US3387671A - Percussion tool - Google Patents

Percussion tool Download PDF

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Publication number
US3387671A
US3387671A US496373A US49637365A US3387671A US 3387671 A US3387671 A US 3387671A US 496373 A US496373 A US 496373A US 49637365 A US49637365 A US 49637365A US 3387671 A US3387671 A US 3387671A
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Prior art keywords
piston
valve
anvil
casing
seat
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US496373A
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English (en)
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Samuel L Collier
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Mission Manufacturing Co
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Mission Manufacturing Co
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Priority to BE735814D priority patent/BE735814A/xx
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers

Definitions

  • a downhole type of percussion drilling tool particularly adapted for operation by the pumped drilling mud or other pressured liquid, including a reciprocating differential piston having a single, double-seating valve between the downstream face of the piston and the abutting anvil face.
  • This invention relates to percussion motors for operating rock drills particularly of the downhole type and utilizing either liquid, such as drilling mud, or gaseous motivating uid.
  • an object or the present invention is to provide a novel percussion drill of the downhole type which is adapted for operation by a liquid, such as the usual drilling mud used for flushing out the debris, lubrieating the bit, sealing the bore wall, and preventing blowouts.
  • a liquid such as the usual drilling mud used for flushing out the debris, lubrieating the bit, sealing the bore wall, and preventing blowouts.
  • Another object is to provide a percussion drill of the above type in which surge or shock pressures are minimized.
  • Another object is to provide a percussion drill which is adapted to utilize motivating uids of substantially varying pressures and volumes.
  • Another object is to provide a percussion drill of the above type which can utilize either liquid or gaseous motivating fluids.
  • Still another object is to provide a percussion drill the use of which is accompanied by substantial continuity in the upward ow of the ambient drill uid.
  • FIG. 1 is a vertical transverse section through a preferred form of the novel percussion drill, just before irnpact;
  • FIG. 2 is a partial vertical transverse section as in FlG. l, but showing the valves just after impact;
  • FlG. 3 is a vertical transverse section illustrating a modification of the piston valve seat design
  • FIG. 4 is a similar section illustrating a modified valve design
  • FIG. 5 is a similar view illustrating another modification
  • FIG. 6 is a detail vertical transverse section illustrating a modification in the bumper design
  • FIG. 7 is an enlarged vertical central section showing another modified valve arrangement
  • FIG. 8 is a view similar to FIG. 7 but showing the valve reversed
  • FIG. 9 is a broken section on line 9-9 of FIG. 7;
  • FIGS. 10-14 inclusive are partial vertical transverse sectional views in different operative positions and showing another modied valve.
  • FIGS. 15 and 16 are similar views of still another valve modilication in different positions.
  • the novel percussion drill is constructed, in general, of a hollow casing or cylinder which is interposed between the drill bit and drill collars usually provided at the lower end of the tubular drill string which is suspended from the rotary rig into the Well.
  • An anvil is telescopingly and slidably received in the forward (lower) part of the casing, and a hollow piston of differential design is Slidable in the casing above the anvil.
  • the usual exhaust duct extends through the anvil and the bit.
  • a novel, double-acting check valve which may take various forms, is received between valve seats provided on the adjacent extremities of the anvil exhaust duct and the passage through the piston and is provided with means which, during normal operation, urges the valve rearwardly against the piston in a manner to resist access of the working fluid to the forward working chamber below the piston so that the working fluid will drive the piston downwardly.
  • the valve is driven forwardly by inertia and the force of the motivating uid so as to open the piston valve seat and close the adjacent Valve seat on the anvil exhaust duct. This exposes the lower surface of the piston, which is greater in area than the upper surface of the piston, to the working uid so as to drive the piston rearwardly.
  • the valve is unseated from the anvil valve seat, either mechanically or hydraulically, and reseated against the piston valve seat, thus initiating another cycle of piston movement.
  • FIGS. 1 and 2 there are shown the lower extremity 8 of a drill string to which is threadedly secured an adapter sub 9 to which is, in turn, threadedly secured a generally cylindrical, top piston case or back head member 10.
  • a cylindrical bumper member 11, having an external Y collar 12, is supported from member 10, as by means of longitudinal ribs 13, so that drill motivating uid can pass downwardly around as well as through the bumper.
  • Cylindrical motor casing 16 is threadedly secured at its rear end to the lower portion of top piston case member 10 and, at its forward extremity, is threadedly secured to driver subnut 17 which, during normal operation, rests upon a shoulder 18 of anvil 19.
  • the anvil shown is threadedly secured to a separate percussion bit 20 but may be formed integrally with the bit.
  • a longitudinal exhaust duct or passage 21 extends through anvil 19 in line with and continuation of exhaust duct extension 22 in the bit.
  • the anvil and casing are provided with externalsplines 23 in which are received roller bearings 24, secured in position by driver subnut 17, for permitting longitudinal movement of the anvil with respect to the casing, While enforcing joint rotation of the casing and the anvil.
  • a hollow, differential hammer piston 26 Slidable Within casing 16 above the anvil and extending into top piston case member 10 is a hollow, differential hammer piston 26 having an upper portion 27 provided with a sealing ring 28 vwhich is slidably received in member 10.
  • the piston also includes a diametrically larger lower portion 29 having lubricant grooves 30 and a sealing ring 30a slidably received in main casing 16.
  • the forwardly-facing area of piston 26 is about twice the rearwardly-facing area thereof.
  • Internal passage 31 in the piston is aligned with internal passage 32 of rbumper 11 and exhaust duct 21 in the anvil.
  • the clearance space 33 in casing 16 between the piston 26 and member 10 is vented by means of passages 34.
  • Vents 34 are of adequate capacity with respect to the displacement of rear piston part 27 in space 33 that the ambient well duid will not be pumped into this space during operation of the tool. In other words, such displacement is less than the volume of vents 34. Thus, the parting line between the fluid charge in space 33 will fluctuate in the vents and will not enter the clearance space. Alternatively, the initial immersion of the tool in the hole will lill space 33 with relatively grit-free well iluid.
  • the forward surface 36 of the piston is provided with a central valve chamber forming countersink 37 having a forwardly-facing shoulder 3S which intersects with the wall of piston passage 31 to form a valve seating clement 35.
  • this seating element is formed by a sharp corner, but may Vbe formed Yby a wider, chamfered surface, as will be explained.
  • the forward face of the piston is peripherally relieved, as at 54, to accommodate a stop ring S which limits the forward movement of the piston when the tool is hanging off bottom.
  • a one-piece valve 39 at least the surface of which, in whole or in part, preferably, is of suitable resilient material, is received in the valve chamber formed by piston countersink 3?
  • This seat preferably, is chamfered, as shown, and may be provided with a resilient seating insert.
  • the valve has a generally cylindrical, skeletonized superstructure 41 provided with an upper flange 42 which is of less radius than internal passage 31 of the hammer piston but radially overlaps a snap ring 43 provided in the wall of passage 31. Ring 43 may have, as shown, a resilient mounting 43a to dissipate some of the shock thereon.
  • a plurality of legs 44 and 45 depend from valve ybody 39, legs 44 resting upon an apertured spring seating disk 46, while center leg 45 extends slidably through the disk and is distally provided with a cotter key 47 or other stop for maintaining the assembly.
  • a coiled compression spring 48 is also received in the enlarged entry part 21a of anvil duct 21 and about spring guiding fingers or sleeve 49 depending from disk 46.
  • Spring 48 at its lower end, seats against a replaceable bushing S0 which rests upon an internal shoulder 51 within exhaust duct 21.
  • the thickness of 'bushing 50 may be varied to vary the prestressing of spring 48.
  • the percussion motor above described operates as follows: When operating uid is not being supplied through the connection formed by inlet passage 32 at suicient pressure to drive piston 26 downwardly against spring 48 and the ambient well pressure, the piston will be urged upwardly causing its upper surface 51 to engage the under surface of bumper 11. This limits the piston movement under such conditions and, at the same time, since motoring valve 39 will be closed against piston seating element 35, the interior of the motor will be substantially sealed against the upward entry of ambient drill fluid, so that an additional float valve is unnecessary.
  • the effective force tending to drive the piston downwardly can be controlled by means of spring 4S. If, for instance, the compressive reaction of the spring is increased, as by increasing the thickness of bushing 1, the operating fluid can be supplied at greater pressure without causing premature unseating of valve 39 from piston seating element 35.
  • the reactive force of spring 48 is more effective than in deep wells where drilling mud is used. This is because in the latter case, the ambient pressure acting upwardly through ducts 2l, 22 upon valve 39 will greatly exceed the reactive force of spring 48. Also, in deep holes, the difference between the areas l1rb2/4 and mi2/4 becomes important as these areas determine the differential lacross the valve body 36. In general, this differential should be minimum where the spring is to be relatively more effective. A greater differential will increase the relative effect of ambient pressure, even to the point where the spring force may be negligible so that a very highly-loaded spring is not necessaryy, particularly in a deep well, to obtain quite large net operating pressures on the piston.
  • the novel percussion motor may be used with gaseous or liquid motivating lluids and in shallow or deep holes, Iand higher operating pressures can be utilized simply by increasing the areasof the valve seating elements.
  • FIG. l shows in dot ⁇ and dash line at S5 the alternate extended position of bumper 11.
  • valve seating element 57 in piston 26a is formed as a separate ring which is inserted Iagainst an inner shoulder 58 Within piston passage 31a and secured in position by a snap ring 59.
  • An O-ring seal is provided at 60.
  • Seat member 57 extends radially inwardly from the Wall of piston passage 31a and has a depending, relatively narrow valve engaging boss 61. The effect of this separate member 57 is to provide a reduced dimension b-l and, accordingly, the upwardly-facing surface area of valve 39a which is exposed to the working fluid pressure when the valve is seated on element 61. This, in turn, reduces the total force tending to open the valve and, therefore, permits the application of higher working fluid pressure to the hammer piston.
  • seat element 57 may strike valve superstructure ange or collar 42a to unseat valve 39a from the anvil.
  • valve 39b is provided with a bypass oritice 64 which provides for a constant supply of working fluid to the bit during operation.
  • a bypass oritice 64 which provides for a constant supply of working fluid to the bit during operation.
  • the same result can be achieved, as explained above, by increasing the Working pressure sufficiently to prevent the valve from engaging piston valve seat element 35. However, this would result in constant bleeding of drilling fluid past the seating element and where the -drilling uid is abrasive, erosion of the seating element would result.
  • the valve 39e is equipped with an axial through passage 66 provided with a. transverse fracturable disk 67. If for any reason it is desired to bypass additional drill iiuid, as vin case the tool should become damaged or stuck, disk 67 can be fractured by a suicient increase in the working uid pressure applied thereto.
  • the valve unseating stop ring 43 of the previous forms is omitted in this form. It has been found that in some cases the water hammer shock produced by irnpact of the hammer and seating of the motoring valve against the anvil decays suciently rapidly to produce an automatic pop off of the valve and avoid the necessity of the mechanical valve reversal.
  • stop ring 11a has its central passage 32a plugged at the bottom, as at 69, and the wall of the bumper is provided with inclined passages 70 which open through the bottom face of the bumper.
  • the passages 70 are positioned to be sealed by the upper surface 51 of piston 26 in the rest position of the piston. This provides an additional seal for preventing the entry of contaminating and/or Vabrasive ambient well liquids into the drill motor.
  • the bumper may be mounted, as shown, on resilient ribs 72 for dampening the vibratory shock where the piston strikes the bumper at the rear end of each stroke to expedite the .turn-around.
  • the bumper of sufcient mass may be constructed by constructing the bumper of sufcient mass that no connection at lall need be provided with the casing, the bumper merely resting on a flange, for instance.
  • Resilient ribs 72 may be secured in grooves or recesses in the surface of the piston.
  • Main valve body 75 has a rearwardly-facing, tapered part 76 for seating against the seat element 77 at the outlet of axial piston passage 78 in piston 91, and a forwardly-facing portion 79 for engaging seat element 80 about the inlet of exhaust duct 81 in the anvil.
  • a generally tubular structure 82 projecting above the valve body slidably fits passage 78 and has -sector-shaped, longitudinal cutouts 83 located oppositely in its outer surface, a transverse passage 84 opening oppositely through ports 8S, and a longitudinal, central passage 86 connecting transverse passage 84 with anvil exhaust through duct 81.
  • Projecting downwardly from the valve body and freely received in duct 81 is a skeletonized part S8 which rests at its lower extremity on a sleeve or bushing 89 which, in turn, rests upon coiled spring 90 supported upon a shoulder Within exhaust duct 81, as 51 in FIG. l.
  • valve body is in the form of a downwardlyand outwardlyinclined ring 96 having a periphera-l seating portion 97 which may be provided with a resilient seating part 98.
  • a skeletonized structure 99 projects above the valve body and its upper end carries an external flange 100.
  • a sleeve 1G11 is secured in the outlet portion of passage 102 in piston 103, as by means of .a snap ring 104 seated between a groove 105 therein and a tapered groove 166 in the piston bore, and a locking nut 104e.
  • An annular, shoulder-'forming element 107 projects from the inner wall of sleeve 101 for eng-aging flange 100 to positively unseat valve 9'6-98 during the latter part of the return stroke of the piston.
  • a plug element 108 is secured at the inlet of anvil exhaust passage 109 by means of parallel longitudinal legs 110 themselves secured in Vpassage 109 in anvil 111, as by a snap ring construction 112.
  • a ring 113 preferably of resilient material, projects above the periphery of plug element 108 and has a tapered outer surface 114 for a purpose to be described.
  • FIG. 10 shows piston 103 after striking anvil 111 and after ring valve 96-98 has been impelled forwardly by inertia to seat against the anvil valve seating element 117.
  • the working fluid then flows through skeletonized structure 99 and into forward working chamber 118 to impel the piston rearwardly.
  • FIGS. l5 and 16 The nal form in FIGS. l5 and 16 is for the purpose of reducing the area of the operating valve exposed to operating pressure, as also achieved in FIG. 3.
  • a cup-like nipple member 126 is secured by means of a snap ring 129 at the outlet end of a sleeve 127 lodged in piston 4passage 128.
  • a resilient packing A13:0 may be interposed between the sleeve and nipple 126.
  • Ports 131 are formed in the skirt of memer 125 just below the lower extremity of sleeve 127.
  • the bottom 132 of the nipple member is provided with a central aperture 133 in which is slida'bly received the shank portion 134 of a bolt whose enlarged head 135 normally rests -on the upper surface of the nipple bottom part.
  • a nut 136 is provided on the free lower end of the bolt and suitably secured in position.
  • a ring valve of angular section has an apertured transverse web 137 received about bolt shank 134 .and lan upstanding peripheral part 138, the inner surface 139' of 4which slides on the exposed outer surface of nipple member 126, sealing grooves being provided in the mating surface of this member.
  • a tapered seat 140 which may engage a corresponding seat element 141 at the lower end of sleeve 127.
  • At the bottom edge of upstanding valve part 138 there is provided atapered seating portion 142 which may cooperate with a seating element 143 about the inlet of exhaust passage 144- in anvil 145.
  • a skeletonized guide sleeve 14.6 depends from valve part 138 and its lower extremity rests upon a spring seat ring 147 which, in turn, rests upon coiled spring 148.
  • the novel drill motor in its several forms, is very flexible .as to pressures and volumes of the working tluid as well as the kind of working fluid it will accommodate. Where the valve closes fully against the hammer seating element during the turn-around and down stroke, the Vworking stroke will be impelled most eiiiciently by positive displacement.
  • the use of the differential area piston results in transfer of energy from the moving uid to the hammer with minimum surges in the drill pipe and annulus. Since energy will be transferred at a pressure level that satisfies the inertial eqn-ation y(force equals mass times acceleration) and since the pressure times area equals the driving force, it follows that the working pressure must increase Ias the area decreases.
  • valve design is important and it is preferred that the area of the valve radially outside of the hammer valve seating element 'be reduced as 4much as possible so that the increased area exposed to the working fluid, as tlte valve opens downwardly, is reduced to Ia minimum.
  • the action of the valve as a pressure costroler is more eiiicient and the valve responds to closely-varying pressures, thus reducing or eliminating the need for an accumulator or da'mpener in the operating iluid line and also reducing the shock to the rig.
  • Another advantage of most of the forms of the novel valve is that they are not guided by any sliding contact with other parts, but rather' tloat in the operating medium so that the valve tends to have the same velocity as the hammer at the time the hammer strikes the anvil. Furthermore, there is no need for any means other than inertia to assist the valve action at the end of the working stroke. At the rear end of the stroke, the turn-around may be mechanically triggered or may rely on changing of fluid for-ces.
  • the pressure within the anvil land on the drilled roei: face is advantageously reduced. This reduces the restraining pressure on the chips being produced making it easier for the chips to ily and requiring less blow energy to trigger the activity. This reduced pressure zone, however, does not affect uphoe conditions materially, since the surge wiihin the hammer acts to accelerate the hammer upward from its impact position causing an upward fluid impulse in the vented space 33 and the well annulus.
  • the spring and vaive will be supplied as a separate assembly which can be replaced as wear occurs or as it is desired to alter the manner of operation or the type of working fluid used.
  • the separate valve seating insert in the piston contributes rnaterially to the flexibility of the tool.
  • a special anvil-bit must be provided for use with this new tool.
  • valve 26 When the tool is lifted off bottom, the spring load on the valve is reduced, duc Ato dropping of the anvil relative to the casing. While the piston is stopped by ring S5, valve 26 would then seat against piston seat 35 to resist access of well fluid into the tool. In order to produce blowing of the -drill fluid under such condition, it is only necessary to increase the delivery pressure thereof suicient to force the valve off seat 35.
  • the ring valve functions more or less as an ordinary check type oat valve.
  • the valve will close up on its piston seating element and lift the piston to engage the bumper, thus shutting off the drill pipe from the well liquid. Further, when a round trip is being made, with the tool in suspended position, the pressure setting of the control valve is reduced allowing the valve to Open and the liquid in the drill stem to run into the well. Thus, dry pipe will be handled on the rig platform.
  • a percussion drill having a casing with a forward part of greater transverse area than the rear part thereof, a hammer piston re-ciprocable in said casing and having 4differential forward and rearward working faces received respectively in said casing forward and rear parts, there lbeing a longitudinal passage extending through said piston, a connection for supplying operating fluid to said casing rear part under normal -operating conditions, and an anvil in said ICasing forward part with an exhaust duct therethrough, the improvement comprising rst and second opposinU valve seats respectively at the radjacent ends of said longitudinal passage and said exhaust duct, a check valve received between said seats, and means operable on said valve for impelling the same towards said rst seat, under normal operating conditions, during the latter part of the rearward return stroke of said piston for restricting said piston passage and exhausting said casing forward part through said anvil duct and thereby initiating the forward power stroke, said valve impelling means Ibeing calibrated and said valve being of suflicient mass
  • a fluid operated percussion drill a casing, an anvil at the forward end of said casing having an exhaust duct, a piston reciprocable in said casing for beating upon said anvil, said piston having a longitudinal passage therethrough and having a forward working face which is larger than the rearward working face thereof, and a connection at the rear end of said casing for constantly supplying operating fluid to said piston rear face and forwardly through said piston passage under normal operating conditions
  • the improvement comprising opposing piston and anvil valve seats at the adjacent ends of said piston passage and said exhaust duct, a double acting check valve having seating parts movable between and cooperable with said seats, and means for impelling said valve toward said piston valve seat under normal operating 'conditions during the latter part of the rearward return stroke of said piston while opening said exhaust duct to said casing forward part for producing the forward power stroke of said piston, said valve seats being spaced apart axially of the drill -a greater distance than said seating parts and said valve impelling means being calibrated and said Valve being constructed and arranged to cause said
  • a percussion drill having a casing, a connection for ⁇ supp-lyinU operating fluid to the rearward part of said casing and an anvil at the forward part thereof, a hammer piston reciprocable in said casing to beat upon said anvil, the forwardly-facing area of said piston being exposed to the forward part of said casing and being greater than the rearwardly-facing area thereof, passage means leading from said connection to the forward part of said casing, an exhaust duct leading from said casing forward part, the improvement comprising valve seat elements, respectively, in the ⁇ outlet of said passage means and the inlet of said duct, valve means movable between said seat elements, and means for alternately causing seating of said valve ⁇ means on said exhaust duct and passage -means seat elements to thereby cause successive application of the -oper-ating fluid pressure through said passage seat element to said piston forwardly-facing area, while said exhaust duct seating element is closed, for impelling said piston rearwardly, and for closing said passage seat element to exclude said ii
  • a tluid operated percussion tool a casing, an anvil at the forward part of said casing with an exhaust duct, a diiferential piston working in said casing with its forward Working face larger in transverse area than its rearward working face, a connection at 'the rear end of said casing for supplying working fluid to the rearward part of said casing, and a longitudinal passage through said piston, the improvement comprising opposing piston and anvil valve seats, respectively, at the adjacent ends of said piston passage and anvil duct, a unitary, double-acting check valve floating between said seats, and means to maintain said valve against said piston seat during normal operation in the latter part of the rearward return stroke and during the forward Working stroke of said piston to cause said working stroke, said valve maintaining means being calibrated and said valve being constructed and arranged to cause said valve to be impelled forwardly by inertia upon striking of said anvil by said piston to close said anvil exhaust duct and again expose said larger piston forward surface to the working fluid to repeat the cycle.
  • a percussion drill as described in claim 4 in which said means maintaining said valve means against said piston seat includes a spring stressed between said valve and said anvil.
  • valve means comprises a one-piece valve body having upper and lower seating faces for cooperating alternately With said seating elements.
  • a percussion drill as described in claim 6 further including cooperating structures projecting, respectively, from said valve body and the wall of said piston passage for unseating said valve body from said exhaust duct seat element during the return stroke of said piston.
  • a percussion drill as described in claim 7 further including spring seat and guide structure depending from said valve.
  • a drill as described in claim 5 further including an internal shoulder in said exhaust duct and spring seating and guiding structure depending from said valve means, said spring being stressed between said shoulder and said structure.
  • a percussion drill as described in claim 4 in which said piston valve seat constitutes a substantial restriction in said piston passage to reduce the area of said valve exposed to the operating uid during the working stroke and thereby reduce the force necessary to maintain said valve on said piston seat during the working stroke.
  • a percussion drill as described in claim 10 in which said passage valve seat is separately formed and replaceable for repair purposes and to adjust the area of said valve means exposed to the operating fluid pressure when said valve means is seated on said passage seat element.
  • a percussion drill as described in claim 4 further including a stop member in the rear part of said casing positioned to limit rearward movement of said piston but to clear said piston during normal reciprocation thereof.
  • a percussion drill as described in claim 4 further including a highly-resilient stop member at the rear end of said casing in position to be engaged by said piston at the rear end of each normal return stroke to expedite the turn-around of the piston.
  • connection for operating fluid includes port means opening through said stop member in position to be closed by said piston when in engagement with said member for sealing communication through said casing.
  • a drill as described in claim 4 further including a constantly open bypass opening through said valve body.
  • a percussion drill as described in claim 4 in which said check valve includes structure projecting into said piston passage and recessed to direct operating uid from said piston passage into the forward part of said casing when said valve is on said anvil seat, said structure having a bypass duct positioned to be closed :by said piston when Asaid valve initially engages said anvil seat and to be exposed beneath said piston vduring the return stroke thereof for bypassing uid in said casing forward part into said anvil duct to relieve the pressure in said casing forward part whereby said check valve may close against piston valve seat -to initiate the working stroke of the piston.
  • a percussion drill as described lin claim 4 in which said anvil exhaust duct opens into said casing forward part through an annulus about a central plug, said anvil valve seat being formed at the outer edge of said annulus, and said check valve having radially-spaced inner and outer annular parts for seating respectively on said piston and anvil valve seats and an upwardly and inwardly disposed wall structure between said parts, the under surface of said wall structure 'being of greater area than the valve area exposed to the operating fluid when said valve is on said piston seat whereby the operating fluid trapped between said under surface and said plug urges said valve toward said piston valve seat.
  • a percussion drill as described in claim 13 further including cooperating structure on said valve and said piston for positively unseating said valve from said anvil seat during the latter part of the rearward piston movement.
  • a percussion drill having a casing, an anvil at the forward end thereof with an exhaust duct, a differential hammer piston reciprocable in said casing for beating upon said anvil, a longitudinal passage through said piston, and a connection with the rearward portion of said casing for supplying operating uid thereto, the improvement comprising a valve seat on said anvil about the entry of said exhaust duct, a nipple member depending from the lower face of said piston and having a closed bottom and port means in the side wall thereof, a ring valve slidable on said nipple, and means for urging said ring Valve to a rearward position during the latter part of the piston rearward movement for closing said port means to substantially confine the operating fluid to the upper surface of said piston and thereby drive said piston forwardly, said valve being constructed and arranged to be impelled forwardly by inertia when said piston strikes said anvil for seating against said anvil to close said anvil exhaust duct and direct operating fluid into said casing forward part and thereby
  • a percussion drill having a casing with an operating fluid connection at its rear end and an anvil at its i;
  • a percussion drill as described in claim 22 in which aid firs-t fluid is relatively immiscible with said ambient well fluid and said vent means is of suicient length to retain the parting line between said fluids therein.
  • An anvil-bit device for a percussion tool having a rear part for slidable reception in a percussion tool casing and an axial exhaust passage for operating fluid, a valve seat about the inlet of said passage for cooperation with a motoring val-ve, and a shoulder within said passage for seatin a motoring valve operating spring.
  • An anvil-bit device for use with a percussion drill having a casing and a hammer piston reciprocable therein, said device having a forward, formation cutting part, a rear part for slidable reception in the forward end of the drill casing, an axial exhaust duct with an enlarged inlet, a motoring valve seat about said inlet, and motoring valve biasing means in said inlet.

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3464505A (en) * 1967-11-01 1969-09-02 Pan American Petroleum Corp Drilling apparatus
US3491838A (en) * 1968-06-21 1970-01-27 Pan American Petroleum Corp Valve for liquid percussion drill
US3602317A (en) * 1969-10-30 1971-08-31 Drilling Well Control Inc Drill bit percussor apparatus
US3712387A (en) * 1968-11-04 1973-01-23 Amoco Prod Co Rotary percussion drilling motor
US3768576A (en) * 1971-10-07 1973-10-30 L Martini Percussion drilling system
US4940097A (en) * 1988-12-13 1990-07-10 Martini Leo A Fluid powered rotary percussion drill with formation disintegration inserts
US4958690A (en) * 1987-02-25 1990-09-25 Salzgitter Maschinenbau Gmbh Drilling device with hydraulic percussion generator for earth drilling purposes
EP0640170A1 (en) * 1992-05-15 1995-03-01 Sds Pty. Ltd. Improved drilling arrangement and method
US5396965A (en) * 1989-01-23 1995-03-14 Novatek Down-hole mud actuated hammer
US20080276444A1 (en) * 2007-05-11 2008-11-13 The Boeing Company., Method and Apparatus for Squeezing Parts such as Fasteners
NO334793B1 (no) * 2011-08-19 2014-05-26 Pen Rock As Høyfrekvent væskedrevet borhammer for perkusjonsboring i harde formasjoner
US8820407B2 (en) 2010-02-08 2014-09-02 Smith International, Inc. Flow diverter ring for reducing wear in mud saver valves
US20140360783A1 (en) * 2013-06-10 2014-12-11 Center Rock Inc. Pressure control check valve for a down-the-hole drill hammer
WO2015003215A1 (en) 2013-07-12 2015-01-15 Drillroc Pneumatic Pty Ltd Dynamic seal tube for a down hole hammer drill
US11686157B1 (en) * 2022-02-17 2023-06-27 Jaime Andres AROS Pressure reversing valve for a fluid-actuated, percussive drilling tool
EP4339416A3 (en) * 2020-03-30 2024-05-29 Mincon International Limited Flushing and connection arrangements for percussion drill tools

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US2403582A (en) * 1942-09-16 1946-07-09 Western Foundation Company Power hammer
US2580203A (en) * 1948-10-28 1951-12-25 Gulf Research Development Co Hammer drill
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US3162251A (en) * 1960-01-19 1964-12-22 Bassinger Ross Enclosed case mud percussion tool
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Publication number Priority date Publication date Assignee Title
US3464505A (en) * 1967-11-01 1969-09-02 Pan American Petroleum Corp Drilling apparatus
US3491838A (en) * 1968-06-21 1970-01-27 Pan American Petroleum Corp Valve for liquid percussion drill
US3712387A (en) * 1968-11-04 1973-01-23 Amoco Prod Co Rotary percussion drilling motor
US3602317A (en) * 1969-10-30 1971-08-31 Drilling Well Control Inc Drill bit percussor apparatus
US3768576A (en) * 1971-10-07 1973-10-30 L Martini Percussion drilling system
US4958690A (en) * 1987-02-25 1990-09-25 Salzgitter Maschinenbau Gmbh Drilling device with hydraulic percussion generator for earth drilling purposes
US4940097A (en) * 1988-12-13 1990-07-10 Martini Leo A Fluid powered rotary percussion drill with formation disintegration inserts
US5396965A (en) * 1989-01-23 1995-03-14 Novatek Down-hole mud actuated hammer
EP0640170A1 (en) * 1992-05-15 1995-03-01 Sds Pty. Ltd. Improved drilling arrangement and method
EP0640170A4 (en) * 1992-05-15 1997-09-03 Sds Pty Ltd IMPROVED DRILLING PROCESS AND ARRANGEMENT.
US20080276444A1 (en) * 2007-05-11 2008-11-13 The Boeing Company., Method and Apparatus for Squeezing Parts such as Fasteners
US8820407B2 (en) 2010-02-08 2014-09-02 Smith International, Inc. Flow diverter ring for reducing wear in mud saver valves
NO334793B1 (no) * 2011-08-19 2014-05-26 Pen Rock As Høyfrekvent væskedrevet borhammer for perkusjonsboring i harde formasjoner
US10385617B2 (en) 2011-08-19 2019-08-20 Hammergy As High frequency fluid driven drill hammer percussion drilling in hard formations
US20140360783A1 (en) * 2013-06-10 2014-12-11 Center Rock Inc. Pressure control check valve for a down-the-hole drill hammer
US10100578B2 (en) * 2013-06-10 2018-10-16 Center Rock, Inc. Pressure control check valve for a down-the-hole drill hammer
WO2015003215A1 (en) 2013-07-12 2015-01-15 Drillroc Pneumatic Pty Ltd Dynamic seal tube for a down hole hammer drill
CN105378206A (zh) * 2013-07-12 2016-03-02 钻岩气动有限公司 用于井下锤钻的动态密封管
EP3019687A1 (en) * 2013-07-12 2016-05-18 Drillroc Pneumatic Pty Ltd Dynamic seal tube for a down hole hammer drill
EP3019687A4 (en) * 2013-07-12 2017-03-29 Drillroc Pneumatic Pty Ltd Dynamic seal tube for a down hole hammer drill
EP4339416A3 (en) * 2020-03-30 2024-05-29 Mincon International Limited Flushing and connection arrangements for percussion drill tools
US11686157B1 (en) * 2022-02-17 2023-06-27 Jaime Andres AROS Pressure reversing valve for a fluid-actuated, percussive drilling tool

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Publication number Publication date
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