EP0022865B1 - Hydraulisch angetriebene bohrvorrichtung im bohrloch - Google Patents

Hydraulisch angetriebene bohrvorrichtung im bohrloch Download PDF

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Publication number
EP0022865B1
EP0022865B1 EP19790900104 EP79900104A EP0022865B1 EP 0022865 B1 EP0022865 B1 EP 0022865B1 EP 19790900104 EP19790900104 EP 19790900104 EP 79900104 A EP79900104 A EP 79900104A EP 0022865 B1 EP0022865 B1 EP 0022865B1
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EP
European Patent Office
Prior art keywords
drill
pressure oil
oil passage
rod
hydraulic
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
Application number
EP19790900104
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English (en)
French (fr)
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EP0022865A1 (de
EP0022865A4 (de
Inventor
Yoshikazu Mikami
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.)
Furukawakogyo Coltd
Original Assignee
Furukawakogyo Coltd
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 PCT/JP1978/000057 external-priority patent/WO1980001300A1/ja
Application filed by Furukawakogyo Coltd filed Critical Furukawakogyo Coltd
Priority to EP19790900104 priority Critical patent/EP0022865B1/de
Publication of EP0022865A1 publication Critical patent/EP0022865A1/de
Publication of EP0022865A4 publication Critical patent/EP0022865A4/de
Application granted granted Critical
Publication of EP0022865B1 publication Critical patent/EP0022865B1/de
Expired legal-status Critical Current

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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
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/18—Pipes provided with plural fluid passages
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B21/00—Methods or apparatus for flushing boreholes, e.g. by use of exhaust air from motor
    • E21B21/12—Methods or apparatus for flushing boreholes, e.g. by use of exhaust air from motor using drilling pipes with plural fluid passages, e.g. closed circulation systems

Definitions

  • the invention relates to a down-the-hole hydraulic drill comprising a down-the-hole hammer drill having a cylinder in which a piston is slidably housed, the piston being reciprocated by means of pressurized oil controlled by a directional control valve housed in said cylinder, said piston having a central axial bore for pressurized air or hydraulic flushing fluid for discharging the cuttings; a drill rod connecting said hammer drill to a rotary drill head, said drill rod consisting of a plurality of segments in the form of pipes which define a high pressure oil passage along the central axis and a low 'pressure oil passage and a passage for said flushing fluid located radially outwardly and concentrically to each other around said high pressure oil passage; a rotary head disposed outside the borehole and being connected to the drill rod said rotary head comprising a shank rod having passages which communicate with respective swivels and with said high pressure oil passage, low pressure oil passage and passage for flushing fluid provided in the rod; and
  • drills of the type utilizing pressurized air for a percussion mechanism of the piston are inferior in efficiency, and much in power loss and yet there has been a certain limitation in the power and the number of repetition of blows or percussive actions.
  • hydraulic passages and the passage for introducing pressurized air or fluid for discharging sludge have been provided by inserting hoses or the like, consequently, connection of these passages have been very troublesome and yet not free from the leakage of oil.
  • a down-the-hole hydraulic drill comprising a cylinder, in which a piston is slidably housed, which is reciprocated by pressurized oil through a directional control valve means. Said piston has on its central axis a passage for pressurized fluid or hydraulic air for discharging sludge.
  • the already known down-the-hole hydraulic drill comprises a rotary head, which is connected with the drill head via an interconnected drill rod.
  • This known down-the-hole hydraulic drill shows the drawback that the piston is not directly operated by hydraulic oil, but that there is provided a spring for operating the piston, by means of said spring no sufficiently sure reciprocating movement of the piston is achieved.
  • the passages for pressurized oil and return oil as well as for pressurized air are arranged in the directional control valve so that the construction of said valve is expensive and complicated.
  • a drill connection to connect the drill rod with the drill head, by means of said drill connection the direction of the passages for the fluid flows can be changed in such a way that the passage for hydraulic air for discharging sludge is to be found on the central axis.
  • This hydraulic drilling device comprises already a compensator for hydraulic pressure interposed between the last drill rod and the drill hammer.
  • the problem of the invention is to prevent the disadvantages of the down-the-hole hydraulic drill and to provide a down-the-hole hydraulic drill with a simplified construction and in which the piston is operated in a faster and safer way so that an improvement in drill efficiency can be achieved.
  • said cylinder of the hammer drill has a high pressure oil passage and low pressure oil passage, that said piston within the cylinder has a front pressure surface and a rear pressure surface each having different areas so that said cylinder is divided into a first hydraulic chamber and a second hydraulic chamber by said piston, that said high pressure oil passage in the cylinder is communicated with both said first hydraulic chamber and second hydraulic chamber, and said low pressure oil passage in the cylinder is communicated with said second hydraulic pressur chamber; that the directional control valve has a front end surface and rear end surface with different areas and is housed slidably in said second hydraulic chamber thus allowing change of action of the hydraulic oil under pressure on said pressure surfaces of the piston, that the hydraulic drill further comprises a drill connection interposed between the last of said rods and said hammer drill such that each of the passages in said rod can be communicated to each of the corresponding passages in said hammer drill, said drill connection comprising a passage for pressurized air or fluid for discharging sludge located and formed
  • This invention includes a preferred embodiment which comprises an automatic valve or valves which opens both said high pressure oil passage and low pressure oil passage only when another rod segment is connected to its connecting end.
  • Down-the-hole hydraulic drill of the present invention is simplified in designing the fluid passages and can be housed in a small space by providing both the directional control valve means and fluid passages for actuating reciprocal movement of the piston in the cylinder constituting the drilling head. Also the piston action can be performed very firmly.
  • the rod portion is composed of a plurality of concentrically disposed pipes wherein the high pressure oil passage is formed on the central axis and the low pressure oil passage is formed around the high pressure oil passage and the passage for pressurized air or fluid is positioned further around the low pressure oil passage.
  • the provision of the automatic oil shutting valve or stop valve at the connecting end ensure complete prevention of oil leaking during the connecting or disconnecting operation of the rod and thereby the connection and disconnection can be done readily and rapidly, thus this invention contributes to improve economical use of both power and material.
  • connection by interposing the drill connection which enables to leads the fluids under pressure from the rod to the drill head having differently positioned fluid passages from the former and to establish correct communication to each corresponding passages, both, the pressurized oil, and the air or hydraulic fluid for discharging the sludge can be done very smoothly.
  • pressure compensation device can be mounted adjacent to the drill head so that drilling operation in a deep well can be performed by maintaining required percussive force and with high efficiency.
  • Fig. 1 is a cross sectional elevation of a drilling head.
  • Fig. 2 is a cross sectional elevation of a drill connection.
  • Fig. 3 is a stepped vertical cross sectional view of the drill connection taken along line A-A of Fig. 2.
  • Fig. 4 is an enlarged cross sectional elevation of the junction of a rod.
  • Fig. 5 is a cross section elevation of a rotary head.
  • Fig. 6 is a cross section plan view taken along line B-B of Fig. 5.
  • Fig. 7 is a cross sectional elevational view of a pressure compensation device.
  • Fig. 8 is a cross sectional view taken along line D-D of Fig. 7.
  • a cylinder 2 having circular cross section comprises an axially extending passing-through bore consisting of a reduced diameter portion 3.
  • a plug 7 being provided therewith a valve seat is inserted therein.
  • a piston 8 consists of an intermediate diameter portion 9, a first enlarged portion 10, a second enlarged portion 11, a reduced diameter portion 12, each of which slidably fits with the reduced diameter portion 3, main or intermediate diameter portion 4 of the cylinder 2 and said plug 7, respectively, and a percussion head 13 at the forward end of the intermediate diameter portion 9.
  • An interconnecting portion 14 having a diameter slightly smaller than that of intermediate portions 10 and 11 is formed between the intermediate portions 10 and 11.
  • a hydraulic or pneumatic passage 50 for discharging sludge formed by drilling operation is bored on the central and longitudinal axis of said piston 8.
  • the piston 8 comprises an annular front pressure surface 15 and an annular rear pressure surface 16, on which surfaces a hydraulic oil under pressure acts.
  • the pressure surface 15 has a surface area defined by a stepped portion between the intermediate portion 9 and the first enlarged diameter portion 11, while said pressure surface 16 has a surface area defined by the second enlarged diameter portion 11 and the reduced diameter portion 12.
  • the surface area of said rear pressure surface 16 is larger than that of the front pressure surface 15.
  • Said front pressure surface 15 and said intermediate diameter portion 9 of the piston 8 defines a first hydraulic pressure chamber 17 with the main or intermediate diameter portion 4 of the cylinder 2.
  • the rear pressure surface 16 and the reduced diameter portion 12 of the piston 8 define a second hydraulic pressure chamber 18 with both of the cylinder 2 and the plug 7.
  • a directional control valve 20 is provided slidably disposed within said second hydraulic pressure chamber 18 and is concentric with the piston 8 so as to annularly surround the reduced diameter portion 12 of the piston 8, whereby the second hydraulic pressure chamber is divided by the directional control valve 20 into a front chamber 18a and rear chamber 18b.
  • Said directional control valve 20 is slidably fitted around the enlarged diameter portions 5, 6 of the cylinder and the valve seat 7a of said plug 7, and rearward end 20b of which has a larger area than that of a forward end 20a.
  • Stroke of the directional control valve 20 is restricted at the forward end portion 20a, by abutment with a stepped portion 21 of said cylinder 2, while at its rear end portion by abutment with a stepped portion 7b of the plunger 7.
  • a stepped portion 22 projecting radially and inwardly toward the longitudinal axial center is formed at the middle part of said directional control valve 20, inside diameter of said stepped portion is slightly larger than the diameter of the reduced portion 12 of said piston 8.
  • a plurality of longitudinal small grooves 23 are formed between the rear end portion 20d of the directional control valve 20, whereby a suitable amount of hydraulic oil can be communicated from the front chamber 18a to the rear chamber 18b.
  • Sectional dimension of said grooves 23 can be decided depending upon the nature of the hydraulic oil and the characteristic of the percussion means.
  • Annular grooves 24 and 25 are formed, respectively, at the main diameter portion 4 and the enlarged diameter portion 5 of said cylinder 2 such that the grooves 24 and 25 communicate, respectively, with a high pressure oil passage 30 formed in said cylinder 2.
  • the annular groove 27 communicates said low pressure hydraulic oil passage 40 to the second hydraulic fluid chamber 18 through a passage 28 and an annular groove 29 both formed in said stepped portion 22, when the directional control valve 20 takes its advanced position.
  • the annular groove 24 is positioned at a location where there occurs no closing thereof by said piston 8 when piston 8 takes its position for percussion, and said first hydraulic chamber 17 usually communicates with a hydraulic oil pressure source ion normal operation.
  • the front chamber 18a and rear chamber 18b of said second hydraulic pressure chamber 18 communicate with each other by a passage 41.
  • the annular groove 28 is formed adjacent to said annular groove 26 thereby these two grooves communicate with each other through the interconnecting portion 14 of the piston 8.
  • 29a is a supplementary passage for effecting smooth sliding of said directional control valve 20.
  • the piston 8 and the directional control valve 20 in Fig. 1 shows a state where said piston 8 is immediately before starting its backward stroke after it has finished its advancing stroke, while the directional control valve 20 is kept to abut against the stepped portion 21 caused by a pressure difference due to difference of area between the forward end 20a and rear end 20b.
  • the first hydraulic pressure chamber 17 communicates to the high pressure oil passage 30, thereby the piston 8 starts its backward stroke by an oil under pressure acting upon said front pressure surface 15 of the piston 8.
  • the piston 8 is also acted on by a pressurized oil on its rear pressure surface 16 having larger pressure surface area than that of the front pressure surface 15, accordingly, the speed of the piston 8 gradually decreases until it finally stops to complete its backward stroke.
  • the directional control valve 20 advances due to pressure difference caused by the difference in surface area between the forward end face 20a' and the rear end face 20b thereof, then it stops when the forward end face 20a abuts against said stepped portion 21 thereby the annular groove 25 is closed to prevent the pressurized oil from flowing into the forward chamber 18a.
  • a drill bit 33 is slidably held in the front head 32 and is also fitted with the chuck 31 by spline engagement.
  • a rear end of the drill rod confronts with the percussion hammer portion 13 of said portion 8.
  • a stepped face 34 is formed at the forward part of the front head 32 defined by an undercut recess 35.
  • a resilient member 36 is inserted into a space between the stepped face 34 and the rear end of said chuck 31 and a set of beveled spring 37 is resiliently interposed within said resilient member 36 such that a flange 38 of the drill bit 33 abuts thereon so as to restrict the stroke thereof as well as to absorb and cushion the shock imparted to the percussion head caused by the percussive action of said drill bit 33.
  • Figs. 2 and 3 show the drill connection 51 in which a passage 50 for pressurized air or fluid for discharging drilled sludge is bored along a body portion 52 having an outside diameter about the same as inside diameter of said cylinder 2.
  • a plurality of high pressure oil passages 30 and low pressure oil passages 40 are formed radially and outwardly around and on the same concentric circle with respect to said passage for pressurized air or fluid.
  • a reduced diameter portion 54 formed with a recessed portion 53 having an inside diameter the same as that of the plug 7 inserted in the cylinder 2 of said drilling head 1 and an intermediate diameter portion 55 between the body portion and the reduced diameter portion.
  • the reduced diameter portion 54 has an outside diameter so as to be inserted into the rear end of the cylinder 2 of the drilling head 1 and is threadably fixed to said cylinder 2 by the screw threads formed on said intermediate diameter portion 55.
  • Fluid passages in the body portion 52 extend to the reduced diameter portion 54 and the air or fluid passage 50 has its opening at the bottom of the recessed portion 53, while the high pressure oil passage 30 and the low pressure oil passage 40 have openings at the outer periphery of the reduced diameter portion 54 and are communicated with respective oil passages formed in the cylinder 2 of said drilling head 1.
  • Rear end portion (upper part in the drawing) of the body member has, from its upper tip end to its lower part, a reduced diameter portion 56, an intermediate diameter portion 57 and an enlarged diameter portion 58, respectively, and constitutes a portion for connection with a rod 60 which will be explained later.
  • a high pressure oil passage 30 is bored along the longitudinal axis of said reduced diameter portion. Said oil passage 30 is radially bent such that it is communicated with the high pressure oil passages 30 formed in the body portion 52.
  • inlet ports 59 and a slit are formed to permit fluid communication with said low pressure oil passage and the passage 50 for pressurized air or fluid, respectively.
  • the high pressure oil passage 30, low pressure oil passage 40 and the passage 50 for pressurized air or fluid of the drill connection 51 communicates, respectively with each of such passages formed in the drilling head 1, when said drill connection 51 is connected with said drilling head 1.
  • Fig. 4 shows the construction of a connecting section of the connecting rod 60 in an enlarged scale.
  • the connecting rod 60 consists of a rod 60a and a rod 60b both having tubular configuration and almost the equal diameter and are jointed together with each other.
  • the connecting rod 60 comprises an outer pipe 61, a first inner pipe 61 a and a second inner pipe 61 b, the latter being concentrically positioned within said outer pipe 61.
  • An annular cavity defined between the outer pipe 61 and said first inner pipe 61 a is used as is passage for the pressurized air or fluid for discharging sludge or cuttings.
  • the connecting rod 60 of such construction is assembled with respect to its outer pipe 61 by jointing said rod 60a and 60b by tightning mating taper screws 62, while upper and lower half of the first inner pipe 61 a and those of the second inner pipe 61b, respectively, are connected by means of faucet joint at 63a and 63b.
  • Numeral 64 denotes an O-ring.
  • valve means shown in the drawing is of mechanical type but any other means such as electrical one or mechanical type of different construct can be used where occasion demands.
  • valve means shown in the drawing are attached at the joint ends of the 60a and 60b, namely, at each butt joint ends of the first inner pipe 61 a and the second inner pipe 61 b such that two mating pieces oppose each other.
  • annular valve seat 66a is threadedly attached along the inner periphery of the inner pipe.
  • annular valve seat 66b of the same configuration is threadedly attached to the inner axial end of the first inner pipe 61 b at the side of the rod 60b.
  • valve seats 66a and 66b project radially from the inner periphery of said first inner pipes 61 a and 61 b toward the center to constitute a tapered surface.
  • Stoppers 67a and 67b each faces with the valve seats 66a and 66b are fixed being fitted with the outer periphery of the second inner pipes 61 b in such a manner that said stoppers 67a and 67b do not prevent opening of the low pressure oil passage 40.
  • 68a and 68b denote lock rings for retaining the stoppers 67a and 67b.
  • Annular valve bodies 65a and 65b are slidably fitted around the outer periphery of the second inner pipes 61b, 61 b such that their outer peripheral faces project radially and outwardly to constitute a tapered face opposing said valve seats 66a and 66b.
  • 69a and 69b are seal packings attached to the valve bodies 65 and 65b, respectively.
  • Springs 70a and 70b are resiliently interposed between the stoppers 67a, 67b and valve bodies 65a and 65b such that said valve bodies are advanced so as to be contacted each other.
  • valve bodies 65 and 65b when said connecting rod 60 is not jointed together, are tightly contacted with the valve seats 66 and 66b, respectively, to block the low pressure oil passage 40.
  • valve bodies 65a and 65b are pushed one another such that their opposing end portion move away from the mating contact with valve seat 66a and 66b to allow communication between the two low pressure oil passages 40.
  • annular valve seat 71 a is threadedly attached, and similarly, a valve seat 71 b of the same configuration is attached at the inner periphery of the second inner pipe 61 b of the rod 60b.
  • valve seats 71 a and 71 b project from the inner periphery of said second inner pipes 61b, 61 b toward the center to constitute a tapered annular face.
  • a pair of stoppers 73a and 73b each having axially extending integral sleeve portion 72a and 72b, within each of which a valve body 74a and 74b each consisting of a shaft and a bevelled head is received being detachable in the axial direction.
  • a tip end portion of each of said valve body 74a and 74b is positioned at such a location that it slidably advances and engages with each of said valve seat 71 a and 71 b.
  • Said stoppers 73a and 73b are fixed and extend diametrically within the second inner pipes 61 b, 61 b but it is constructed so as not to prevent fluid communication of the high pressure oil passage 30.
  • 75a and 75b denote seal packings and 76a and 76b denote lock rings for retaining said stoppers 73a and 73b, respectively.
  • a pair of springs 77a and 77b are resiliently interposed between the rear face of each head of said valve body 74a and 74b and the stoppers 73a and 73b such that the valve bodies are urged advanced and opposedly contacted with each other.
  • valve bodies 74a and 74b engage with said valve seats 71 a and 71 b thereby to close the high pressure oil passage 30.
  • valve bodies 74a and 74b push one another to move tip end of each valve body away from the valve seats 71 a and 71 b to allow communication of the high pressure oil passage 30.
  • valve means 65 automatically opens to pass flow of the actuating oil, whereas it automatically closes to shut down flowing of the actuating oil.
  • a joint portion is formed so as to be connected with the drill connection 51.
  • this joint portion is constructed such that said inner pipes 61 b and 61 a threadably engages with the reduced diameter portion 56 and the intermediate diameter portion 57, respectively, both formed on the rear (upper) end of the drill connection 51, and the outer pipe 61 is also threadedly fitted to the enlarged diameter portion 58.
  • Figs. 5 and 6 show the construction of a rotary head 80 which consists of a rotary actuating means 81 and a shank rod 82 rotatably mounted on said rotary actuating means 81.
  • the rotary actuating means 81 consists of a driving means 84 fixed on a base 83 and a driven shaft 86 rotably journalled by a bearing 85 mounted on said base 83.
  • the driven shaft 86 can be rotated by rotating said driving means 84 by a power supplied by any suitable power source (not shown) as a drive gear 88 is meshed with driven gear 89 each of which is fixedly attached to driving shaft 87 of the driving means and said driven shaft 86, respectively.
  • the driven shaft 86 is a hollow shaft body, to the inner periphery of which the rear end of said shank rod 82 is fitted and engaged by a spline, thereby the shank rod 82 can be rotated about its longitudinal axis and also can be moved at a certain distance in axial direction.
  • a reduced diameter portion 90 At the front (lower side of the drawing) portion there formed a reduced diameter portion 90, an intermediate diameter portion 91 and an enlarged diameter portion 92 each of which threadedly engages with the second inner pipe 61 b, the first inner pipe 61 a and outer pipe 61, respectively, of the rod 60.
  • a high pressure oil passage 30 is formed within and along the central axis of the shank rod 82 and a plurality of low pressure oil passages 40 and a passage 50 for pressurized air or fluid are formed at radially and outwardly and coaxially spaced positions from said centrally located high pressure oil passage 30.
  • the high pressure oil passage 30 has its end opening at the end face of the reduced diameter portion 90, while each of the low pressure oil passage 40 and pressurized air or fluid passage 50 has openings at the end face of the intermediate diameter portion 91 and the enlarged diameter portion 92, respectively.
  • a swivel 96 provided with inlet port 93 for high pressure oil, inlet port 94 for low pressure oil and inlet port 95 for pressurized fluid is fitted around the outer periphery of the shank rod 82, thereby allow communication of each fluid under pressure to respective fluid passage.
  • each of said high pressure oil passage 30, low pressure oil passage 40 and pressurized air or fluid passage 50 communicate with respective passage formed in the rod 60.
  • the base 83 of the rotary head 80 is carried by a guide shell, not shown, in such a manner as capable of moving forward and backward and also is constructed to be imparted with suitable thrust force by a feeding device, not shown.
  • Figs. 7 and 8 show a pressure compensation device 100.
  • This pressure compensation device 100 comprises a coaxially disposed core tube 101 at both axial ends of which are fitted with auxilary joints 102 and 103.
  • auxiliary joints 102 and 103 are both annular or tubular shape which communicate to the core tube 101.
  • a high pressure oil passage 30 which further extends through the auxiliary joints 102 and 103.
  • each auxiliary joint 102 and 103 fitted with the core tube has a plug fitting end face 104 and 105 and each of the other end is formed to have flange 106 and 107.
  • a rib 108 having a height equal to the wall thickness of the core tube 101 both axial end of which are shaped to constitute thrust faces 109 and 110 and said core tube 101 is supported by said thrust face 109.
  • auxiliary joint 103 Inside of the auxiliary joint 103 is formed to have a recessed bore 111 with a large inside diameter to receive said core tube 101 and a bore 112 with a small inside diameter defined by a thrust face 111 by which said core tube is supported.
  • a protruding sleeve 113 is integrally formed for faucet joint member, while the flange 107 is partly undercut to attach there a gas supply pipe 114.
  • a gas vent 116 is formed, which opens at an annular groove 115 formed on the periphery of said auxiliary joint 103.
  • a plurality of orifices 117 are formed on the periphery of the core tube 101.
  • Diameter and number of the orifices can be suitably selected as desired.
  • the core tube 101 is connected through said auxiliary joints 102 and 103 to joints 118 and 119, respectively.
  • joint 118 is inserted into said auxiliary joint 102 up to the thrust face 110 thereof so as to be supported by said auxiliary joint 102.
  • Said joint 119 is fitted about the sleeve 113.
  • the joint 118 threadedly engages with the drilling head 1 at the forward end of its flange 120.
  • Rear part of said joint 118 is formed to become stepwisely smaller in diameter defined by stepped faces 121, 122 and 123.
  • a high pressure oil passage 30 Within the joint 118, there are formed a high pressure oil passage 30, a low pressure oil passage 40 and a passage 50 for pressurized air or fluid.
  • the passage 50 for pressurized air or fluid opens at the periphery of the joint 118 between the stepped faces 122 and 123.
  • the low pressure oil passage 40 opens at the periphery between the end face of the flange 120 and the auxiliary joint 102.
  • the joint 119 is formed at one end of its flange 124 to become stepwisely smaller in diameter defined by stepped faces 125, 126 and 127, while the other end of which is formed to become stepwisely smaller in diameter defined by stepped faces 128, 129, 130 and 131 so as to be used for connection with the rod 60.
  • a high pressure oil passage 30, low pressure oil passage 40 and a passage 50 for pressurized air or fluid are formed within the joint 119.
  • a tube proper 133 within which a bladder 132 is fixed is secured by screw thread to the auxiJiary joints 102 and 103.
  • the core tube 101 is connected to both the auxiliary joints 102 and 103.
  • Diaphragm fabricated of flexible synthetic resinous sheet or metallic foil can be used for said bladder 132.
  • fluid chambers 134 are formed between the core tube 101 and the bladder 132, similarly, gas chambers 135 are formed adjacent to said fluid chamber 134 between the bladder 132 and the tube proper 133.
  • the fluid chamber 134 communicates to the high pressure oil passage 30 within the core tube 101 through said orifices 117.
  • Rear part of the tube proper 133 is formed to have a thick wall portion within which a gas vent 136 is formed which communicates with the gas vent 116 and further to said gas chamber 135.
  • the gas chamber 135 is rendered in communication with the gas supply valve 114 when the tube proper 133 is assembled with the auxiliary joints 102 and 103.
  • Said gas supply valve 114 is exposed to the outside when the auxiliary joint 103 is removed from the joint 119 thereby permitting adjustment of the supplied gas.
  • An intermediate tube body 137 is faucet jointed to the stepped face 123 and peripheral surface between the stepped face and the end face of the joint 118 as well as to the stepped face 127 and the peripheral surface between the stepped face and the end face of the joint 119.
  • a low oil passage 40 is extendedly defined, which leads to those formed in the joints 118 and 119.
  • outer tube bodies 138 having outside diameter equal to the outside diameter of the flange portion 120 and 124 are threadedly fitted. Between the outer periphery of the intermediate tube body 137 and the inner periphery of the outer tube body 138, a passage 50 for pressurized air or fluid for discharging formed sludges are extendedly defined and communicate with those passages formed in the jionts 118 and 119.
  • fluid chamber 134 is acted by a pressure imparted by a gas filled in the gas chamber 135, thereby the fluid pressure in the high pressure oil passage 30 can be compensated through the orifices 117.
  • Excessive energy generated due to retraction of the piston 8 of the drilling head or switching of the valve can be stored within the pressurized fluid chamber 134 through the orifices 117.
  • Gas pressure within the gas chamber 135 changed (lowered by repeated operation can be adjusted by the gas supply valve 114.
  • the high pressure oil passage 30, the low pressure oil passage 40 and the passage 50 for pressurized air or fluid in the pressure compensation device 100 extend and communicate with those provided in the rod 60 and the drilling head 1.
  • this kind of joint means can be interposed between the drill connection 51 and 60 as well as between the two segments of the rod.

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  • Earth Drilling (AREA)

Claims (3)

1. Hydraulisch angetriebene Bohrvorrichtung im Bohrloch mit: einem Bohrhammer (1) im Bohrloch, der einen Zylinder (2) aufweist, in dem ein Kolben (8) verschiebbar gelagert ist, wobei der Kolben mittels Drucköl hinund herverschiebbar ist, das durch ein Richtungssteuerventil (20) gesteuert wird, das in dem Zylinder angeordnet ist, und der Kolben eine mittlere axiale Bohrung (50) für Druckluft oder hydraulisches Spülfluid zum Entfernen des Bohrmehls aufweist; einer Bohrstange (60), die den Bohrhammer (1) mit einem drehbaren Bohrkopf (80) verbindet, wobei die Bohrstange (60) aus mehreren Segmenten in Form von Rohren besteht, die einen Hochdruckölkanal (30) längs der mittleren Achse und einen Niederdruckölkanal (40) und einen Kanal (50) für das Spülfluid begrenzen, und zwar radial nach außen und konzentrisch zueinander um den Hochdruckölkanal (30) angeordnet; einem drehbaren Kopf (80), der außerhalb des Bohrloches angeordnet und mit der Bohrstange (60) verbunden ist, wobei der drehbare Kopf eine Schaftstange (82) mit Kanälen (30, 40, 50) aufweist, die mit zugeordneten Wirbeln (93, 94, 95) und mit dem Hochdruckölkanal (30), dem Niederdruckölkanal (40 und dem Kanal (50) für das Spülfluid in der Stange (60) in Verbindung stehen; und einem Antriebsmittel (81) zum Drehen der Schaftstange (82), der Bohrstange (60) und des Bohrhammers (1), dadurch gekennzeichnet, daß der Zylinder (2) des Bohrhammers (1) einen Hochdrückölkanal (30) und einen Niederdruckölkanal (40) aufweist, daß der Kolben (8) in dem Zylinder (2) eine vordere Druckfläche (15) und eine hintere Druckfläche (16) aufweist, die unterschiedlich groß sind, so daß der Zylinder (2) durch den Kolben in eine erste Hydraulikkammer (17) und eine zweite Hydraulikkammer (18) unterteilt wird, daß der Hochdruckölkanal (30) in dem Zylinder (2) sowohl mit der ersten Hydraulikkammer (17) als auch der zweiten Hydraulikkammer (18) in Verbindung steht und der Nieder-druckölkanal (40) in dem Zylinder (2) mit der zweiten Hydraulikdruckkammer (18) in Verbindung steht; daß das Richtungssteuerventil (20) eine vordere Stirnfläche (20a) und eine hintere Strinfläche (20b) mit verschiedener Größe aufweist und verschießbar in der zweiten Hydraulikkammer (18) angeordnet ist und dadurch eine Wirkungs- änderung des unter Druck stehenden Hydrauliköls auf die Druckflächen (15; 16) des Kolbens (8) gestattet, daß die hydraulische Bohrvorrichtung ferner aufweist eine Bohrverbindung (51) zwischen der letzten der Stangen (60) und dem Bohrhammer, so daß jeder der Kanäle in der Stange (60) mit jedem der entsprechenden Kanäle in dem Bohrhammer in Verbindung .bringbar ist, wobei die Bohrverbindung (51) einen auf der mittleren Längsachse ihres Körpers angeordneten und gebildeten Kanal (50) für Druckluft oder Druckfluid zum Entfernen von Schlamm, mehrere Hochdruckölkanäle (30) und Niederdruckölkanäle (40), die radial und nach außen um den Kanal (50) für die Druckluft oder das hydraulische Fluid herum angeordnet und ausgebildet sind und sich bis zu dem einen Endteil der Verbindung (51) erstreken, und einen zurückspringenden Teil aufweist, der an dem Endteil der Verbindung (51) angeordnet und ausgebildet ist, dessen Boden die Öffnung des Kanals (50) für Druckluft oder - fluid begrenzt, wobei sich die Hochdruckölkanäle (30) und die Niederdruckölkanäle (40) am äußeren Umfang des Körperteils der Verbindung (51) öffnen, as andere Ende der Bohrverbindung (51) so geformt ist, daß es einen Teil mit reduziertem Durchmesser aufweist, ein Teil mit mittlerem Durchmesser und ein Teil mit größerem Durchmesser von seiner Spitze an nacheinander enden und ein Hochdruckölkanal, der auf der mittleren Achse des Teils mit reduziertem Durchmesser ausgebildet ist, radial nach aussen gebogen ist, so daß er mit dem Hochdruckölkanal (30) in dem Körperteil in Verbindung steht; und Öffnungen und Schlitze, die mit dem Niederdruckölkanal (40) und dem Kanal (50) für Druckluft oder hydraulisches Fluid in dem Körperteil in Verbindung stehen, am äußeren Umfang des den mittleren Durchmesser aufweisenden Teils ausgebildet sind.
2. Bohrvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Segmente der Bohrstange (60) mit automatischen Stoppventilen (65) an der Verbindungsstelle jeder ihrer axialen Stirnflächen versehen sind, so daß sowohl der Hochdruckölkanal (30) als auch der Niederdruckölkanal (40) geöffnet werden kann, wenn das zugehörige Segment der Stange (60) angeschlossen ist.
3. Bohrvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Bohrvorrichtung ferner eine Durckkompensationseinrichtung (100) zwischen dem Bohrhammer (1) und der Stange (60) oder zwischen den Segmenten der Stange aufweist.
EP19790900104 1978-12-15 1980-07-01 Hydraulisch angetriebene bohrvorrichtung im bohrloch Expired EP0022865B1 (de)

Priority Applications (1)

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EP19790900104 EP0022865B1 (de) 1978-12-15 1980-07-01 Hydraulisch angetriebene bohrvorrichtung im bohrloch

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/JP1978/000057 WO1980001300A1 (en) 1978-12-15 1978-12-15 Hydraulically-driven downhole drill
EP19790900104 EP0022865B1 (de) 1978-12-15 1980-07-01 Hydraulisch angetriebene bohrvorrichtung im bohrloch

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EP0022865A1 EP0022865A1 (de) 1981-01-28
EP0022865A4 EP0022865A4 (de) 1981-01-28
EP0022865B1 true EP0022865B1 (de) 1984-08-01

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Publication number Priority date Publication date Assignee Title
DE3015696A1 (de) * 1980-04-24 1981-10-29 Salzgitter Maschinen Und Anlagen Ag, 3320 Salzgitter Hyraulische antriebsvorrichtung fuer ein schlagwerkzeug
FR2523202A1 (fr) * 1982-03-11 1983-09-16 Stenuick Freres Marteau a entrainement pneumatique du type " fond-de-trou "
SE444127B (sv) * 1984-06-25 1986-03-24 Atlas Copco Ab Tryckvetskedriven senkborrmaskin
US4711310A (en) * 1985-01-04 1987-12-08 Luen Lam M Rotary head
DE3807321C1 (de) * 1988-03-05 1989-05-11 Salzgitter Maschinenbau Gmbh, 3320 Salzgitter, De
DE4027414C1 (en) * 1990-08-30 1992-02-13 Komotzki, Michael, 4708 Kamen, De Tubular rock bore drill stem - has concentric channels for fluids and has spring-loaded control valves
WO1996020330A1 (en) * 1994-12-23 1996-07-04 Oy Winrock Technology Ltd Drilling apparatus
AT407184B (de) * 1996-05-20 2001-01-25 Boehler Pneumatik Internat Gmb Hydraulischer tieflochbohrhammer
JP3818438B2 (ja) 2001-12-14 2006-09-06 独立行政法人産業技術総合研究所 坑底駆動型パーカッションドリル
SE1050155A1 (sv) * 2010-02-18 2011-08-19 Wassara Ab Metod och anordning för provtagning av berggrund
GB2518383A (en) * 2013-09-19 2015-03-25 Mincon Internat Ltd Drill rod for percussion drill tool
CN107152252B (zh) * 2017-07-05 2023-03-24 唐山博皓工程技术有限公司 新型钻机水龙头
CN113445902B (zh) * 2021-08-11 2023-09-19 中煤科工集团重庆研究院有限公司 一种自闭式多通道高压钻杆
CN113445903B (zh) * 2021-08-11 2023-09-19 中煤科工集团重庆研究院有限公司 一种自闭式双油道钻杆连接结构

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EP0022865A4 (de) 1981-01-28

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