sleeve 719 carrying it forward.
  • the front end of the piston 735 contacts the shoulder 714 and the dowel pins 727 become disengaged from the slots or splines 810.
  • compressed air or fluid is admitted through the passage 434 from the source into the annular chamber 736.
  • the fin sleeve 719 is then free to rotate relative to the tool body.
  • the driving force of the tool hammer carries the tool including the sub 701 forward relative to the fin sleeve 719 (Fig. 24).
  • the shoulder 724 moves the piston rearwardly and the dowel pins 727 become engaged once again in the slots 710 and the fin sleeve 719 becomes locked against rotational movement relative to the tool body.
  • the cycle may be selectively repeated as necessary for proper alignment of the slanted nose member and attitude adjustment of the tool.
  • Figs. 31 and 32 are partial longitudinal cross sections of another variation of the fixed/lockable fin assembly using a series of slots or splines and dowel pins to prevent rotational movement.
  • the tail fin assembly 750 comprises a cylindrical connecting sub 751 having external threads 752 at the front end which are received within the internal threads 32 at the rear portion of the body 28.
  • the circumference of the sub 751 has a first reduced diameter portion 753 forming a first shoulder 754 therebetween.
  • a second reduced diameter 755 forms a second shoulder 906.
  • a third reduced diameter 757 forms a third shoulder 758.
  • An enlarged diameter 759 approximately the same diameter as the second is spaced therefrom and provided with a series of circumferentially spaced slots 760 defining a series of raised lugs or splines 761 on the third reduced diameter 757.
  • the third diameter 757 extends longitudinally from the lugs or splines 761 and is provided with exterior threads 762 at the back end.
  • a thin cylindrical retainer ring 763 is received on the first reduced diameter 753 of the sub 751 by screws 754.
  • the rear end of the ring 763 extends a short distance beyond the shoulder 756 to surround the forward end of the reduced diameter 755.
  • a rod wiper 765 is contained on the interior of the rear end of the ring 763.
  • An elongated hollow cylindrical rotating fin sleeve 766 is slidably and rotatably received within the extended portion of the ring 763 and surrounds the rear portion of the sub 751.
  • the fin sleeve 766 has a central longitudinal bore 767, a front and rear counterbore 768 and 769 respectively of larger diameter extending inwardly from each end and defining annular shoulders 770 and 771 therebetween.
  • An annular bushing 772 is disposed on the inner diameter of the counterbore 768 and a rod wiper 773 is provided on the inner diameter of the rear counterbore 769.
  • a plurality of circumferentially spaced dowel pins 774 extend radially inwardly through the side wall of the fin sleeve 766 and terminate a short distance from the circumference of the third reduced diameter 757 of the sub 751.
  • a plurality of radially and angularly opposed fins 775 are secured to the exterior of the rotating fin sleeve 766 to extend radially outward therefrom.
  • the fins 775 are secured at opposing angles relative to the longitudinal axis of the sleeve 766 to impart a rotational force on the sleeve.
  • An elongated hollow cylindrical cap 776 having a central bore 777 provided with interior threads 778 and a counterbore 779 extending inwardly from the front end is received on the threads 762 of the sub 751 and within the counterbore 769 of the fin sleeve 766.
  • An annular O-ring 780 on the bore 777 provides a seal on the third reduced diameter 757 of the sub 751.
  • An annular bushing 781 is provided on the circumference of the cap 776.
  • a cylindrical reciprocating piston 782 is slidably received on the third reduced diameter 757 of the sub 751 and within the counterbore 769 of the cap 776.
  • a reduced diameter 783 at the front end of the piston is received within the central bore 767 of the fin sleeve 766.
  • Annular O-rings 784 and 785 are provided on the inner and outer diameters respectively of the piston 781.
  • annular chamber 786 is formed between the circumference of the sub 751 and the counterbore 777 and sealed at each end by the O-rings 780, 784 and 785.
  • a threaded bore 433 at the back end of the cap 786 receives a hose fitting (not shown) and a small passageway 434 extends inwardly from the threaded bore to communicate the annular chamber 785 with a fluid or air source (not shown) for effecting reciprocation of the piston 782 and fin sleeve 766.
  • the operation of the tail fin assembly 750 is best seen with reference to Figs. 31 and 32.
  • the piston 782 Under action of compressed air or fluid in the annular chamber 786 the piston 782 begins to move toward the front of the sub 751 and carries the fin sleeve 766 with it.
  • the front end of the piston 782 contacts the lugs or splines 761 and the dowel pins 774 become disengaged from the slots 760.
  • compressed air or fluid is admitted through the passage 434 from the source into the annular chamber 786.
  • the fin sleeve 766 is then free to rotate relative to the tool body.
  • the driving force of the tool hammer carries the tool including the sub 751 forward relative to the fin sleeve 766 (Fig. 32).
  • the shoulder 771 moves the piston rearwardly and the dowel pins 774 become engaged once again in the slots or splines 760 and the fin sleeve 766 becomes locked against rotational movement relative to the tool body.
  • the cycle may be selectively repeated as necessary for proper alignment of the slanted nose member and attitude adjustment of the tool.
  • Figs. 33 and 34 are partial longitudinal cross sections of another variation of the fixed/lockable fin assembly using a series of dowel pins and drive teeth to prevent rotational movement.
  • the tail fin assembly 800 comprises a cylindrical connecting sub 801 having external threads 802 at the front end which are received within the internal threads at the rear portion of the tool body.
  • the circumference of the sub 801 has a first reduced diameter portion 803, and a second reduced diameter 804 forms a shoulder 805 therebetween.
  • a third reduced diameter 806 forms a third shoulder 807.
  • the third diameter 806 extends longitudinally from the shoulder 807 and is provided with exterior threads 808 at the back end.
  • a thin cylindrical retainer ring 809 is received on the first reduced diameter 803 of the sub 801 by screws 810.
  • the rear end of the ring 809 extends a short distance beyond the shoulder 805 to surround the forward end of the reduced diameter 804.
  • a rod wiper 811 is contained on the interior of the rear end of the ring 809.
  • An elongated hollow cylindrical rotating fin sleeve 812 has a central longitudial bore 813, and a rear counterbore 814 of larger diameter extending inwardly from the back end and defining an annular shoulder 815 therebetween.
  • An annular bushing 816 is provided on the central bore and another bushing 817 is provided on the counterbore 814.
  • the outer circumference of the fin sleeve 812 is provided with front reduced diameter 818 and a rear reduced diameter 819.
  • the fin sleeve 812 is slidably and rotatably received on the sub 801 with the central bore 813 on the second reduced diameter 804 and the front reduced diameter 818 within the extended portion of the ring 809.
  • a series of drive teeth 428 previously shown and described with reference to Fig. 22 are formed on the back end of the fin sleeve 812.
  • a plurality of radially and angularly opposed fins 820 are secured to the exterior of the rotating fin sleeve 812 to extend radially outward therefrom.
  • the fins 820 are secured at opposing angles relative to the longitudinal axis of the sleeve 812 to impart a rotational force on the sleeve.
  • An elongated hollow cylindrical cap 821 having a central bore 822 provided with interior threads 823 and a counterbore 824 extending inwardly from the front end and defining a shoulder 825 therebetween is received on the threads 808 of the sub 801 and within the counterbore 814 of the fin sleeve 812.
  • An annular O-ring 826 on the bore 822 provides a seal on the third reduced diameter 806 of the sub 801, and another O-ring 827 on the counterbore 814 provides a seal on the reduced portion of a piston member described hereinafter.
  • a plurality of circumferentially spaced dowel pins 828 extend radially outward through the side wall of the fin sleeve 812 (shown out of position).
  • a cylindrical reciprocating piston 829 is slidably received on the third reduced diameter 806 of the sub 801.
  • the rear portion 830 of the piston 829 is smaller in diameter than the outer circumference defining a shoulder 831 therebetween.
  • the outer circumference of the piston 829 is received in the annulus between the third reduced diameter 806 and the fin sleeve counterbore 814 and the rear portion 830 is received in the annulus between the third reduced diameter 806 and counterbore 824 of the cap 821.
  • An annular O-ring 832 is provided on the inner diameter of the piston 829. With the piston 829 properly positioned, an annular chamber 833 is formed between the back end of the piston and the counterbore 824 of the cap 821 and sealed by the O-rings 826, 827, and 832.
  • a threaded bore 433 at the back end of the cap 821 receives a hose fitting (not shown) and a small passageway 434 extends inwardly from the threaded bore to communicate the annular chamber 833 with a fluid or air source (not shown) for effecting reciprocation of the piston 829 and fin sleeve 812.
  • a second thin cylindrical retainer ring 834 is secured on the rear reduced diameter 819 of the fin sleeve 812 by screws 835 and extends rearwardly to surround the drive teeth 428 and the dowel pins 828 .
  • the rear end of the ring 834 extends a distance beyond the dowel pins 828 and is provided with a rod wiper 836.
  • the operation of the tail fin assembly 800 is best seen with reference to Figs. 33 and 34.
  • the piston 829 Under action of compressed air or fluid in the annular chamber 833 the piston 829 begins to move toward the front of the sub 801 contacting the shoulder 815 and carrying the fin sleeve 812 with it.
  • the front end of the piston 829 contacts the shoulder 815 and the drive teeth ecome disengaged from the dowel pins 828.
  • compressed air or fluid is admitted through the passage 434 from the source into the annular chamber 833.
  • the fin sleeve 812 is then free to rotate relative to the tool body.
  • the driving force of the tool hammer carries the tool including the sub 801 forward relative to the fin sleeve 812 (Fig. 34).
  • the shoulder 815 moves the piston rearwardly and the drive teeth 428 become engaged once again with the dowel pins 828 and the fin sleeve 812 becomes locked against rotational movement relative to the tool body.
  • the cycle may be selectively repeated as necessary for proper alignment of the slanted nose member and attitude adjustment of the tool.
  • Fig. 35 is a longitudinal cross sectional view of a movable tail fin assembly.
  • Fig. 36 is a vertical cross sectional view of the movable tail fin assembly of Fig. 35 taken along line 36 - 36 of Fig. 35.
  • the movable tail fin arrangement is similar to the fixed/lockable tail fins previously described with the exception that it rotates the boring tool through an inclined, anti-parallel or skewed fin arrangement. When the two fins are parallel, the soil forces acting on their faces prevents rotation of the tool housing and allows the nose member or eccentric hammer to produce a net deflective force which causes the tool to veer in a curved trajectory.
  • the movable tail fin assembly 900 comprises a cylindrical connecting sub 901 having external threads at the front end which are received within the internal threads at the rear portion of the tool body.
  • the outer rear portion of the sub 901 is reduced in diameter defining a shoulder 902 and provided with external threads 903.
  • a series of circumferentialy spaced openings 904 extend radially through the side wall of the sub 901 communicatng the interior of the tool to atmosphere.
  • a pair of opposed J-slots 905 extend longitudinally inward from the back end of the sub 901 and terminate a distance from the openings 904.
  • An annular O-ring seal 906 on the central bore 90 provides a seal on the air distribution tube 46.
  • a circular opening 908 extends transversly through the rear portion of the sub 901 and the J-slots 905.
  • annular arcuate groove 909 is formed in the interior of each circular opening 908 spaced outwardly from each side of the slots 905 and concentric with the opening 908, and a small opening 910 extends from each groove to the outer surface of the sub 901. The openings are used to fill the grooves with ball bearings 911 after which they are enclosed by threaded plugs 912.
  • a piston spool 913 is slidably received on the air distribution tube 46.
  • the piston spool 913 comprises an elongated cylindrical member having a central longitudinal bore 914 with an O-ring seal 915 near the back end to seal on the tube 46.
  • the front portion of the spool 913 is in the form of a tubular extension 916 and has a short reduced diameter 917 at the forward end.
  • the rear portion of the spool has an enlarged diameter 918 greater than the extension 916 to define a shoulder 919 therebetween.
  • An O-ring seal 920 is provided on the enlarged diameter 918.
  • a pair of radially opposed threaded bores 921 and 922 extend longitudinally through the rear portion of the spool 913 to receive hose fittings for connection to an air or fluid source (not shown).
  • a cylindrical piston 923 having a central bore 924 is slidably mounted on the circumference of the tubular extension 916.
  • a pair of radially opposed bores 925 and 926 in axial alignment with the bores 921 and 922 extend longitudinally through the piston 923 and are provided with internal threads 927 at the rear portion.
  • An O-ring seal 928 disposed in the central bore 924 provides a reciprocating seal on the tubular extension 916.
  • Another O-ring seal 929 is provided on the circumference of the piston 923.
  • a cylindrical bulkhead 930 having a central bore 931 is mounted on the forward end of the tubular extension 916.
  • a pair of radially opposed bores 932 and 933 in axial alignment with the bores 925 and 926 extend longitudinally through the bulkhead 930 and are provided with internal O-ring seals 934.
  • An O-ring seal 935, disposed in the central bore 931 provides a seal on tubular extension 916.
  • Another O-ring seal 936 is provided on the circumference of the bulkhead 930.
  • a slot 937 extends vertically through one side wall of the bulkhead at the forward end and receives a rectangular key 938 for keying the bulkhead to the back end of sub 901.
  • An actuating rod 939 having a flat rectangular front portion 940 and a longitudinally offset round tail portion 941 is carried by the piston 923.
  • the front portion of the actuating rod 939 is slidably recived in the elongated portion of the J-slot 905 and the tail portion 941 extends outwardly therefrom to be slidably received through the bulkhead bore 932 and provided with external threads at the rear end which are received on the threads 927 of the bore 925 in the piston 923.
  • the rectangular front portion 940 is provided with a transverse slot 942 which engages the protruding lug of a cup-shaped member described hereinafter.
  • An O-ring seal 948 is disposed on the circumference of the tail portion 941 to provide a seal on the piston bore 925.
  • a longer, reverse actuating rod 943 having a flat rectangular front portion 944 and a longitudinally offset round tail portion 943 is carried by the piston 923.
  • the front portion of the actuating rod 943 is slidably recived in the elongated portion of the opposing J-slot 905 and the tail portion 945 extends outwardly therefrom to be slidably received through the opposed bulkhead bore 933 and provided with external threads which are received on the threads 927 of the bore 926 in the piston 923.
  • a reduced diameter 946 extends rearwardly from the threads 927 and is slidably received within the bore 922 of the piston spool 913.
  • the rectangular front portion 944 is provided with a transverse slot 947 which engages the protruding lug of another cup-shaped member (hereinafter described).
  • An O-ring seal 948 is disposed on the circumference of the tail portion 945 to provide a seal on the piston bore 926.
  • An elongated hollow cylindrical outer sleeve 949 is slidably received on the outer periphery of the bulkhead 930, the piston 923, and the piston sleeve 913.
  • the outer sleeve 949 has interior threads 950 at the front portion, a central longitudinal bore 951 extending therefrom and terminating at a reduced bore 952 defining an annular shoulder 953 therebeteen.
  • the outer sleeve 949 is threadedly received on the threaded portion of the sub 901 with a seal 954 provided between the front end and the sub shoulder 902.
  • a pair of circular openings 955 extend transversly through the side wall of the sleeve in axial alignment with the opening 908 to receive the cup-shaped members (described hereinafter).
  • the reduced bore 952 is received on a short reduced diameter 956 of the piston spool 913 and the O-rings 920, 929, and 936 providing a seal on the central bore 951.
  • the side wall of the sleeve forms a sealed front chamber 957 between the bulkhead 930 and the piston 923.
  • a second rear chamber 958 is formed between the piston 923 and the piston sleeve 913.
  • a small passageway 959 extends inwardly from the back end of the reverse actuating rod 943 and communicates the bore 922 of the piston sleeve 913 with the front chamber 957.
  • the opposed bore 921 of the piston sleeve 913 is in communication with the rear chamber 958. It should be understood that the opposed bores 921 and 922 at the back end of the piston sleeve receive hose fittings and flexible hoses extend outwardly therefrom and to be connected to the fluid or air source for effecting reciprocation of the piston.
  • a pair of steering fins 960 and 961 each comprising a flat rectangular fin 962 secured to a cylindrical cup-shaped member 963 and 964 are rotatably received within the transverse circular openings 908 and 955.
  • Each cup-shaped member is provided with an annular O-ring seal 965 to provide a rotary seal on the interior of the opening 908, and a circumferential arcuate groove 966 in alignment with the grooves 909 to receive the ball bearings 911.
  • the tail fins are locked against outward movement, and are free to rotate about the transverse axis within the openings.
  • the opposed cylindrical ends of the cup-shaped members 963 and 964 extend inwardly to meet at the center of the sub 901.
  • An arcuate eliptical cut-away portion extends transversly across the ends of each cup-shaped member leaving a flat raised segment 967 and a dimetrically opposed protruding lug 968 which is disposed angularly relative to the longitudinal axis of the rectangular fin 962.
  • the lugs 968 are diametrically opposed and the elliptical opening surrounds the air distribution tube 46, whether the fins are rotated to a position parallel or angularly disposed relative to the longitudinal axis of the tool.
  • One lug is received in the slot 942 of the actuating rod and the opposing lug is received within the slot 947 of the reverse actuating rod.
  • Figs. 35, 37, and 38 The operation of the movable tail fin assembly is best seen with reference to Figs. 35, 37, and 38.
  • the piston 923 moves toward the back of the sub 901 carrying the actuating rods 939 and 943 with it.
  • This action causes the cup-shaped members 963 and 964 to rotate in opposite directions relative to the transverse axis.
  • the air or fluid in the rear chamber 958 has been relieved or exhausted.
  • the fins are positioned angularly relative to the longitudinal axis of the tool body.
  • the soil forces acting on their faces causes the tool housing to rotate about its longitudinal axis and the tool bores in a straight direction.
  • the front chamber 957 is pressurized to move the pistons in the opposite direction (Figs. 37 and 38).
  • the fins are positioned parallel to the longitudinal axis of the tool body. In this position, the fins prevent rotation of the tool housing and the tool bores in a curved direction as a result of the asymmetric boring force of the slanted nose member or the eccentric hammer.
  • the positioning of the fins in parallel or anti-parallel positions may be selectively changed as necessary for proper alignment and attitude adjustment of the tool.
  • Figs. 40 and 41 are longitudinal cross sections of a portion of a boring tool including an eccentric hammer arrangement.
  • An off-axis or eccentric hammer may be used in combination with the tail fin arrangements described previously.
  • a deflective side force results. This force causes the boring tool to deviate in the direction opposite to the impact point as depicted in Fig. 40.
  • Orientation may be controlled by the external rotation of the tool body with tail fins. The only internal modification required is the replacement of the existing hammer.
  • Fig. 40 shows the front portion details of a boring tool 23 which was shown previously in schematic form in Fig. 8 with a movable tail fin system in combination with an eccentric hammer 24.
  • the rear portion of the hammer 24 in not shown, with the understanding that the rear portion of the hammer 24 would be the same as the concentric hammer 37 shown in Fig 9B.
  • the rear portion of the tool is not shown in Figs. 40 or 41 since the eccentric hammer may be used in combination with either the fixed/lockable fin systems or the movable fin systems and with or without the slanted nose member previously shown and described.
  • the boring tool 23 comprises an elongated hollow cylindrical outer housing or body 25.
  • the outer front end of the body 25 tapers inwardly forming a conical portion 29.
  • the internal diameter of the body 23 tapers inwardly near the front end forming a conical surface 30 which terminates in a reduced diameter 31 extending longitudinally inward from the front end.
  • the rear end of the body is provided with internal threads for receiving a tall fin assembly previously described.
  • An anvil 33 having a conical back portion 34 and an elongated cylindrical front portion 35 is contained within the front end of the body 23.
  • the conical back portion 34 of the anvil 33 forms and interference fit on the conical surface 30 of the body 23, and the elongated cylindrical portion 35 extends outwardly a distance beyond the front end of the body.
  • a flat surface 36 at the back end of anvil 33 receives the impact of eccentric reciprocating hammer 24.
  • a slanted nose member 18 having a cylindrical back portion 52 and a central cylindrical bore 53 extending inwardly therefrom may be secured on the cylindrical portion 35 of the anvil 33 (Fig. 40).
  • a slot 54 through the sidewall of the cylindrical portion 51 extends longitudinally substantially the length of the central bore 53 and a transverse slot 55 extends radially from the bore 53 to the outer circumference of the cylindrical portion, providing flexibility to the cylindrical portion for clamping the nose member to the anvil.
  • Longitudinally spaced holes in alignment with threaded bores 58 on the opposing side of the slot 54 receive screws 59 which secure the nose member 18 to the anvil 33.
  • the sidewall of the nose member 18 extends forward from the cylindrical portion 52 and one side is milled to form a flat inclined surface 60.
  • the eccentric hammer 24 is an elongated cylindrical member slidably received within the internal diameter 38 of the body 23. A substantial portion of the outer diameter of the hammer 24 is smaller in diameter than the internal diameter 38 of the body, forming an annular cavity 39 therebetween.
  • the front portion of the hammer is constructed in a manner to offset the center of gravity of the hammer with respect to its longitudinal axis. As shown in Fig. 40, the side wall of the hammer is provided with a longitudinal slot 970 which places the center of mass eccentric to the longitudinal axis and the front surface 43 of the front end of the hammer 24 is shaped to provide an impact centrally on the flat surface 36 of the anvil 33.
  • Fig. 40 the side wall of the hammer is provided with a longitudinal slot 970 which places the center of mass eccentric to the longitudinal axis and the front surface 43 of the front end of the hammer 24 is shaped to provide an impact centrally on the flat surface 36 of the anvil 33.
  • the side wall of the hammer 24a is provided with a longitudinal slot 970 and the front surface 43a is radially offset from the longitudinal axis to place the center of mass eccentric to the longitudinal axis and thereby deliver an eccentric impact force on the anvil.
  • a series of longitudinal circumferentially spaced slots 972 are provided on the outer surface of the front of the hammer to allow passage of air or fluid from the front end to the reduced diameter portion.
  • a key or pin 26 is secured through the side wall of the body 25 to extend radially inward and be received within the slot 970 to maintain the larger mass of the hammer on one side of the longitudinal axis of the tool.
  • a relatively shorter portion 40 at the back end of the hammer 37 is of larger diameter to provide a sliding fit against the interior diameter 38 of the body.
  • a central cavity 41 extends longitudinally inward a distance from the back end of the hammer 37.
  • a cylindrical bushing 42 is slidably disposed within the hammer cavity 41, the circumference of which provides a sliding fit against the inner surface of the central cavity 41.
  • Air passages 44 are provided through the sidewall of the hammer 37 inwardly adjacent the shorter rear portion 40 to communicate the central cavity 41 with the annular cavity 39.
  • An air distribution tube 45 extends centrally through the bushing 42 and its back end 46 extends outwardly of the body 28 and is connected by fittings 47 to a flexible hose 48.
  • the air distribution tube 45 is in permanent communication with a compressed air source (not shown).
  • the arrangement of the passages 44 and the bushing 42 is such that, during reciprocation of the hammer 37, the air distribution tube 45 alternately communicates via the passages 44, the annular cavity 39 with either the central cavity 41 or atmosphere at regular intervals.
  • a cylindrical stop member 49 is secured within the inner diameter of the body 28 near the back end and is provided with a series of longitudinally extending, circumferentially spaced passageways 50 for communicating the interior of the body 28 with atmosphere.
  • the air distribution tube 45 is centrally disposed within the stop member 49.
  • the hammer 24 moves toward the front of the body 25.
  • the hammer imparts an impact on the flat surface 36 of the anvil 33.
  • compressed air is admitted through the passages 44 from the central cavity 41 into the annular cavity 39. Since the effective area of the hammer including the larger diameter rear portion 40 is greater than the effective area of the central cavity 41, the hammer starts moving in the opposite direction. During this movement, the bushing 42 closes the passages 44, thereby interrupting the admission of compressed air into annular cavity 41.
  • the hammer 37 continues its movement due to the expansion of the the air in the annular cavity 39 until the passages 44 are displaced beyond the ends of the bushing 42, and the annular cavity is placed to communication to atmosphere through the holes 50 in the stop member 49. In this position, the air is exhausted from the annular cavity 39 through the passages 44 now above the trailing edge of the bushing 42 and the holes 50 in the stop member 49. Then the cycle is repeated.
  • the eccentric hammer can be used for straight boring by averaging the defective side force over 360 degrees by rotating the outer body.
  • the fins provide orientation capabilities as previously described and are brought into an unlocked rotating or straight parallel alignment position when executing turns. Straight boring of the tool is accomplished by activating the fins to a spin inducing position counteracting the tendency of the eccentric hammer to turn the tool.

Landscapes

  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Electromagnetism (AREA)
  • Remote Sensing (AREA)
  • Geophysics (AREA)
  • Mechanical Engineering (AREA)
  • Earth Drilling (AREA)
  • Drilling Tools (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Excavating Of Shafts Or Tunnels (AREA)
  • Geophysics And Detection Of Objects (AREA)
  • Drilling And Boring (AREA)

Claims (27)

  1. Steuerbares Schlagbohrwerkzeug mit einer asymmetrischen Bohrkraft zum Bohren von Löchern in den Erdboden, wobei die Vorrichtung ein zylinderförmiges Gehäuse (19) mit einem spitz auslaufenden vorderen Ende (18), eine erste Vorrichtung am vorderen Ende zum Anlegen einer Bohrkraft an den Erdboden, eine zweite Vorrichtung im Gehäuse (19) zum Anlegen einer Schlagkraft an die Bohrvorrichtung, wobei die erste und die zweite Vorrichtung zum Anlegen der asymmetrischen Bohrkraft zusammenwirken können, und mindestens eine Steuerflosse (17) mit einer außen am hinteren Ende des Gehäuses (19) angebrachten Flossenanlage (62) aufweist, die eine erste Position hat, die eine nicht-rotierende Bewegung des Gehäuses (19) durch den Erdboden zuläßt, sowie eine zweite Position, in der sich das Gehäuse (19) während des Bewegens durch den Erdboden um seine Längsachse dreht, dadurch gekennzeichnet, daß eine Einrichtung (16) die Flossenanlage (62) zwischen der ersten und der zweiten Position hin- und herbewegt, wobei das Gehäuse (19) eine kurvenförmige Bahn durch den Erdboden einschlägt, wenn das Rotieren verhindert wird, und eine im wesentlichen gerade Bahn, wenn es sich dreht.
  2. Steuerbares Schlagbohrwerkzeug nach Anspruch 1, dadurch gekennzeichnet, daß das Gehäuse hohl ist, die erste Vorrichtung einen Amboß (33) mit einer Auftreffläche (36) innerhalb des Gehäuses (19) und eine Bohrfläche außerhalb des Gehäuses umfaßt, und die zweite Vorrichtung einen im Gehäuse (19) befestigten, sich hin- und herbewegenden Hammer (24) zum Anlegen einer Schlagkraft an die Auftrefffläche des Amboß umfaßt.
  3. Steuerbares Schlagbohrwerkzeug nach Anspruch 2, dadurch gekennzeichnet, daß die Bohrfläche des Amboß eine zylindrische Nase (18) mit einer sich von der Spitze im spitzen Winkel zu ihr erstreckenden Seitenfläche (60) aufweist.
  4. Steuerbares Schlagbohrwerkzeug nach Anspruch 3, dadurch gekennzeichnet, daß die äußere Bohrfläche des Amboß einen zylinderförmigen Stock (28) aufweist und die Nase (18) abnehmbar auf ihm befestigt ist.
  5. Steuerbares Schlagbohrwerkzeug nach Anspruch 2, dadurch gekennzeichnet, daß der Hammer (24) einen asymmetrischen Stirnbereich zum Anlegen der asymmetrischen Erdbohrkraft aufweist.
  6. Steuerbares Schlagbohrwerkzeug nach Anspruch 2, dadurch gekennzeichnet, daß der Hammer (24) einen zylinderförmigen Körper (28) und einen zur Amboßstirnseite asymmetrischen Stirnbereich (29) aufweist, so daß ein Hammerschlag an die Umgebung abgegeben wird, um die asymmetrische Erdbohrkraft anzulegen.
  7. Steuerbares Schlagbohrwerkzeug nach einem der Ansprüche 3 bis 6, dadurch gekennzeichnet, daß das zylinderförmige Gehäuse (19) ein spitz auslaufendes vorderes Ende aufweist, wobei der Amboß (33) und die Nase (18) im Gehäuse in nicht drehbarer Position fest angebracht sind und die Vorrichtung so in ihrer Bewegung durch den Erdboden aufgrund der Einwirkung der winkligen Seitenfläche auf den Boden von einer geraden Bahn abweicht, wobei mindestens eine Steuerflosse (17) am hinteren Ende des Gehäuses (19) außen angebracht ist und eine erste Position hat, die eine nicht-rotierende Bewegung durch den Erdboden zuläßt und eine zweite Position, in der sich das Gehäuse (19) beim Bewegen durch den Erdboden um seine Längsachse dreht, und eine Einrichtung (16) zum Bewegen mindestens einer Flosse zwischen der ersten und der zweiten Position.
  8. Steuerbares Schlagbohrwerkzeug nach Anspruch 7, dadurch gekennzeichnet, daß eine drehbare Hülse (91) am hinteren Ende des Gehäuses (19) angebracht ist, wobei eine Vielzahl von Flossen (17) auf der Außenseite der drehbaren Hülse (63) zueinander beabstandet und winklig zu ihr befestigt sind, die Hülse (91) und die Flossen (17) die Flossenanlage (62) und eine Vorrichtung umfassen, die mit mindestens einem Element der Flossenanlage (62) zusammenwirken kann, um eine Position einzunehmen, in der sich die Flossenanlage beim Bewegen durch den Erdboden (62) frei auf dem Gehäuse (19) dreht, und eine andere Position, in der sie zum Gehäuse (19) unbeweglich ist, so daß sich das Gehäuse (19) beim Bewegen durch den Erdboden dreht, wobei die Bohrvorrichtungen so betätigt werden können, daß sie gerade bohren, wenn sich die Flossenanlage (62) nicht bewegt, und kurvenförmig, wenn sich die Flossenanlage (62) dreht.
  9. Steuerbares Schlagbohrwerkzeug nach Anspruch 8, dadurch gekennzeichnet, daß das hintere Ende des Gehäuses (19) eine Trägerhülse (63) umfaßt, wobei die drehbare Hülse (91) drehbar auf der Trägerhülse (63) gelagert ist, sowie eine Kupplung, die die Hülse (91) und die Trägerhülse (63) funktionsfähig miteinander verbindet, und die eine erste, ausgekuppelte Position hat, in der sich die drehbare Hülse gegennüber der Trägerhülse dreht, und eine zweite, eingekuppelte Position, in der sich die drehbare Hülse (91) und die Trägerhülse (63) zusammen drehen, und eine Vorrichtung zum Ein- und Auskuppeln.
  10. Steuerbares Schlagbohrwerkzeug nach Anspruch 8, dadurch gekennzeichnet, daß das hintere Ende (28) des Gehäuses (19) eine Trägerhülse (63) umfaßt, wobei die drehbare Hülse (91) auf der Trägerhülse (63) drehbar und in fester Längsposition aufliegt, sowie eine Kupplung mit einem ersten, funktionsfähig auf der drehbaren Hülse (91) gelagerten und zu ihr beweglichen Teil (86), einem zweiten, funktionsfähig auf der Trägerhülse (63) angebrachten Teil und einem dritten, mit dem ersten und zweiten Teil ein- und auskuppelbaren Teil, wobei der dritte Teil der Kupplung in einer ersten Position aus dem ersten und zweiten Teil ausgekuppelt werden kann, so daß sich die drehbare Hülse (91) zur Trägerhülse (63) drehen kann, und in einer zweiten Position mit dem ersten und zweiten Teil eingekuppelt wird, so daß sich die drehbare Hülse (91) und die Trägerhülse (63) zusammen drehen, und eine Vorrichtung zum Bewegen des dritten Teiles längs zum ersten und zweiten Teil zwischen ein- und ausgekuppelter Position.
  11. Steuerbares Schlagbohrwerkzeug nach Anspruch 10, dadurch gekennzeichnet, daß der dritte Teil eine Hülse (77) umfaßt, die zur Trägerhülse (63) und innerhalb der drehbaren Hülse (91) verschiebbar ist und eine Mitnehmerfläche aufweist, die mit der drehbaren Hülse (91) und der Trägerhülse (63) zur Gewährleistung der gemeinsamen Bewegung ineinandergreift.
  12. Steuerbares Schlagbohrwerkzeug nach Anspruch 11, dadurch gekennzeichnet, daß die verschiebbare Hülse (77) zwischen ein- und ausgekuppelter Position zur drehbaren Hülse (91) und zur Trägerhülse (63) hin- und herbewegt werden kann.
  13. Steuerbares Schlagbohrwerkzeug nach Anspruch 11, dadurch gekennzeichnet, daß die verschiebbare Hülse (77) drehbar auf der Trägerhülse (63) angebracht ist, wobei die drehbare Hülse (91) und die verschiebbare Hülse (77) mindestens eine Vertiefung (83) auf der einen und einen vorstehenden Teil auf der anderen aufweisen, die in eingekuppelter Position ineinandergreifen, damit sich die drehbare Hülse (91) und die Trägerhülse (63) zusammen bewegen, und die verschiebbare Hülse (77) zwischen ein- und ausgekuppelter Position zur drehbaren Hülse (91) bewegt werden kann.
  14. Steuerbares Schlagbohrwerkzeug nach Anspruch 8, dadurch gekennzeichnet, daß das hintere Ende (28) des Gehäuses (19) eine Trägerhülse (63) umfaßt, wobei die drehbare Hülse (91) drehbar auf der Trägerhülse (63) aufliegt und sich in vorher festgelegtem Umfang in Längsrichtung bewegen kann, sowie eine Kupplung mit einem funktionsfähig auf der drehbaren Hülse (91) befestigten und mit ihm beweglichen Teil (86) und einem anderen, funktionsfähig auf der Trägerhülse (63) befestigten Teil (101), wobei die Kupplungsteile eine erste Position aufweisen, in der sich die drehbare Hülse (91) zur Trägerhülse (63) dreht, und eine zweite Position, in der sich die drehbare Hülse (91) und die Trägerhülse (63) zusammen drehen, sowie Vorrichtungen zum Bewegen der drehbaren Hülse (91) längs zur Trägerhülse (63), um die Kupplungsteile ein- und auszukuppeln.
  15. Steuerbares Schlagbohrwerkzeug nach Anspruch 14, dadurch gekennzeichnet, daß die Kupplungsteile Mitnehmerzähne (86) und (101) auf der drehbaren Hülse (91) und auf der Trägerhülse (63) sowie Vorrichtungen zum Ineinandergreifen und Freigeben der Mitnehmerzähne.
  16. Steuerbares Schlagbohrwerkzeug nach Anspruch 15, dadurch gekennzeichnet, daß die Mitnehmerzähne mit den Stirnseiten greifen.
  17. Steuerbares Schlagbohrwerkzeug nach Anspruch 15, bei der sich die Mitnehmerzähne (86) und (101) jeweils auf der Innenseite der drehbaren Hülse (91) und der Außenseite der Trägerhülse (63) befinden, und Vorrichtungen zum Ineinandergreifen von mindestens einer Hülse mit den Zähnen.
  18. Steuerbares Schlagbohrwerkzeug nach Anspruch 14, dadurch gekennzeichnet, daß die Kupplungsteile Mitnehmerzähne (86) auf einer der Hülsen und einen Mitnehmer auf der anderen Hülse umfasen, die ineinandergreifen und sich voneinander lösen lassen, sowie Vorrichtungen zum Ineinandergreifen und Freigeben der Mitnehmerzähne und des Mitnehmers.
  19. Steuerbares Schlagbohrwerkzeug nach Anspruch 14, dadurch gekennzeichnet, daß die Kupplungsteile eine Mitnehmernut (78) auf einer Hülse (63) und einen Mitnehmer (79) auf der anderen Hülse (91) umfassen, die ineinandergreifen und sich voneinander lösen lassen, sowie Vorrichtungen zum Ineinandergreifen und Freigeben der Mitnehmernut (78) und des Mitnehmers (79).
  20. Steuerbares Schlagbohrwerkzeug nach Anspruch 18 oder 19, dadurch gekennzeichnet, daß der Mitnehmer einen Mitnehmerstift (79) umfaßt.
  21. Steuerbares Schlagbohrwerkzeug nach Anspruch 19, dadurch gekennzeichnet, daß der Mitnehmer eine Mitnehmerfeder umfaßt.
  22. Steuerbares Schlagbohrwerkzeug nach Anspruch 7, dadurch gekennzeichnet, daß eine befestigte Trägerhülse auf dem hinteren Ende (28) des Gehäuses (19) aufliegt, und eine Vielzahl von Flossen (17) drehbar und zueinander beabstandet auf der Hülse (91) befestigt sind, wobei die Flossen (17) eine erste Position, parallel zur Längsachse des Gehäuses (19), und eine zweite Position, spitzwinklig zur Längsachse des Gehäuses (19), haben, sowie mit den Flossen (17) zusammenwirkende Vorrichtungen aufweisen, die die Flossen in die erste oder zweite Position bringen, wobei die Bohrvorrichtung in der zweiten Position der Flossen (17) gerade bohrt und in der ersten kurvenförmig.
  23. Steuerbares Schlagbohrwerkzeug nach Anspruch 22, dadurch gekennzeichnet, daß das hintere Ende (28) des Gehäuses (19) eine Trägerhülse (63) umfaßt, wobei die befestigte Hülse auf der Trägerhülse (63) aufliegt, sowie in den Zwischenraum zwischen Trägerhülse (63) und befestigter Hülse ragende Haltestifte mit auf ihnen angebrachten Betätigungselementen für jede Flosse, sowie eine auf der Trägerhülse (63) verschiebbare Bedieneinrichtung, die mit den Flossenbetätigungselementen ineinandergreifen kann, und Vorrichtungen zum Bewegen der Bedieneinrichtung längs zum Flossenbetätigungelement, um so die Flossen parallel bzw. winklig zu positionieren.
  24. Steuerbares Schlagbohrwerkzeug nach Anspruch 23, dadurch gekennzeichnet, daß die Flossenbetätigungseinrichtung ein auf jeder Stützflosse (17) befestigtes Drehelement (91) umfaßt, wobei die Betätigungseinrichtung eine verschiebbare Hülse (77) umfaßt, wobei das Drehelement zur Flossenbetätigung (91) und die Mitnehmerhülse (63) eine Vertiefung (78) in der einen und einen hervorstehenden Mitnehmer (79) auf der anderen aufweist, die so zusammenwirken können, daß sich beim Verschieben der verschiebbaren Hülse (77) alle Flossen (17) drehen.
  25. Steuerbares Schlagbohrwerkzeug nach einem der Ansprüche 1, 7, 16, 17 oder 18, dadurch gekennzeichnet, daß das Werkzeug ein Hohlzylindergehäuse (19) mit einem spitz auslaufendem vorderen Ende (18), einen im Gehäuse (19) angebrachten Amboß (33), eine sich längs daraus herausragende, mit Schlagbohrkraft betriebene Spitze, einen im Gehäuse (19) zum Hin- und Wegbewegen zum und vom Amboß (33) angeordneten Hammer (24), einen Anschluß des Hammers (24) an eine äußere Stromquelle, eine Vielzahl von außen am hinteren Ende des Gehäuses (19) befestigten Führungsflossen (17) mit einer ersten Position, die eine nicht-rotierende Bewegung durch den Erdboden zuläßt, und einer zweiten Position, in der sich das Gehäuse (19) beim Bewegen durch den Erdboden um seine Längsachse dreht, und von außen betätigte Vorrichtungen, zum Bewegen der Flossen (17) zwischen ersten und zweiten Position umfaßt.
  26. Steuerbares Schlagbohrwerkzeug nach einem der Ansprüche 2 - 25, dadurch gekennzeichnet, daß der Hammer (24) hydraulisch angetrieben wird und das Gehäuse (19) eine Anschlußleitung (45) zu einer Quelle mit Antriebsflüssigkeit aufweist.
  27. Steuerbares Schlagbohrwerkzeug nach einem der Ansprüche 1 - 7, dadurch gekennzeichnet, daß eine Vielzahl von Flossen (17) vorhanden ist.
EP86302534A 1985-04-05 1986-04-04 Führungs- und Steuerungssystem für Schlagbohrwerkzeuge Expired - Lifetime EP0202013B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT86302534T ATE86355T1 (de) 1985-04-05 1986-04-04 Fuehrungs- und steuerungssystem fuer schlagbohrwerkzeuge.
EP90122531A EP0428181B1 (de) 1985-04-05 1986-04-04 Schlagwerkzeug zum Bohren von Löchern in den Boden
EP90122530A EP0428180B1 (de) 1985-04-05 1986-04-04 Kontrollsystem zum Leiten von Bohrwerkzeugen und Messsystem, diese zu lokalisieren

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US720582 1985-04-05
US06/720,582 US4632191A (en) 1985-04-05 1985-04-05 Steering system for percussion boring tools
US722807 1985-04-12
US06/722,807 US4646277A (en) 1985-04-12 1985-04-12 Control for guiding a boring tool
US723792 1985-04-16
US06/723,792 US4621698A (en) 1985-04-16 1985-04-16 Percussion boring tool

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP90122530.0 Division-Into 1990-11-26
EP90122531.8 Division-Into 1990-11-26

Publications (3)

Publication Number Publication Date
EP0202013A2 EP0202013A2 (de) 1986-11-20
EP0202013A3 EP0202013A3 (en) 1988-08-03
EP0202013B1 true EP0202013B1 (de) 1993-03-03

Family

ID=27419012

Family Applications (3)

Application Number Title Priority Date Filing Date
EP90122530A Expired - Lifetime EP0428180B1 (de) 1985-04-05 1986-04-04 Kontrollsystem zum Leiten von Bohrwerkzeugen und Messsystem, diese zu lokalisieren
EP90122531A Expired - Lifetime EP0428181B1 (de) 1985-04-05 1986-04-04 Schlagwerkzeug zum Bohren von Löchern in den Boden
EP86302534A Expired - Lifetime EP0202013B1 (de) 1985-04-05 1986-04-04 Führungs- und Steuerungssystem für Schlagbohrwerkzeuge

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP90122530A Expired - Lifetime EP0428180B1 (de) 1985-04-05 1986-04-04 Kontrollsystem zum Leiten von Bohrwerkzeugen und Messsystem, diese zu lokalisieren
EP90122531A Expired - Lifetime EP0428181B1 (de) 1985-04-05 1986-04-04 Schlagwerkzeug zum Bohren von Löchern in den Boden

Country Status (5)

Country Link
EP (3) EP0428180B1 (de)
AT (3) ATE86355T1 (de)
AU (1) AU589615B2 (de)
CA (2) CA1255651A (de)
DE (3) DE3687855T2 (de)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1001218A3 (nl) * 1987-11-12 1989-08-22 Smet Marc Jozef Maria Detectie-inrichting voor een boorkop.
GB2215257B (en) * 1988-02-10 1992-03-04 Ronald Albert William Clarke Apparatus for reflex-percussive cutting of concrete etc.
US4878547A (en) * 1988-10-28 1989-11-07 Ingersoll-Rand Company Rock drilling apparatus
JP2819042B2 (ja) * 1990-03-08 1998-10-30 株式会社小松製作所 地中掘削機の位置検出装置
DE4438934C1 (de) * 1994-10-31 1995-11-16 Tracto Technik Ortungsvorrichtung für Rammbohrgeräte
WO1996018118A1 (en) * 1994-12-08 1996-06-13 Noranda Inc. Method for real time location of deep boreholes while drilling
US6411094B1 (en) 1997-12-30 2002-06-25 The Charles Machine Works, Inc. System and method for determining orientation to an underground object
GB2341754B (en) * 1998-09-19 2002-07-03 Cryoton Drill string telemetry
DE19859367C2 (de) * 1998-12-22 2003-03-20 Tracto Technik Lenkkopf-Rammbohrgerät
GB9903256D0 (en) 1999-02-12 1999-04-07 Halco Drilling International L Directional drilling apparatus
GB2382143B (en) * 2000-05-01 2004-05-26 Schlumberger Holdings A method for telemetering data between wellbores
AU2001273549A1 (en) * 2000-07-18 2002-01-30 Geoff D. Koch Remote control for a drilling machine
US6871712B2 (en) 2001-07-18 2005-03-29 The Charles Machine Works, Inc. Remote control for a drilling machine
US6607045B2 (en) 2001-10-10 2003-08-19 Donald Beyerl Steering apparatus
CN109209221B (zh) * 2018-11-14 2024-02-09 中国铁建重工集团股份有限公司 一种潜孔锤设备及其冲击导向系统
CN109372424B (zh) * 2018-12-13 2023-09-29 长江大学 一种连续油管用复合冲击提速钻具
CN112443274A (zh) * 2019-08-27 2021-03-05 永城煤电控股集团有限公司 一种煤仓电缆孔的施工方法
US11674354B2 (en) 2020-11-03 2023-06-13 The Charles Machine Works, Inc. Piercing tool aiming device
CN113700433B (zh) * 2021-09-09 2023-05-12 西南石油大学 一种自发电风压电磁联合冲击自转式空气锤及使用方法
CN113756788B (zh) * 2021-10-18 2022-08-02 中国地质大学（北京） 一种机械式随钻井斜测量仪

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3375885A (en) * 1965-09-13 1968-04-02 California Inst Res Found Burrowing apparatus
US3525405A (en) * 1968-06-17 1970-08-25 Bell Telephone Labor Inc Guided burrowing device
US3529682A (en) * 1968-10-03 1970-09-22 Bell Telephone Labor Inc Location detection and guidance systems for burrowing device
US3630295A (en) * 1969-12-10 1971-12-28 Bell Telephone Labor Inc Steering apparatus for soil-burrowing mole
US3656161A (en) * 1969-12-31 1972-04-11 Bell Telephone Labor Inc Maintaining a circularly polarized magnetic field at a moving point
US3731752A (en) * 1971-06-25 1973-05-08 Kalium Chemicals Ltd Magnetic detection and magnetometer system therefor
US3712391A (en) * 1971-06-28 1973-01-23 Bell Telephone Labor Inc Mole guidance system
US3794128A (en) * 1972-11-29 1974-02-26 Bell Telephone Labor Inc Subterranean penetrator steering system utilizing fixed and rotatable fins
US3888319A (en) * 1973-11-26 1975-06-10 Continental Oil Co Control system for a drilling apparatus
US3952813A (en) * 1975-02-07 1976-04-27 Nikolai Prokhorovich Chepurnoi Percussive device for driving holes in soil
DE2911419C2 (de) * 1979-03-23 1984-03-01 Wolfgang Dr.-Ing. 7500 Karlsruhe Ständer Vorrichtung zum richtungsgesteuerten Herstellen von Bohrlöchern in Lockergestein
DE3027990A1 (de) * 1980-07-24 1982-03-04 Paul 5940 Lennestadt Schmidt Selbstgetriebenes rammbohrgeraet
CA1111831A (en) * 1981-03-25 1981-11-03 Arthur Adam Broaching head
US4396073A (en) * 1981-09-18 1983-08-02 Electric Power Research Institute, Inc. Underground boring apparatus with controlled steering capabilities

Also Published As

Publication number Publication date
EP0202013A3 (en) 1988-08-03
DE3650461T2 (de) 1996-05-15
CA1255651A (en) 1989-06-13
DE3650026D1 (de) 1994-09-15
EP0202013A2 (de) 1986-11-20
ATE132226T1 (de) 1996-01-15
EP0428180A1 (de) 1991-05-22
CA1274817A (en) 1990-10-02
EP0428180B1 (de) 1995-12-27
EP0428181A1 (de) 1991-05-22
DE3650461D1 (de) 1996-02-08
DE3687855D1 (de) 1993-04-08
DE3687855T2 (de) 1993-07-01
ATE109866T1 (de) 1994-08-15
ATE86355T1 (de) 1993-03-15
AU5565286A (en) 1986-10-09
AU589615B2 (en) 1989-10-19
EP0428181B1 (de) 1994-08-10
DE3650026T2 (de) 1994-12-01

Similar Documents

Publication Publication Date Title
US4632191A (en) Steering system for percussion boring tools
US4621698A (en) Percussion boring tool
EP0202013B1 (de) Führungs- und Steuerungssystem für Schlagbohrwerkzeuge
US4858704A (en) Guided earth boring tool
USRE44427E1 (en) Apparatus for directional boring under mixed conditions
EP0322170B1 (de) Rammbohrgerät mit Kontrollventil
EP0391669B1 (de) Richtungsstangenstosser
US5449046A (en) Earth boring tool with continuous rotation impulsed steering
US5803187A (en) Rotary-percussion drill apparatus and method
US6755593B2 (en) Pipe replacement method and rotary impact mechanism for pipe bursting
US4852669A (en) Directional downhole drill apparatus
US6371223B2 (en) Drill head for directional boring
EP3228809B1 (de) Lenkverbindung für ein lenkbares bohrsystem
US6516902B1 (en) Directional drilling system
CA2147431A1 (en) Self-propelled earth drilling hammer-bit assembly
WO2017174488A1 (en) Magnetic propulsion system and/or counter hold for a drilling system
JP2616933B2 (ja) 土地穴あけ用工具と穴あけ方法
CA2201058A1 (en) A method and system for steering and guiding a drill
CA2036528A1 (en) Steering mechanism for a subsoil boring apparatus
WO2017174486A1 (en) Counter hold system for a drilling system
RU2215110C2 (ru) Буровой комплекс для прокладки коммуникаций
Howell Impact moling
WO2017174485A1 (en) Protection sleeve for a drilling system
Kramer et al. Steerable Horizontal Boring

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

RIN1 Information on inventor provided before grant (corrected)

Inventor name: ENK, JOSEPH O.

Inventor name: PITTARD, GERARD T.

Inventor name: BRIDGES, JACK E.

Inventor name: MCDONALD, WILLIAM J.

Inventor name: COHEN, JOHN H.

Inventor name: GIVLER, GREGORY C.

Inventor name: MAURER, WILLIAM C.

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19890127

17Q First examination report despatched

Effective date: 19900216

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 19930303

Ref country code: SE

Effective date: 19930303

REF Corresponds to:

Ref document number: 86355

Country of ref document: AT

Date of ref document: 19930315

Kind code of ref document: T

XX Miscellaneous (additional remarks)

Free format text: TEILANMELDUNG 90122530.0 EINGEREICHT AM 04/04/86.

REF Corresponds to:

Ref document number: 3687855

Country of ref document: DE

Date of ref document: 19930408

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19930430

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19960319

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19960321

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19960401

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19960409

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19960416

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19960425

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19960430

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19970404

Ref country code: AT

Effective date: 19970404

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19970430

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19970430

Ref country code: BE

Effective date: 19970430

BERE Be: lapsed

Owner name: GAS RESEARCH INSTITUTE

Effective date: 19970430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19971101

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19970404

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19971231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980101

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19971101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST