EP0391161A2 - Dispositif automoteur de forage par battage - Google Patents

Dispositif automoteur de forage par battage Download PDF

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Publication number
EP0391161A2
EP0391161A2 EP90105472A EP90105472A EP0391161A2 EP 0391161 A2 EP0391161 A2 EP 0391161A2 EP 90105472 A EP90105472 A EP 90105472A EP 90105472 A EP90105472 A EP 90105472A EP 0391161 A2 EP0391161 A2 EP 0391161A2
Authority
EP
European Patent Office
Prior art keywords
percussion
boring device
percussion piston
piston
ram boring
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.)
Withdrawn
Application number
EP90105472A
Other languages
German (de)
English (en)
Other versions
EP0391161A3 (fr
Inventor
Franz-Josef Püttmann
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.)
Tracto Technik GmbH and Co KG
Original Assignee
Tracto Technik GmbH and Co KG
Tracto Technik Paul Schmidt Spezialmaschinen KG
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
Application filed by Tracto Technik GmbH and Co KG, Tracto Technik Paul Schmidt Spezialmaschinen KG filed Critical Tracto Technik GmbH and Co KG
Publication of EP0391161A2 publication Critical patent/EP0391161A2/fr
Publication of EP0391161A3 publication Critical patent/EP0391161A3/fr
Withdrawn legal-status Critical Current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
    • E21B4/10—Down-hole impacting means, e.g. hammers continuous unidirectional rotary motion of shaft or drilling pipe effecting consecutive impacts
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/26—Drilling without earth removal, e.g. with self-propelled burrowing devices

Definitions

  • the invention relates to a self-propelled ram boring device, in particular for the production of earth bores, with a percussion head which is arranged on the propulsion side of a cylindrical housing and can be acted upon by a percussion piston with ram pounding impulses, the percussion piston being drivable in pulsating, translatory working strokes by means of an energy carrier which can be fed into the device.
  • a ram boring machine of the type mentioned is preferably used to lay supply lines such as those for water supply and drainage, electrical energy or telephone connections, for example under streets or sidewalks, without having to dig up the road surface or sidewalks for this purpose.
  • the ram boring machine moves through the soil by displacing and compacting it as it advances and creating an earth channel into which the supply line can be easily inserted.
  • the ram boring machine can be connected at the rear end to a connecting part or a coupling for fastening a pulling tube.
  • a pipe to be laid can also be pulled in by means of a pulling cable inserted into the earth channel.
  • the device must be supplied with lubricant during operation. This is done by switching on a mist oiler in the compressed air supply, while at the same time paying attention to the correct metering of an oil mist and to the use of a certain oil quality, especially at different working temperatures.
  • the compressed air In winter, for example, the compressed air is heated by another additional heat exchanger in order to avoid condensation with ice formation and thus malfunctions. The pressure and quantity of the working medium compressed air are carefully observed so that the risk of damage due to excessive demands on the material is excluded.
  • the impact numbers are largely influenced set limits. These difficulties can occur occasionally if the device is used as a soil displacement hammer in very different types of soil, for example with more or fewer stone inclusions. Furthermore, it is also not possible to carry out targeted single strikes, for example when the ground displacement hammer enters the ground.
  • a pneumatically driven ram boring machine In difficult ground conditions, for example with rock inclusions, a pneumatically driven ram boring machine, the tip of which only works with translational ramming, can be pushed out of its working direction when striking stronger obstacles.
  • the invention has for its object to provide a self-propelled ram boring device of the type mentioned, which is improved and further developed compared to the prior art.
  • the device should be able to pierce rock inclusions and rock as well as hard ground without impact from the working direction once struck, whereby the speed of advance and the number of impacts should be infinitely adjustable with simple means and the generation of single impacts, for example when entering the Soil that should be easily possible.
  • the solution to the above problem consists in a self-propelled ram boring device of the type mentioned with or without a movable impact tip in that a spring is used to drive the impact piston, which is periodically tensioned and relaxed.
  • the spring is preferably tensioned by a pneumatically or hydraulically driven motor.
  • the ram boring device according to the invention device can have a rotary drive with at least one cam mechanism that can be driven by this, and the percussion piston can be designed with a helical guide groove or a helical guide surface as part of the cam mechanism.
  • the number of blows can advantageously be set continuously via the speed of the rotary drive. This has a particularly positive effect when the device is used as a soil displacement hammer in different types of soil.
  • the ram boring device in such a way that it also works as an impact drilling device if, for example, the impact head is connected to the rotating impact piston via the drive shaft or a driving shaft.
  • This has the advantage that larger stone inclusions, due to the impact drilling effect of the ram boring device, do not pose any problems.
  • the impact head can be equipped with a rock drill bit for better effect in stony soils.
  • the device can also be equipped with a beveled head, according to the technical teaching according to DE-PS 30 27 990, in order to be able to drive curved tracks in the ground.
  • a beveled head with such a beveled head, a straight-line run can be achieved with the aid of a targeted rotational movement.
  • the device is controlled in a certain direction according to the inclined surface on the head.
  • the motor can preferably be designed as a hydraulic motor and connected to a supply and discharge line for a hydraulic energy source, preferably for pressurized water.
  • the advantage of a hydraulic mode of operation of the motor lies in the fact that it can exert high torques in a construction in a small space and can be driven continuously at a predeterminable speed within its speed range.
  • the use of pressurized water instead of pressurized oil is also advantageous in order to prevent any damage to the environment caused by oil leaks.
  • the rotary drive with a motor located outside the device can be connected to the cam mechanism via a preferably flexible transmission shaft in a rotationally locking, power-transmitting connection.
  • the rotary drive has a drive shaft arranged in the housing axis, which on the one hand is in a rotationally locked connection with the motor or the transmission shaft and on the other hand engages in a rotationally locked manner in the cam mechanism with axial movement play.
  • the percussion piston is driven by the drive motor, which is hydraulic, pneumatic or electric can be set in rotation as well as in translation via the drive shaft.
  • the percussion piston is connected on the one hand in a rotationally locking manner and on the other hand freely movable in the axial direction to the drive shaft and has a guide groove cut helically in its cylindrical circumferential area with a helical pitch, and a guide element projecting radially inward from the housing wall engaging and arranged in this.
  • the guide groove has an area which extends helically in approximately 360 degrees and a return groove area which connects the beginning and end thereof and which is essentially linear in the axial direction or steeply helical by a few degrees.
  • the percussion piston is supported with its end opposite the impact surface against a drive spring which acts as an energy store during its return stroke.
  • the guide element is at the beginning of the groove curve when the percussion piston begins to rotate.
  • the guide element runs through the helical region of the groove curve, the drive spring being more and more pretensioned by the translational movement of the percussion piston thereby resulting in the storage of impact energy, until the guide element has reached the end of the groove curve.
  • the percussion piston moves under the effect of the restoring force of the drive spring abruptly translationally against the impact surface of the striking head through the return groove area through to the beginning of the groove curve again.
  • the device according to FIG. 1 has a housing 6 with two housing parts 6.1 and 6.2 screwed together and with a housing end 6.4.
  • the drive motor 7 is clamped between the housing end 6.4 and a shoulder 43 formed on the inner housing wall 16.
  • the feeds 8 and 9 are provided for energy supply. These can be lines for a hydraulic or pneumatic working medium or for electrical energy.
  • the rotary drive 2 comprises the drive motor 7, the drive shaft 11 and, in the present embodiment Example, the rotatably arranged percussion piston 1 with the cam mechanism 3.
  • the drive shaft 11 is on the one hand in a rotational connection with the motor 7 and, on the other hand, engages with the cam mechanism 3 in a rotationally locked manner with axial movement play.
  • the shaft 11 engaging in a bore 24 of the percussion piston 1 with an axial sliding spring and the bore 24 with an axial spring groove, so that these elements can slide into one another in the axial direction but are non-rotatably connected to one another.
  • the drive spring 17 is clamped between the motor 7 and the rear end of the percussion piston 1.
  • the percussion piston 1 has a guide groove 4 cut into its cylindrical circumferential region, into which a guide element 12 protruding radially inward from the housing wall 16 engages.
  • This guide groove 4 has a region 4.1 which extends helically in approximately 360 degrees and a groove region 4.2 connecting its start 13 and end 14. This is essentially rectilinear in the axial direction or has a steep helical shape by a few degrees.
  • the percussion piston 1 When the percussion piston 1 rotates clockwise, viewed from the direction of the drive shaft 11, it screws back against the spring by the axial distance between the groove start 13 and the groove end 14. As soon as the guide element 12 has reached the groove end 14, the drive spring 17 swings the percussion piston 1 in front of and against the impact surface 15 of the striking head 18.
  • the guide element 12 passes in the axial direction of the return groove area 4.2 from the groove end 14 to the groove start 13. This process repeats itself periodically every full revolution by 360 o . If at the high speed of the percussion piston 1 rushing against the impact surface 15, the If the width of the return groove area 4.2 is not sufficient to ensure an uninterrupted continuation of the rotary movement of the piston, the return groove area 4.2 can also be designed to be steep-helical.
  • the striking head 18 is also displaceable in the axial direction at the front end of the housing part 6.2 and is supported against the striking direction via the striking head spring 31 on the housing end part 6.3 from.
  • a driver shaft 19 is arranged and the striking head 18 is connected to the striking piston 1 on the one hand in a rotationally locking manner and on the other hand in the axial direction with free play.
  • the striking head 18 itself can be equipped with a rock drill bit or with a stepped carbide insert 18.1.
  • the working stroke of the percussion piston 1 is limited by the slope of the helical part 4.1 of the groove curve 4.
  • the piston stroke can, however, as shown in the exemplary embodiments corresponding to FIGS. 2 and 4, be increased by a plurality of cam mechanisms 3.1, 3.2 synchronously and acting in the same direction by the drive shaft 11 in a rotationally locking manner and in the axial direction with play and the two cam mechanisms 3.1, 3.2 a separate drive spring 17.1, 17.2 is assigned.
  • FIG. 2 there is a cylindrical insert 32 in the middle housing part 6.2, which can be displaced in the axial direction, but is non-rotatably arranged in the housing part 6.2. This supports against the mainspring 17.2.
  • the insert has a helical guide surface 5, the beginning and end of which are connected to one another by an axial surface part.
  • the drive shaft 11 has a radial guide element 12.2 which slides on the helical guide surface 5 when the shaft 11 rotates and thereby pushes the insert 32 back against the restoring force of the spring 17.2 in the direction of the motor 7.
  • the percussion piston 1.1 has a helical groove 4.1 in its rear part. A guide element 12.1 arranged on the insert 32 engages in this.
  • a drive spring 17.1 is arranged as a restoring element and impact energy store between a collar 44 directed radially inwards from the front end of the middle housing part 6.2 and a shoulder 34 of the percussion piston 1.1.
  • the helical groove 4.1 of the percussion piston 1.1 and the guide element 12.1 engaging therein form the cam mechanism 3.1, while the helical guide surface of the insert 32 with the guide element 12.2 of the shaft 11 represent the second cam mechanism 3.2.
  • Both cam gears 3.1 and 3.2 are synchronously connected to one another by the drive shaft 11 and act in the same direction.
  • the translational return strokes of the insert 32 and the other part of the percussion piston 1.1 to an enlarged Kolbenge aparhub add one hand.
  • the rear part of the percussion piston 1.1 has a bore 24.1 in which the drive shaft 11 is on the one hand non-rotatable and on the other hand is guided with axial play corresponding to the increased return stroke of the percussion piston 1.1. Otherwise, corresponding elements of the device in FIGS. 1 to 8 are identified by the same reference numerals.
  • the embodiment of the device according to FIG. 3 has a percussion piston 1.2 which can be driven in rotary connection with the drive shaft 11 in a rotary connection.
  • this is formed with a blind bore 20 and at the bottom thereof with an impact surface 15.1.
  • the striking head 18 has a central striking tool with a central flange 45. From this extends forward to an axially movable chisel 18.2 and backwards to a plunger 21.
  • the central striking tool is movably mounted in the striking head 18 in the axial direction and is supported with play against the return spring 38 in the direction against the striking piston 1.2.
  • the plunger 21 of the central percussion tool dips into the blind bore 20 and lies in the position shown in FIG.
  • the piston 1.2 swings forward under the action of the restoring force of the spring 17 and strikes the end face 21.1 of the plunger 21 with its impact surface 15.1.
  • the piston strikes the central striking tool the position shown in Fig. 3 against the back Adjustment force of the return spring 38 to the front, whereby the chisel 18.2 receives a drive pulse, for example, to smash a boulder with great force and high impact energy.
  • two cam mechanisms 3.1 and 3.2 interact with one another synchronously and in the same direction to increase the working stroke of the percussion piston 1.3.
  • the percussion piston 1.3 has an axial guide groove 23, and a guide cam 25 arranged on the housing inner wall 16.1 engages in this. This leads the percussion piston 1.3 with axial freedom of movement in a non-rotatable manner in the housing 6.
  • the percussion piston 1.3 has the central bores 24.1 for the drive shaft 11 and 24.2 for a rotatable plunger 21.1 which is connected to it in a rotationally locking manner.
  • FIG. 5 shows a simplified version of the device, which has only one cam mechanism 3.1. Otherwise, the design is similar to the device shown in FIG. 4, the axial return surface on the cam mechanism 3.1 being designated by the number 33.1.
  • FIG. 6 branches off a device whose internal structure is basically the same as that of the device according to FIG. 5. Deviating from this, the built-in motor 7 is missing in the housing 6. According to the feature of claim 4, it is located outside the device and is in a power-transmitting connection with the latter by means of the transmission shaft 10 and in a rotationally co-operating drive shaft 11. To couple the transmission shaft 10 to the drive shaft 11, a coupling 29 is expediently provided in the area of the housing closure 6.4.
  • the displacement of the drive motor out of the housing 6 to a location outside the device has the result that a longer space for the percussion piston 1.3 and the drive spring 17 is available overall in the longitudinal direction of the housing 6.
  • the impact piston 1.3 could be increased in length and thus in its kinetic mass, for example compared to the embodiment according to FIG. 5, which would result in higher impact energy, for example by reinforcing the drive spring 17.
  • the overall length of the device could also be shortened overall in comparison to the embodiment shown in FIG. 5.
  • the embodiment shown in Fig. 6 also has the advantage of lower manufacturing costs and possibly lighter overall weight.
  • guide surfaces 36, 36.1 can be arranged on the device.
  • FIGS. 1 to 6 are designed so that they are driven only in one direction forward.
  • 7 and 8 represent an embodiment of the ram boring device in which it can be reversed from forward to return. These each have two percussion pistons 1.4, 1.5 in an antipodal arrangement for forward or reverse of the device. These are held in their respective end positions by a drive spring 17.4 clamped between the two.
  • the cam mechanism 3.5 is provided for the propulsion piston 1.5, while the cam mechanism 3.4 is assigned to the impact piston 1.4 intended for the return stroke.
  • These are designed so that, depending on the direction of rotation of the drive shaft 11, only one of the percussion pistons 1.4, 1.5 can be excited or driven in working strokes. This means that by reversing the direction of rotation of the drive motor 7, the direction of impact of the device is reversed.
  • the reversal is achieved in that the drive shaft 11 is divided into two drive shaft parts 11.4 and 11.5.
  • a torque transmission of the shaft part 11.4 to the shaft part 11.5 takes place via the coupling 27 which can be oriented in the direction of rotation and via the axial coupling surfaces 40.
  • the shaft part 11.4 rotates in the direction of the drive motor 7, counterclockwise, the shaft part 11.5 is caused by the interaction of the axial coupling surfaces 40 rotatably entrained and also rotatably engages the plunger 21.5.
  • the radial this arranged guide cams 22.5 moves during a rotary movement through 360 o in brushing along on the guide surface 5.5 the blow piston 1.5 by the amount of the slope of the helical guide surface 5.5 in the direction toward the drive motor 7 until the end of the drive curve is reached.
  • the percussion piston 1.5 strikes under the restoring action of the drive spring 17.4 with its impact surface 15.5 here against the end face 21.6 of the plunger 21.5 and drives the device forward in the direction of arrow 41.
  • the freewheel 26 of the percussion piston 1.4 acts in such a way that it remains motionless, that is to say out of rotation in the end position shown in FIG. 7.
  • the design of the device according to FIG. 8 shows that the drive direction can be reversed by means of two antipodically arranged percussion pistons 1.4 and 1.5.
  • the cam mechanisms 3.4 and 3.5 each have an additional freewheel groove area 28.4 and 28.5. These each open into the beginning of a helical guide groove 4.4 or 4.5 and run in the circumferential direction of the corresponding percussion piston 1.4 or 1.5.
  • Guide elements 12.4 or 12.5 engage in the guide grooves 4.4, 4.5 or in the free-running grooves 28.4, 28.5 which open tangentially at the beginning thereof.
  • These are arranged with a switch function on cylindrical inserts 32.4 or 32.5 which can be displaced axially by the amount of a groove width. These inserts are each supported against restoring forces of the control springs 42.4 and 42.5.
  • the control function of the inserts 32.4, 32.5 and the guide elements 12.4, 12.5 arranged on them is as follows: Assuming that the drive shaft 11, viewed from the drive motor 7, rotates counterclockwise to the left in accordance with the directional arrow 47, the guide element 12.4 in the percussion piston 1.4 remains constantly in the region of the freewheel groove 28.4 and the percussion piston 1.4 thus remains in rotation, but in translational direction unmoved.
  • the restoring force of the control spring 42.5 acts by resiliently pressing the insert 32.5 in the direction of the striking tool 18, which due to the axial mobility of the insert 32.5, the guide element 12.5 arranged thereon is deflected into the helical cam track of the guide groove 4.5 and thus with this is engaged.
  • the rotating piston is moved back towards the motor against the restoring force of the spring 17 and, as before, it flips more described above, after reaching the end of the curve of the guide groove 4.5 to the front through the return groove area 4.6 and strikes the end face of the plunger 21.5 with its impact surface 15.5.
  • the functional play takes place in the opposite manner so that the percussion piston 1.5 by remaining the guide element 12.5 in the region of the freewheel groove 18.5 in its end position remains without executing an impact stroke, although it rotates with the shaft 11 in a rotationally locking engagement.
  • the percussion piston 1.4 responsible for the return stroke now carries out percussion movements that are caused by the fact that the guide cam 12.4 on the insert 32.4 axially movably arranged around the groove width moves into the helical groove area 4.4 of the cam mechanism 3.4 and, when the percussion piston 1.4 is rotated accordingly, its percussion movements induced in the manner described above.
  • the rear part of the housing 6 is closed off by a separate motor housing 6.5 and, with its end face, delimits the area of the larger inner diameter required for the cylindrical insert 32.4 and its control spring 42.4.
  • the area of the larger inner diameter for receiving the insert 32.5 and the control spring 42.5 is closed off by the front flange 35 of the device.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (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)
  • Mechanical Engineering (AREA)
  • Earth Drilling (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP19900105472 1989-04-01 1990-03-23 Dispositif automoteur de forage par battage Withdrawn EP0391161A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3910515 1989-04-01
DE3910515A DE3910515A1 (de) 1989-04-01 1989-04-01 Selbstantreibbare rammbohrvorrichtung, insbesondere zur herstellung von rohrfoermigen erdbohrungen

Publications (2)

Publication Number Publication Date
EP0391161A2 true EP0391161A2 (fr) 1990-10-10
EP0391161A3 EP0391161A3 (fr) 1991-03-20

Family

ID=6377576

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900105472 Withdrawn EP0391161A3 (fr) 1989-04-01 1990-03-23 Dispositif automoteur de forage par battage

Country Status (3)

Country Link
EP (1) EP0391161A3 (fr)
JP (1) JP2965315B2 (fr)
DE (1) DE3910515A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2320952A (en) * 1997-01-03 1998-07-08 Earth Tool Co Llc Pipe bursting or bore widening apparatus with impact tool
EP0964133A1 (fr) * 1998-05-27 1999-12-15 Tracto-Technik Paul Schmidt Spezialmaschinen Boítier pour transmetteur
WO2002046564A2 (fr) * 2000-12-09 2002-06-13 Fisher Power Wave Ltd Appareil de forage
WO2002055830A2 (fr) * 2001-01-15 2002-07-18 Tracto-Technik Gmbh Procede pour buriner de la roche
GB2334053B (en) * 1998-02-07 2002-11-13 Tracto Technik Percussion boring machine
CN104405321A (zh) * 2014-10-21 2015-03-11 中国石油天然气集团公司 钻压推加器
CN108662284A (zh) * 2018-06-01 2018-10-16 成都金玉雄辉建筑工程有限公司 小口径顶管的施工方法
CN110067516A (zh) * 2019-05-22 2019-07-30 成都迪普金刚石钻头有限责任公司 一种快速冲击-刮切复合式破岩pdc钻头
CN114198013A (zh) * 2021-11-30 2022-03-18 九江萨普智能科技有限公司 一种便于夹持多种物料的工业夹持机器人

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CH683016A5 (de) * 1990-12-24 1993-12-31 Terra Ag Tiefbautechnik Verfahren zum Aufweiten eines Bohrloches und Aufweitgerät.
CN103306600B (zh) * 2013-06-27 2016-02-10 深圳市百勤石油技术有限公司 一种凸轮式轴向旋冲工具
CN104482297A (zh) * 2014-11-15 2015-04-01 赵涌韬 牵引鼠
CN106522844B (zh) * 2016-11-10 2018-11-30 王天勇 十字型冲击钻头结构、含有该结构的旋挖机钻头及其应用
JP7260219B1 (ja) * 2023-01-18 2023-04-18 株式会社エステック 掘削機

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3421735A (en) * 1966-11-23 1969-01-14 Ingersoll Rand Co Acceleration limiting means for fluid motors
DE1483854A1 (de) * 1966-12-28 1970-03-19 Metabowerke Kg Bohrhammer
DE2533284A1 (de) * 1975-07-25 1977-02-17 Bosch Gmbh Robert Schlagbohrmaschine
DE2526511B2 (de) * 1974-06-13 1979-09-20 Institut Gornogo Dela Sibirskogo Otdelenija Akademii Nauk Ssr, Nowosibirsk (Sowjetunion) Zwei-Kolben-Bohrhammer mit einer eine Drallnutenverbindung aufweisenden Vorrichtung zum Umsetzen eines Bohrers
EP0288123A2 (fr) * 1987-04-21 1988-10-26 Shell Internationale Researchmaatschappij B.V. Moteur de forage de fond de trou

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4530561Y1 (fr) * 1964-08-21 1970-11-24
DE2157259C3 (de) * 1971-11-18 1973-06-07 Tracto Technik Rammbohrgerät

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3421735A (en) * 1966-11-23 1969-01-14 Ingersoll Rand Co Acceleration limiting means for fluid motors
DE1483854A1 (de) * 1966-12-28 1970-03-19 Metabowerke Kg Bohrhammer
DE2526511B2 (de) * 1974-06-13 1979-09-20 Institut Gornogo Dela Sibirskogo Otdelenija Akademii Nauk Ssr, Nowosibirsk (Sowjetunion) Zwei-Kolben-Bohrhammer mit einer eine Drallnutenverbindung aufweisenden Vorrichtung zum Umsetzen eines Bohrers
DE2533284A1 (de) * 1975-07-25 1977-02-17 Bosch Gmbh Robert Schlagbohrmaschine
EP0288123A2 (fr) * 1987-04-21 1988-10-26 Shell Internationale Researchmaatschappij B.V. Moteur de forage de fond de trou

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
SOVIET INVENTIONS ILLUSTRA- TED, P,Q Sektionen, Woche vom 2.MÛrz 1983 DERWENT PUBLICATIONS LTD., London, Q 49 *

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2320952B (en) * 1997-01-03 2001-07-04 Earth Tool Co Llc Method and apparatus for installation of underground pipes
GB2320952A (en) * 1997-01-03 1998-07-08 Earth Tool Co Llc Pipe bursting or bore widening apparatus with impact tool
GB2334053B (en) * 1998-02-07 2002-11-13 Tracto Technik Percussion boring machine
EP0964133A1 (fr) * 1998-05-27 1999-12-15 Tracto-Technik Paul Schmidt Spezialmaschinen Boítier pour transmetteur
GB2388135A (en) * 2000-12-09 2003-11-05 Fisher Powerwave Ltd Boring Apparatus
WO2002046564A2 (fr) * 2000-12-09 2002-06-13 Fisher Power Wave Ltd Appareil de forage
US7410013B2 (en) 2000-12-09 2008-08-12 Wave Craft Limited Boring and drilling apparatus
WO2002046564A3 (fr) * 2000-12-09 2002-10-17 Fisher Power Wave Ltd Appareil de forage
WO2002055830A2 (fr) * 2001-01-15 2002-07-18 Tracto-Technik Gmbh Procede pour buriner de la roche
WO2002055830A3 (fr) * 2001-01-15 2002-09-12 Tracto Technik Procede pour buriner de la roche
CN104405321A (zh) * 2014-10-21 2015-03-11 中国石油天然气集团公司 钻压推加器
CN108662284A (zh) * 2018-06-01 2018-10-16 成都金玉雄辉建筑工程有限公司 小口径顶管的施工方法
CN110067516A (zh) * 2019-05-22 2019-07-30 成都迪普金刚石钻头有限责任公司 一种快速冲击-刮切复合式破岩pdc钻头
CN110067516B (zh) * 2019-05-22 2024-03-22 倪政敏 一种快速冲击-刮切复合式破岩pdc钻头
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JP2965315B2 (ja) 1999-10-18
DE3910515C2 (fr) 1991-08-08

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