US3910358A - Horizontal earth boring machine - Google Patents

Horizontal earth boring machine Download PDF

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Publication number
US3910358A
US3910358A US485803A US48580374A US3910358A US 3910358 A US3910358 A US 3910358A US 485803 A US485803 A US 485803A US 48580374 A US48580374 A US 48580374A US 3910358 A US3910358 A US 3910358A
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Prior art keywords
pump
pressure
hydraulic
signal ports
motor
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Expired - Lifetime
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US485803A
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English (en)
Inventor
Norman A Martinek
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Koehring Co
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Koehring Co
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Priority to US485803A priority Critical patent/US3910358A/en
Priority to CA224,055A priority patent/CA1009223A/en
Priority to GB1468175A priority patent/GB1457493A/en
Priority to JP4827875A priority patent/JPS5550556B2/ja
Application granted granted Critical
Publication of US3910358A publication Critical patent/US3910358A/en
Assigned to KOEHRING COMPANY, A CORP. OF DE reassignment KOEHRING COMPANY, A CORP. OF DE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KOEHRING COMPANY A WI CORP.
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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
    • E21B44/00—Automatic control systems specially adapted for drilling operations, i.e. self-operating systems which function to carry out or modify a drilling operation without intervention of a human operator, e.g. computer-controlled drilling systems; Systems specially adapted for monitoring a plurality of drilling variables or conditions
    • E21B44/02—Automatic control of the tool feed
    • E21B44/06—Automatic control of the tool feed in response to the flow or pressure of the motive fluid of the drive
    • 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
    • E21B7/20—Driving or forcing casings or pipes into boreholes, e.g. sinking; Simultaneously drilling and casing boreholes
    • E21B7/201—Driving or forcing casings or pipes into boreholes, e.g. sinking; Simultaneously drilling and casing boreholes with helical conveying means

Definitions

  • horizontal earth boring machines are usually of the portable type, they employ internal combustion engines as the power source.
  • the positioning of such engines in the confines of a ditch results not only in a high noise level, but also can be a health hazard to an operator working adjacent to the engine.
  • complex exhaust and engine muffler arrangements have been employed which add to the complexity and size of the earth boring apparatus and make it difficult to properly locate it in a working position.
  • Another solution to the problem has been to use a pair of hydraulic pumps, one for driving a hydraulic motor which rotates the earth boring auger and the other to supply hydraulic fluid for reciprocating hydraulic actuators which acts to advance or retract the auger as it is rotated in the earth.
  • Both of the pumps are driven by internal combustion engines which can be positioned remotely from the earth boring auger and, as a consequence, can be positioned at ground level above the ditch in which the operator is located.
  • This invention contemplates the use of a single hydraulic pump to furnish pressure fluid to hydraulic motor means to rotate an earth boring auger and to reciprocate the auger using controls which are so arranged that demands in excess of the capacity of the pump to rotate or to advance the auger, or both, are rejected and the capacity of the pump, and therefore the capacity of the internal combustion engine driving the pump, cannot be exceeded.
  • the single hydraulic pump utilizes controls responsive to the higher of the load pressures required to either rotate the auger or to advance the auger which places a limit on the displacement of the pump and, consequently, on its output.
  • FIG. 1 is a perspective view showing an earth boring machine embodying the present invention, located in a working position with the power source located remotely from the working position;
  • FIG. 3 is a top view of the machine shown in FIG. 2;
  • FIG. 4 is a sectional view taken on line 4-4 in FIG. 3;
  • FIG. 5 is a schematic diagram of the hydraulic circuit used to control the earth boring machine.
  • FIG. 6 is a curve depicting the characteristics of the pump employed to supply power to the earth boring machine.
  • a preferred embodiment of the invention includes a horizontal earth boring machine 10 which is operated to rotate an auger 12 and to advance the auger while it is being rotated to form a bore in the earth.
  • the machine can also be used to advance a casing member 14 which forms a lining to the bore formed by the auger l2 and serves to convey the material cut by the auger rearwardly from the bore which is being formed.
  • the horizontal earth boring machine includes a base structure 16 which is made up of a basic track section 18 and one or more extension track sections 20 and 22.
  • the basic track section 18 includes a pair of generally channel-shaped rail members 24 and 26 which are held apart in parallel spaced relationship to each other by a plurality of cross braces 28 which may be rigidly attached to the rails 24 and 26 as by welding or the like.
  • the cross braces 28 also act to engage the ground and to support the rails generally horizontally and parallel to the axis of rotation of the auger l2 and to the bore which is to be formed in the earth.
  • the cross members 28 at opposite ends of the base structure 18 are provided with lift rings 30 to which lifting equipment may be connected to raise and lower the base track structure relative to the ditch.
  • the rear or left end of the basic track structure 18, as viewed in FIGS. 2 and 3, is provided with a cross member 32 hich acts as a backstop and the other, or right end of the basic track structure 18, is provided with connecting plates 34 associated with the tracks 24 and 26 for securing the basic track structure 18 to an extension track structure 20.
  • the extension track structure 20 also includes a pair of tracks 24 and 26, cross members 28 and lift rings 30 by which the extension section 20 may be raised and lowered relative to the ditch in which the machine is to operate.
  • connecting plates 34 may be located at the joint between the extension track sections 20 and 22 to secure them relative to each other.
  • a carriage structure indicated generally at 36 is disposed on top of the tracks 24 and 26 for longitudinal sliding movement relative to the latter.
  • the carriage structure 36 includes a pair of anchor plates 38 associated with the track 24 and a similar pair of anchor plates 40 associated with the track 26 which serve to secure the carriage 36 against vertical movement relative to the tracks 24 and 26.
  • the carriage 36 supports a reversible hydraulic motor 42 which serves to drive a gear reduction unit 44 which in turn rotates the auger 12.
  • the carriage structure 36 is moved longitudinally of the tracks 24 and 26 by means of a pair of hydraulic actuators 48, each of which has a cylinder portion pivotally connected to the carriage 36 and a rod portion 52 pivotally connected to an anchor structure 54.
  • the anchor structure 54 extends transversely to the tracks 24 and 26.
  • One end of the anchor structure 54 is provided with a pair of pins 56 which are adapted to be inserted and retracted from selected, adjacent pairs of holes 58 in the track 24.
  • the other end of the anchor structure 54 is provided with pins 56 adapted to be inserted into selected ones of pairs of openings 58 in the track 26.
  • Pins 56 are rigidly connected to a pin bracket 63 and are adapted to be moved vertically into and out of the openings 58 by means of a lever 64 which serves to raise and lower the pin bracket 63 and the pins 56 through means of links 66.
  • the hydraulic actuators 48 are of the double-acting type, and the transmission of hydraulic fluid to one end of the actuators 48 causes extension of the rods 52 so that the carriage structure is moved to the right relative to the anchor structure 54 as viewed in FIGS. 2 and 3. Similarly, the transmission of hydraulic fluid to the left end of the hydraulic actuators 48 serves to retract the rods 52 so that the carriage structure 36 moves to the left. Such extension and retraction of the piston rods 52 serves to move the carriage structure 36 relative b the anchor structure 54 to either advance or retract the auger 12.
  • the carriage structure 36 is also provided with a casing pusher which serves to engage one end of the casing 14 and to hold it nonrotatably relative to the auger 12.
  • the casing pusher 70 serves to advance the casing 14 together with the auger 12 so that, as a bore is formed in the earth, the casing 14 lines the bore.
  • the casing 14 also acts to convey the material cut by the auger 12 from the open end of the casing 14 toward the casing pusher from which it is discharged by means of rotating paddles 71.
  • a pair of generally vertical bar structures 76 are disposed at opposite sides of the carriage 36.
  • the bar members 76 serve as a lift cage by which the carriage member may be lowered into a ditch or raised from a ditch by lifting machinery such as a crane.
  • the carriage member 36 Disposed on the bar member 76 are control levers 78 and 80 operating valve controls to be described.
  • the carriage member 36 also includes an operators platform 82 at which an operator may position himself for operation of the valve control levers.
  • the platform is positioned rearwardly of the direction of auger advance for good visibility of auger operation.
  • the hydraulic motor 42 and the hydraulic actuators 48 receive hydraulic fluid which is controlled manually by the operator located on the platform by manipulation of a pair of valve operating levers 78 and 80.
  • the Iever 78 is used to control a directional valve mechanism regulating the direction of rotation and speed of the motor 42 and the lever 80 is used to similarly control the operation of the hydraulic actuators 48 to advance or retract carriage 36.
  • the power assembly 86 includes a base frame structure 88 in which an internal combustion engine 90 is mounted to drive a hydraulic pump 92 which is indicated in FIG. 5.
  • the base structure 88 also serves to support a battery 96, a fuel tank 98 and a reservoir 100 for the hydraulic fluid.
  • a lift bar 101 is rigidly secured to the base structure 88 so that all of the components mounted thereon may be lifted and positioned by means of a crane or the like at some point adjacent to the machine 10 but preferably at ground level and out of the ditch in which the machine 10 is being operated.
  • the hydraulic pump 92 is connected to a control valve 102 manually actuated by lever 78 and a control valve 104 manually actuated by the lever 80 by means of a delivery line 106.
  • a line 108 serves as a return line, and a line 110 serves as a control signal line.
  • FIG. 5 schematically illustrating the closed-center hydraulic system employed in operating the horizontal earth boring machine 10, the variable displacement pump 92 driven by the internal combustion engine 90 receives hydraulic fluid from the reservoiry100 through a line 112 for delivery by the pump 92 through the line 106 to branch supply lines 116 and 118.
  • the supply line 116 delivers hydraulic fluid to a control circuit which is utilized to control the doubleacting hydraulic actuators 48 by manual movement of the control lever 80.
  • the supply line 118 delivers hydraulic fluid to a control circuit for controlling the direction and speed of the hydraulic motor 42 which rotates the auger 12.
  • movement of the control lever 80 controls the directional four-way control valve 104. Movement of the control lever 80 to the left, as viewed in FIG. 5, is effective to supply hydraulic fluid from the line 116 to a pressure compensating valve 122 and through a line 124 to the directional valve 104.
  • the valve 104 controls the flow of fluid to a line 126 to the head end of both of the actuators 48, forming part of the hydraulic actuators 48. Delivery of hydraulic fluid under pressure in this manner causes the hydraulic actuator rods 52 to move to the left, as seen in FIG. 5 and also in FIG. 2, to advance the carriage 36 to the right in an earth boring direction.
  • hydraulic fluid is ejected from the rod ends of the cylinders 50 through line 130 to the control valve 104 from which it passes to the return line 108 and back to the reservoir 100.
  • Movement of the control lever 80 to the right to move valve 104 from its neutral position shown in FIG. 5 causes hydraulic fluid to be delivered to the valve 104 and through the line 130 to the rod end of the cylinders 50, causing the piston rods 52 to move to the left relative to the cylinders 50. At the same time fluid is ejected through the lines 126 to the control valve 104 and to the return line 108 back to the reservoir 100.
  • the working pressure in either of the lines 126 or 130 which is being delivered to the hydraulic actuators 48 also is made available in a pilot signal line 134.
  • the pilot control pressure in the line 134 is made available to control the pressure compensating valve 122 through a line 136 and also is made available to a pressure relief valve 138 by way of hydraulic line 140.
  • the pressure relief valve 138 is connected to the return line 108 by way of a line 142.
  • the pressure relief valve 138 serves to relieve the pressure in the working end of the hydraulic actuators 48 when the pressure exceeds some predetermined maximum which, for example, can be to the order of 2,300 psi.
  • the hydraulic fluid pressure in the pilot signal line 134 from the hydraulic actuator control valve 104 communicates through a one-way check valve 144 to a line 146 which communicates with a signal port 148 associated with the pump 92 and its controls.
  • hydraulic fluid is delivered through the line 118 through a presssure compensating valve 150 which is similar to the pressure compensating valve 122. Hydraulic fluid from the pressure compensating valve 150 is delivered to a control valve 102 through a line 154 and is returned through a line 156 to the return line 108 and to the reservoir 100.
  • the valve 102 is identical to the directional four-way valve 104 and movement of the control lever 78 to the right causes delivery of hydraulic fluid from the line 154 to a line 158 to cause rotation of the motor 42 in one direction.
  • hydraulic fluid is exhausted from the motor 42 through a return line 160, through the valve 152 and to the line 156 communicating with the return line 132 and the reservoir 100.
  • the movement of the control lever 78 to the left causes delivery of the hydraulic fluid from the line 154 through the valve 102 and to the line 160 causing the motor 42 to rotate in the opposite direction. Fluid from the motor 42 is returned by way of the lines 158, 156 and 108 to the reservoir 100.
  • the working pressure delivered through the valve 102 to the motor 42 is made available in a pilot signal line 162 whenever the control valve 102 is moved to the left or to the right of its neutral or center position. Pilot signal pressure from the line 162 is made available to control the pressure compensating valve 150 through a line 164.
  • a pressure relief valve 170 is disposed between the supply line 118 and the return line 108 to limit the maximum pressure which can be made available to the motor 42, for example, 3000 psi.
  • the check valve 144 associated with the control circuit for the hydraulic actuators 48 and the check valve 166 associated with the control circuit for the hydraulic motor 42 are so arranged that the higher of the working pressures existing in either the motor 42 or in the'actuators 48 is made available at the signal port 148.
  • the pump 92 is a pressure compensated variable displacement pump 92 of the axial piston type which includes a swashplate indicated at 174 the angle of which is under the control of a pump servo piston 176. Increase of piston stroke in response to increase of signal pressures results in an increase in the swashplate angle and a corresponding increase ,in displacement of the pump 92.
  • the pump servo piston 176 is under the control of a pressure compensating circuit designated generally at 178 which responds to a differential in pressure at the signal port 148 and in an output pressure signal line 180 communicating with the output line 106 from the pump 92.
  • the circuit 178 operates to maintain the pressure differential at signal port 148 and signal line 180 at some predetermined constant level which could be selected, for example, to be 200 psi. If the working pressure downstream of the valves 102 and 104 and at the signal port 148 changes, the position of the pump servo piston 176 changes to regulate the displacement of the pump 92 to maintain a constant pressure differential at the signal port 148 and the high pressure signal line 180.
  • the operator of the earth boring machine 10 can sense only the velocity of flow due to his control of the valves 102 and 104 but cannot sense the magnitude of the pressure demanded by the load.
  • the control circuit 178 is provided with a horsepower limiting control indicated at 184 which functions automatically to reject any requirement which is made manifest by operation of the valves 102 and 104 to require more power than is available in the system.
  • the horsepower limiting device 184 is biased by a spring 186 which is grounded against an arm 188 connected to the swashplate 174.
  • the power limiter spring is relaxed requiring less load pressure in the line 180 to overcome the force generated by the spring 186, and the load pressure at which the horsepower limiting device shifts is inversely proportional to the displacement of the pump 92.
  • the control circuit also includes a valve 192 which is connected to the system so that the pump control differential pressure at the signal port 148 and in the high pressure signal line 180 act across the spool urging it to the right as seen in FIG. 5. Since the control differential is maintained at a constant level during operation, the force on the spool due to the pressure differential remains constant throughout the range of operation.
  • a biasing spring 194 is employed to keep the spool in its normal position. When the directional control valves 102 and 104 are in their neutral position, the output of the pump 92 is blocked and pressure in the high pressure signal line 180 will rise.
  • This pressure acts on the valve 192 and the rate of the spring 194 can be selected to require an increase in pressure above the normal control differential pressure at the signal part 148 and the high pressure line 180 to overcome the spring load.
  • the valve 192 shifts to the left to communicate a fixed bypass orifice 196 with a line 198 to the reservoir 100.
  • the orifice 196 is selected to be only small enough to maintain enough pressure drop across the orifice to keep the valve 192 shifted. Since the valve pressure drop is also the pump control differential, the pump 92 is commanded to a minimum stroke at a low working pressure.
  • the pump could be controlled to deliver one or two gallons of fluid per minute at a pressure of 400 to 500 psi.
  • FIG. 6 illustrates the operating characteristics of the pump 92 in terms of hydraulic fluid flow designated by the coordinate Q and the pressure which is designated by the coordinate P.
  • the variable displacement pump is designed and controlled to deliver up to a maximum of 21 gallons per minute and up to a pressure of 2000 psi which is designated by that portion of the characteristic curve between points A and B.
  • Maximum flow to either of the actuators 48 or to the motor 42 is a function of the fluid capacity of the pump 92 and the maximum metering characteristics of valves 102 and 104 determined by the stroke of the valves from their neutral position.
  • the maximum horsepower output of the pump which is a product of flow and pressure, is maintained constant by means of the horsepower limiting valve 184 which modifies the displacement of the pump 92 as the working pressure at the signal port 148 increases.
  • the maximum pressure of the system occurs at point C at which point the pressure relief valve 170 in the motor circuit opens.
  • the pressure at this point could be 3000 psi with fluid flow to the order of 10 or I 1 gallons per minute.
  • the point E on the curve denotes the condition in which both of the directional control valves 102 and 104 are in their neutral position and the pump 92 is restricted to limit flow at a relatively moderate pressure, for example, one to two gallons per minute at 400 to 500 psi.
  • the maximum torque required to drive the pump 92 is determined by the load occurring at point B at which the maximum flow of the system occurs at its highest pressure.
  • the engine 90 to drive the pump 92 is selected to accommodate this load so that when it occurs the engine will not overload and stall.
  • the horizontal earth boring operation is begun by placing the machine 10 in a ditch adjacent to the location where the bore is to be formed in the earth and by placing the power assembly 86, preferably to one side of the ditch, in a remote location.
  • the machine 10 and the power assembly 86 are then connected by means of the delivery line 106 the return line 108 and the signal line 110.
  • the differential in pressure at the port 148 and in the output line 106 will adjust the pump 92 to deliver hydraulic fluid to the line 106 at a pressure approximately 200 psi higher than the pressure in the signal line 146 which represents the working pressure downstream of the valve 102.
  • the control lever 80 may be moved to the right, as seen in FIG. 5, to cause advance of the carriage 36 together with the auger 12. If the carriage 36 is advanced at a speed requiring more than the remaining fluid of the system and at a pressure or load which develops a working pressure less than the working pressure of the motor 42, the flow of fluid to the motor 42 will be restricted and, consequently, the augers rotation will be retarded. Slowing of rotation of the auger 12 will be apparent to the operator, and, if desired, he may retard the demanded speed of operation of the motor 40 or of the actuators 48 to make fluid flow available in the other of these circuits.
  • valves 102 and 104 are simultaneously stroked to utilize the full flow of the pump and to create a working pressure at one of the functions, for example the motor 42, in excess of 2000 psi, the horsepower control functions to maintain the maximum output or horsepower, which is the product of flow and pressure, at a relatively constant value as depicted in the curve of FIG. 6 between points B and C. As the working pressure increases, the flow decreases. At the point C, for example, the horsepower output of the pump can be equal to or slightly less than the output at point B and the engine driving the variable displacement pump 92 will not be overloaded or stall.
  • valves 102 and 104 have been disclosed to control two different functions of the earth boring machine 10, it should be apparent that additional functions and control circuits can be added and operated independently of the other control circuits.
  • a horizontal earth boring machine has been provided in which the earth boring functions, such as rotation of an auger and advancing of the auger into a bore which is to be formed, may be conducted at one location, for example in a ditch, and the power source for conducting such functions may be located remotely and to one side and out of the ditch.
  • the functions, such as rotating the auger and advancing the auger or bore casing, can be conducted independently or simultaneously under the control of an operator located close to the boring operation and remote from the power source.
  • a horizontal earth boring machine comprising:

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  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
US485803A 1974-07-05 1974-07-05 Horizontal earth boring machine Expired - Lifetime US3910358A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US485803A US3910358A (en) 1974-07-05 1974-07-05 Horizontal earth boring machine
CA224,055A CA1009223A (en) 1974-07-05 1975-04-08 Horizontal earth boring machine
GB1468175A GB1457493A (en) 1974-07-05 1975-04-10 Horizontal earth boring machine
JP4827875A JPS5550556B2 (enrdf_load_stackoverflow) 1974-07-05 1975-04-22

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US485803A US3910358A (en) 1974-07-05 1974-07-05 Horizontal earth boring machine

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JP (1) JPS5550556B2 (enrdf_load_stackoverflow)
CA (1) CA1009223A (enrdf_load_stackoverflow)
GB (1) GB1457493A (enrdf_load_stackoverflow)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3995700A (en) * 1975-10-14 1976-12-07 Gardner-Denver Company Hydraulic rock drill system
US4042043A (en) * 1974-03-27 1977-08-16 The Richmond Manufacturing Company Portable earth boring machine
US4059163A (en) * 1976-08-16 1977-11-22 Caterpillar Tractor Co. Mine drilling apparatus and method
EP0300080A1 (de) * 1987-07-25 1989-01-25 Ing. G. Klemm Bohrtechnik GmbH Überlagerungsbohrvorrichtung
US5004055A (en) * 1989-04-14 1991-04-02 Meta-Probe Inc. Vibratory core drill apparatus for the recovery of soil or sediment core samples
US5058688A (en) * 1989-04-14 1991-10-22 Meta-Probe Inc. Convertible vibratory or rotary core drill apparatus
WO1992019837A3 (de) * 1991-04-25 1993-02-18 Klemm Bohrtech Erdbohrgerät
US5964306A (en) * 1998-03-03 1999-10-12 Barbera; Leo J. Auger earth boring machine with improved efficiency and safety
US6736219B1 (en) 2002-12-10 2004-05-18 William A. White Underground horizontal boring apparatus
US6883620B1 (en) * 1999-12-23 2005-04-26 Montabert S.A. Device for hydraulic power supply of a rotary apparatus for percussive drilling
WO2005102597A1 (en) * 2004-04-13 2005-11-03 White William A Underground horizontal boring apparatus
WO2006135303A1 (en) * 2005-06-17 2006-12-21 Atlas Copco Rock Drills Ab Method and system for controlling power consumption during rock drilling and rock drilling apparatus incorporating such a system
US7497274B1 (en) * 2006-01-24 2009-03-03 Astec Industries, Inc. Hydraulic fluid tank for drilling machine
US20100065331A1 (en) * 2008-09-11 2010-03-18 Harrison Stuart Ronald Auger boring machine
EP2514911A1 (de) * 2011-04-20 2012-10-24 Klemm Bohrtechnik GmbH Bohrgerät
US20130000988A1 (en) * 2011-06-30 2013-01-03 Bauer Maschinen Gmbh Drilling unit
WO2015132204A1 (en) 2014-03-03 2015-09-11 Hpm - Hydraulic Performance Machines Srl Drilling machine with optimized tool unloading system
CN108431360A (zh) * 2016-01-06 2018-08-21 伊索德里尔股份有限公司 使用动态可调节可变排量泵的井下动力转换和管理

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Publication number Priority date Publication date Assignee Title
JPS5324696A (en) * 1976-08-19 1978-03-07 Furukawa Kogyo Kk Device for controlling feeding speed of drilling machine
JPS5879835U (ja) * 1981-11-18 1983-05-30 中川電化産業株式会社 タイマ
JPS6117692A (ja) * 1984-07-04 1986-01-25 東京瓦斯株式会社 横穴掘削装置
GB2239276A (en) * 1989-12-18 1991-06-26 Int Pipe Replacement Systems L An hydraulic, horizontal thrust, rotary drilling machine
CN103470181B (zh) * 2013-09-23 2015-07-08 阿特拉斯科普柯(南京)建筑矿山设备有限公司 凿岩装置推进力单向延迟响应方法及实现该方法的装置

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US3107738A (en) * 1959-01-20 1963-10-22 Gilbert M Turner Hydraulically operable horizontal drilling apparatus
US3117420A (en) * 1962-05-24 1964-01-14 New York Air Brake Co Hydrostatic transmission
US3118509A (en) * 1959-06-24 1964-01-21 Salem Tool Co Trench drill
US3191382A (en) * 1964-06-29 1965-06-29 New York Air Brake Co Hydraulic system
US3429123A (en) * 1967-08-29 1969-02-25 Leblond Mach Tool Co R K Speed control system
US3587755A (en) * 1969-08-11 1971-06-28 Emmet G Slusher Earth boring apparatus

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Publication number Priority date Publication date Assignee Title
US2867091A (en) * 1955-12-07 1959-01-06 British Messier Ltd Hydraulic systems
US3107738A (en) * 1959-01-20 1963-10-22 Gilbert M Turner Hydraulically operable horizontal drilling apparatus
US2932948A (en) * 1959-03-19 1960-04-19 American Brake Shoe Co Horsepower limiting device
US3118509A (en) * 1959-06-24 1964-01-21 Salem Tool Co Trench drill
US3117420A (en) * 1962-05-24 1964-01-14 New York Air Brake Co Hydrostatic transmission
US3191382A (en) * 1964-06-29 1965-06-29 New York Air Brake Co Hydraulic system
US3429123A (en) * 1967-08-29 1969-02-25 Leblond Mach Tool Co R K Speed control system
US3587755A (en) * 1969-08-11 1971-06-28 Emmet G Slusher Earth boring apparatus

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4042043A (en) * 1974-03-27 1977-08-16 The Richmond Manufacturing Company Portable earth boring machine
US3995700A (en) * 1975-10-14 1976-12-07 Gardner-Denver Company Hydraulic rock drill system
US4059163A (en) * 1976-08-16 1977-11-22 Caterpillar Tractor Co. Mine drilling apparatus and method
EP0300080A1 (de) * 1987-07-25 1989-01-25 Ing. G. Klemm Bohrtechnik GmbH Überlagerungsbohrvorrichtung
US5004055A (en) * 1989-04-14 1991-04-02 Meta-Probe Inc. Vibratory core drill apparatus for the recovery of soil or sediment core samples
US5058688A (en) * 1989-04-14 1991-10-22 Meta-Probe Inc. Convertible vibratory or rotary core drill apparatus
WO1992019837A3 (de) * 1991-04-25 1993-02-18 Klemm Bohrtech Erdbohrgerät
US5964306A (en) * 1998-03-03 1999-10-12 Barbera; Leo J. Auger earth boring machine with improved efficiency and safety
US6883620B1 (en) * 1999-12-23 2005-04-26 Montabert S.A. Device for hydraulic power supply of a rotary apparatus for percussive drilling
US6736219B1 (en) 2002-12-10 2004-05-18 William A. White Underground horizontal boring apparatus
WO2005102597A1 (en) * 2004-04-13 2005-11-03 White William A Underground horizontal boring apparatus
WO2006135303A1 (en) * 2005-06-17 2006-12-21 Atlas Copco Rock Drills Ab Method and system for controlling power consumption during rock drilling and rock drilling apparatus incorporating such a system
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CA1009223A (en) 1977-04-26
GB1457493A (en) 1976-12-01
JPS5550556B2 (enrdf_load_stackoverflow) 1980-12-18
JPS516303A (enrdf_load_stackoverflow) 1976-01-19

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