EP0300080A1 - Dispositif pour le forage au travers de morts-terrains - Google Patents

Dispositif pour le forage au travers de morts-terrains Download PDF

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Publication number
EP0300080A1
EP0300080A1 EP87110824A EP87110824A EP0300080A1 EP 0300080 A1 EP0300080 A1 EP 0300080A1 EP 87110824 A EP87110824 A EP 87110824A EP 87110824 A EP87110824 A EP 87110824A EP 0300080 A1 EP0300080 A1 EP 0300080A1
Authority
EP
European Patent Office
Prior art keywords
pump
drilling
pumps
power
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.)
Withdrawn
Application number
EP87110824A
Other languages
German (de)
English (en)
Inventor
Günter Dr.Ing. Klemm
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.)
Ing G Klemm Bohrtechnik GmbH
Original Assignee
Ing G Klemm Bohrtechnik GmbH
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 Ing G Klemm Bohrtechnik GmbH filed Critical Ing G Klemm Bohrtechnik GmbH
Priority to EP87110824A priority Critical patent/EP0300080A1/fr
Publication of EP0300080A1 publication Critical patent/EP0300080A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/328—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the axis of the cylinder barrel relative to the swash plate
    • 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
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • 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

Definitions

  • the invention relates to an overlay drilling device according to the preamble of patent claim 1.
  • the drill rod When drilling into the ground, the drill rod is subjected to a feed force and rotated in the process and, if necessary, struck with a hydraulic hammer so that the drill bit provided at the front end of the drill rod drives the borehole.
  • the known drilling devices have hydraulic drives for the feed, turning and possibly the striking device. These hydraulic drives each consist of a pump, which is driven by an internal combustion engine or an electric motor, and a hydraulic motor, which is either a linear motor in the form of a piston-cylinder unit or a rotary motor.
  • the pumps used in the drives are volume-controlled pumps that maintain a constant delivery volume regardless of the load-side pressure.
  • volume controlled pumps are used in the various drilling processes for the following reasons:
  • the rotary drive and impact device are coordinated with one another in such a way that they work with a constant speed and constant number of impacts, irrespective of the resistance that the rock opposes, the feed force, which is selected as a function of the rock hardness, also being kept constant.
  • a ring core bit When core drilling to obtain soil samples and rock samples, a ring core bit is driven with constant pressure and speed so that a defined cutting speed is created.
  • a desired cutting speed which depends on the nature of the soil or rock and on the diameter of the borehole, is selected and maintained.
  • manual gearboxes may be used to obtain the desired speed for both large and small borehole diameters. In any case, it is always ensured that a certain speed is maintained with the highest possible accuracy, regardless of the drilling resistance.
  • speed-controlled pumps are used that have a constant liter output per minute, regardless of the drilling resistance. Keeping the delivery volume constant means that the motors that drive these pumps are required to perform at varying times.
  • the motor power is relatively low with a low drilling resistance, while it also increases with increasing drilling resistance.
  • the motors must each be designed for the maximum required power, but are only operated with significantly lower power during most of the drilling operation. This means that a high mechanical power installation is required, but this is only used to a small extent.
  • Another disadvantage of the known drilling devices is that due to the constant delivery rate of the pumps, when the drilling resistance is low, the drilling operation is too low. This also applies to the installation and removal of pipe rods. If the pipe string is pulled out of the borehole practically without resistance, this is only possible with the regulated pump volume of the pump of the feed drive, so that the pulling out and reinstalling of the drill pipe takes a very long time. In the past, in order to accelerate the pulling out and reinserting of the drill pipe, help was provided by connecting the pump of the percussion drive, which is not required at this stage, to the pump of the feed drive in order to combine the delivery rates of the two pumps and thereby faster To achieve displacement movements of the drill pipe.
  • both pumps are designed for different pressures. Additional measures to decouple the pumps are required. In normal drilling operations, such an interconnection of the pumps is not possible because each drive is then required individually.
  • Such pumps are designed, for example, as variable displacement pumps which have a plurality of cylinder chambers in a cylinder body which is adjustable by a pivoting angle.
  • the pistons are on supported by a drive shaft.
  • the piston stroke changes depending on the adjustment angle of the cylinder block relative to the axis of the drive shaft.
  • a control system adjusts the swivel angle of the cylinder block as a function of the pump pressure so that the pump operates at a constant output regardless of the pump pressure. This means that the pump volume decreases at higher pump pressure or higher load pressure, while the pump delivers a lower pump volume at higher load pressure.
  • the invention has for its object to provide an overlay drilling device according to the preamble of claim 1, which enables faster and more effective drilling and in which the installed drive power is better used. This object is achieved according to the invention with the features specified in the characterizing part of patent claim 1.
  • a volume-controlled pump is used in the overlay drilling for the rotary drive and / or the feed drive.
  • Overlay drilling is performed on overlay soils. These are mixed floors, which consist of non-homogeneous material. Drilling in overlay soils requires the use of supported holes, which can be supported either with an outer pipe string or by introducing a concrete mass that hardens during drilling and forms a tubular support for the borehole. Since overlay soils, the loam, gravel, sand or the like. can not contain self-supporting boreholes, a borehole support is required.
  • Overlay drilling can be carried out, for example, by connecting the outer support tube and the inner drill tube to one another in a torque-proof and impact-resistant manner, so that both tubes are inserted simultaneously.
  • the invention offers the advantage that the drive motors for the pumps are always operated at full power, so that the installed motor power is fully utilized. Furthermore, the effectiveness of drilling is increased, ie the drilling is carried out at the speed that corresponds to the installed power. If the drilling resistance is low, the drilling operation is significantly higher than if the drilling resistance is high.
  • the overlay drilling device according to the invention can only be used with non-homogeneous mixed soils and not with drilling in hard rock, with rotary drilling, with core drilling and also not with roller chisel drilling, because with the mentioned drilling types from certain rotation and feed speeds must be observed.
  • the invention is initially based on the idea that in the case of overlay drilling, it is not necessary to maintain certain rotational and feed speeds and certain impact frequencies, although in the prior art overlay drilling was always carried out with the same drive devices as the other drilling types mentioned.
  • the invention also has the advantage that when installing and removing drill pipe using only the feed drive at very high speed without having to switch on other pumps and without any intervention. Since the load is relatively low when installing and removing drill pipe, the power-controlled pump delivers a large volume of liquid, so that the above-mentioned processes can be carried out very quickly.
  • a return line containing a current regulator is connected to the output of the power-controlled pump via a valve.
  • a valve This makes it possible to branch off a meterable part from the delivery volume of the power-controlled pump and to feed it back into the sump.
  • the motor power or pump power is not fully utilized, but there is the possibility of manually adjusting the drive speed or number of strokes. This is necessary, for example, if a boulder that coincides with the other occurs during the overlay drilling Mode of operation of the overlay drilling device cannot be broken or only very slowly.
  • the overlay drilling device is generally intended and designed for overlay drilling, it can nevertheless also be used, for example, for auger drilling, only the rotary drive and possibly also the feed drive being used. Although it is basically a superimposed drilling device, this drilling device can also be operated in connection with a worm drill, which then runs at a relatively high speed of 200 rpm. running.
  • the overlay drilling device shown in FIG. 1 serves to advance a drill string 10 which consists of the outer pipe string 11, which forms the support pipe for supporting the borehole, and the inner pipe string 12, which has a drill bit (not shown) at its front end.
  • the outer tube linkage 11 and the inner tube linkage 12 in the present exemplary embodiment are connected to one another at their rear ends by a head piece 13 in a rotationally fixed and impact-resistant manner.
  • the outer tube linkage 11 extends through a spline toothing of a gearwheel 14 which is in engagement with a gearwheel 15, so that the two tube linkages 11 and 12 are rotated about their common longitudinal axis by the rotating gearwheel 15.
  • the gear wheel 15 is driven by the hydraulic rotary drive 16, which is a hydraulic rotary motor.
  • the hammer piston 17 of a hydraulic hammer drill 18 strikes the head piece 13.
  • the percussion piston 17 can be displaced linearly in the hammer housing 19 and is reversed via hydraulic lines 20, 21 by a control valve 22, so that the hammer piston 17 alternately carries out stroke strokes and return strokes.
  • the control valve 22 is controlled in dependence on the changing pressures on the lines 20 and 21.
  • the unit 23 that the Includes hammer drill 18 with the control valve 22 forms an assembly which is provided with a rack 24 which is linearly driven by the gear 25 to advance the unit 23 towards the drill string 10.
  • the gear 25 is driven by the hydraulic feed drive 26, which in the present case is a rotary motor.
  • the feed drive could also consist of a piston-cylinder unit, the piston of which acts directly on the unit 23 in order to advance it.
  • the rotary drive 16 is supplied with hydraulic fluid by the pump 27.
  • the pump 27 draws this liquid from a tank 28 and conveys it via the reversing valve 29 to the rotary motor 15.
  • the reversing valve 29 has three positions, one position for clockwise rotation, another position for counter-clockwise rotation of the rotary drive 16 and a middle position for switching off the rotary drive is determined. In the middle position, the pressure line 30 of the pump 27 is connected to the tank 28, so that the pump feeds back into the tank when the rotary drive is switched off.
  • the pump 27 is connected to the output shaft of a motor 31, which is an electric motor or an internal combustion engine.
  • the feed drive 26 is supplied with hydraulic fluid by a pump 27a via a reversing valve 29a, the pump 27a being driven by a motor 31a.
  • the pressure line of the pump 27a is designated 30a.
  • the hammer drill 18 is supplied with hydraulic fluid via a pump 27b which is supplied by a Motor 31b is driven and hydraulic fluid conducts to the control valve 22 via the reversing valve 29b.
  • the reversing valves 29, 29a and 29b are manually operated valves with which the direction of movement of the connected consumers can be reversed or the consumers can be stopped.
  • Each of the pumps 27, 27a and 27b is a power-controlled pump.
  • the structure of the pump 27 is explained below with reference to FIG. 2.
  • the pumps 27a and 27b are designed in the same way.
  • the motor 31 drives the drive shaft 33 of the pump 27.
  • the drive shaft 33 is rotatably mounted in the pump housing 34 and has a plate 35 in the interior of the pump housing, in which the heads 36 of a plurality of piston rods 37 are supported and pivotally held.
  • Each piston rod 37 is connected to a piston 38 which is longitudinally displaceable in the cylinder chamber 39 of a cylinder block 40.
  • the piston rods 37 and the cylinder chamber 39 are arranged along a circular ring and the cylinder block 40 can be pivoted in a space 41 around the center 42 of the plate 35 so that the longitudinal axis of the cylinder block 40 is angled with respect to the axis of the drive shaft 33 .
  • All cylinder chambers 39 are interconnected and lead to a pressure outlet, not shown in FIG. 2, which is connected to the pressure line 30.
  • the pivoting of the cylinder block 40 is carried out by a driver 43 which engages in the cylinder block and is linearly displaceable in the housing part 44.
  • the driver 43 is at the end of an actuating piston 45 be consolidates, which is displaceable in the cylinder space 46, in which the pressure of the pressure line 30 prevails.
  • the actuating pistons 45 and 47 act in opposite directions, the effective piston area of the actuating piston 47 being larger than that of the actuating piston 45.
  • the cylinder block 40 is pivoted in the direction in which its longitudinal axis coincides with that the drive shaft 33 is aligned.
  • the force of this actuating movement depends on the amount of pressure.
  • This adjustment movement is counteracted by the forces of two springs 49 and 50, which are supported in the housing part 44 and strive to move the driver 43 into the position in which the axis of the cylinder block 44 assumes the greatest angulation with respect to that of the drive shaft 33.
  • the spring 49 In the illustrated position of maximum deflection of the cylinder block 40, only the spring 49 initially acts. If the deflection becomes smaller with a greater hydraulic pressure, then the spring 50 also becomes effective from a certain value, so that both springs 49 and 50 are subject to the force of the actuating piston 47 oppose.
  • the pump performance can be kept constant with the appropriate dimensioning of the springs 49 and 50.
  • the start of control is controlled by an auxiliary piston 51 which can be moved in a cylinder 52 which is acted upon by the pump pressure.
  • a spring 53 counteracts the pressure in the cylinder 52. If this pressure exceeds a limit value, the spring 53 yields and the piston 51 opens a connection through which the cylinder space 48 is connected to the pressure side of the pump.
  • the piston 51 thus forms, together with the spring 53, a pressure-dependent switching valve which allows the control to be used when a limit pressure is exceeded. As long as this limit pressure is not reached, the pump works with the full delivery volume.
  • Fig. 3 shows the characteristics of the pumps for feed, turning and beating. All three pumps have a maximum delivery volume of 150 l / min., But different response pressures.
  • the pump power for the feed drive is 11 kW, that for the rotary drive is 37 kW and that for the percussion drive is 54 kW.
  • the operating point A1 is set, for example, for the feed drive, at which the pump 27a with a full delivery rate of 150 l / min. works, while the pressure of 40 bar is still below the response pressure of the pump 27a of 44 bar. If the drilling resistance increases, the operating point moves to Bl, for example, with the delivery rate Q being 35 l / min. decreases, while the delivery pressure p increases to about 200 bar. The contact pressure increases many times, while the feed speed decreases.
  • the power control of the pump 27 of the rotary drive 16 starts at a pressure of 150 bar. At lower pressures, the rotary drive runs at a constant rotational speed, at higher pressures the rotational speed decreases in accordance with the curve labeled "turning".
  • the hammer drill 18 is normally subjected to a pressure of approximately 180 bar. This pressure is still below the start of control (220 bar). Above the start of the control, the delivery volume of the pump 27b decreases, which reduces the number of strokes, but increases the individual impact energy due to the higher pressure.
  • the course of the control characteristic curves shown in FIG. 3 is essentially determined by the springs 49 and 50 of the respective pumps.
  • the course of the control characteristic curves can be set so that the pump output within the control range is essentially constant for all pressures.
  • each of the drives 16, 26 and 18 is set independently, and only as a function of the resistance which the drill string 10 opposes to the drive in question.
  • the pressure line 30 for the rotary drive 16 is connected via the valve 60 to a return line 61 which leads back into the tank 28 and which contains a current regulator 62, for example in the form of a throttle element.
  • a current regulator 62 for example in the form of a throttle element.
  • a valve 60a, return line 61a and current regulator 62a are provided in the same way for the pump 27a of the feed drive.
  • a valve 60b with return line 61b and flow regulator 62b are also provided for the pump 27b of the hammer drill 18.
  • Fig. 4 shows the invention using the example of a double-head drilling device in which the inner tube carries a core bit and the outer tube a ring bit and both tubes are rotated separately.
  • the drill string 10 consists of the outer pipe string 11 and the inner pipe string 12 running coaxially therein.
  • the rear end of the outer pipe string 11 is included a gearbox 63 which is driven by a rotary drive 16a consisting of a hydraulic motor.
  • the rotary drive 16a drives a gear 64 with internal teeth.
  • the gear 64 is in engagement with a connecting pipe 65, the front end of which is screwed to the outer pipe rod 11.
  • In the lateral surface of the connecting pipe 65 there is an opening 66 which runs along an annular groove 67 inside the housing 68 when it is rotated.
  • the annular groove 67 is connected to an ejection opening 69, so that the drilling mud that is flushed up through the outer pipe rod 11 passes through the opening 66 and the annular groove 67 to the ejection opening 69.
  • a seal 70 which seals the passage between the inner pipe string 12 and the connecting pipe 65, prevents the drilling mud from getting out along the inner pipe string 12.
  • the inner pipe string 12 leads through the gear 63 and through the gear 71 to the hydraulic hammer drill 18.
  • the hydraulic rotary drive 16b drives the inner pipe string 12 in rotation, while the hammer drill 18 strikes the rear end of the inner pipe string.
  • the inner tube linkage 12 is screwed via a connecting piece 73 to a connecting tube 74, which forms the rear end of the inner tube linkage 12.
  • the gear 63 is attached to the first part 75 of a feed device 77, while the gear 71 and the hammer drill 18 are attached to the second part 76 of the feed device.
  • the two parts 75 and 76 can be moved relative to one another by a piston-cylinder unit 78. They are on one level and their mutual distance can be changed by the piston-cylinder unit 78.
  • the feed device 27 is driven by the hydraulic feed motor 26. It has a chain drive, the chain 79 engages an extension 80.
  • the endless chain 79 runs around sprockets 81, 82, one of which is driven by the feed motor 26. By driving the chain 79, the assembly of the gears 63, 71 and the hammer drill 72 can be pushed forward or back as a whole.
  • all three hydraulic drives 16a, 16b, 18 and 26 are supplied by power-controlled pumps of the type shown in FIG. 2.
  • the rotary drive 16a for the outer pipe string and pushing it again as soon as the drill bit attached to the end of the inner pipe string has advanced the hole further.
  • the outer tube linkage and the inner tube linkage can be coupled to one another, in which case one of the rotary drives 16a or 16b is then also unnecessary.
  • each of the power-controlled pumps is driven by its own motor.
  • Two or more pumps are advantageously driven by a common motor, and the power can be distributed via a transfer case.

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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)
  • General Engineering & Computer Science (AREA)
  • Earth Drilling (AREA)
EP87110824A 1987-07-25 1987-07-25 Dispositif pour le forage au travers de morts-terrains Withdrawn EP0300080A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP87110824A EP0300080A1 (fr) 1987-07-25 1987-07-25 Dispositif pour le forage au travers de morts-terrains

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP87110824A EP0300080A1 (fr) 1987-07-25 1987-07-25 Dispositif pour le forage au travers de morts-terrains

Publications (1)

Publication Number Publication Date
EP0300080A1 true EP0300080A1 (fr) 1989-01-25

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EP87110824A Withdrawn EP0300080A1 (fr) 1987-07-25 1987-07-25 Dispositif pour le forage au travers de morts-terrains

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EP (1) EP0300080A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0849468A2 (fr) * 1996-12-19 1998-06-24 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la capacité d'une pompe à pistons axiaux
WO2004065761A1 (fr) * 2003-01-24 2004-08-05 Sandvik Tamrock Oy Systeme hydraulique destine a du materiel d'exploitation des mines et procede de reglage de la puissance d'une perforatrice de roches
CN101871316A (zh) * 2010-06-23 2010-10-27 李恩怡 一种桩机
EP2955316A1 (fr) * 2014-06-13 2015-12-16 Sandvik Mining and Construction Oy Forage de roches et procédé de forage
EP2955315A1 (fr) * 2014-06-13 2015-12-16 Sandvik Mining and Construction Oy Appareil de forage de roches et procédé de forage
CN108612516A (zh) * 2018-06-07 2018-10-02 中国铁建重工集团有限公司 一种凿岩钻机及其液压控制阀组
EP4194617A1 (fr) * 2021-12-10 2023-06-14 Sandvik Mining and Construction Oy Système hydraulique, véhicule de travail et procédé
EP4198305A4 (fr) * 2020-09-16 2023-08-23 Beijing Jodin Technology Co. Ltd. Pompe à moteur hydraulique variable de type à piston à axe brisé

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2298849A (en) * 1939-03-30 1942-10-13 Vickers Inc Power transmission
US3189103A (en) * 1961-07-20 1965-06-15 Atlas Copco Ab Hydraulic drill feed control
US3910358A (en) * 1974-07-05 1975-10-07 Koehring Co Horizontal earth boring machine
US4042043A (en) * 1974-03-27 1977-08-16 The Richmond Manufacturing Company Portable earth boring machine
DE2924393A1 (de) * 1979-06-16 1980-12-18 Brueckner Grundbau Gmbh Bohrvorrichtung zum ueberlagerungsbohren
US4246973A (en) * 1978-01-23 1981-01-27 Cooper Industries, Inc. Controls for hydraulic percussion drill
DE3503893C1 (de) * 1985-02-06 1985-10-24 Ing. Günter Klemm, Spezialunternehmen für Bohrtechnik, 5962 Drolshagen Bohrvorrichtung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2298849A (en) * 1939-03-30 1942-10-13 Vickers Inc Power transmission
US3189103A (en) * 1961-07-20 1965-06-15 Atlas Copco Ab Hydraulic drill feed control
US4042043A (en) * 1974-03-27 1977-08-16 The Richmond Manufacturing Company Portable earth boring machine
US3910358A (en) * 1974-07-05 1975-10-07 Koehring Co Horizontal earth boring machine
US4246973A (en) * 1978-01-23 1981-01-27 Cooper Industries, Inc. Controls for hydraulic percussion drill
DE2924393A1 (de) * 1979-06-16 1980-12-18 Brueckner Grundbau Gmbh Bohrvorrichtung zum ueberlagerungsbohren
DE3503893C1 (de) * 1985-02-06 1985-10-24 Ing. Günter Klemm, Spezialunternehmen für Bohrtechnik, 5962 Drolshagen Bohrvorrichtung

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0849468A3 (fr) * 1996-12-19 1999-09-15 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la capacité d'une pompe à pistons axiaux
EP0849468A2 (fr) * 1996-12-19 1998-06-24 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la capacité d'une pompe à pistons axiaux
US7900712B2 (en) 2003-01-24 2011-03-08 Sandvik Mining And Construction Oy Hydraulic system for mining equipment and method of adjusting power of rock drill machine
WO2004065761A1 (fr) * 2003-01-24 2004-08-05 Sandvik Tamrock Oy Systeme hydraulique destine a du materiel d'exploitation des mines et procede de reglage de la puissance d'une perforatrice de roches
AU2004206070B2 (en) * 2003-01-24 2009-03-12 Sandvik Mining And Construction Oy Hydraulic system for mining equipment and method of adjusting power of rock drill machine
CN101871316B (zh) * 2010-06-23 2013-03-06 李恩怡 一种桩机
CN101871316A (zh) * 2010-06-23 2010-10-27 李恩怡 一种桩机
EP2955316A1 (fr) * 2014-06-13 2015-12-16 Sandvik Mining and Construction Oy Forage de roches et procédé de forage
EP2955315A1 (fr) * 2014-06-13 2015-12-16 Sandvik Mining and Construction Oy Appareil de forage de roches et procédé de forage
CN108612516A (zh) * 2018-06-07 2018-10-02 中国铁建重工集团有限公司 一种凿岩钻机及其液压控制阀组
CN108612516B (zh) * 2018-06-07 2024-02-20 中国铁建重工集团股份有限公司 一种凿岩钻机及其液压控制阀组
EP4198305A4 (fr) * 2020-09-16 2023-08-23 Beijing Jodin Technology Co. Ltd. Pompe à moteur hydraulique variable de type à piston à axe brisé
EP4194617A1 (fr) * 2021-12-10 2023-06-14 Sandvik Mining and Construction Oy Système hydraulique, véhicule de travail et procédé
WO2023105048A1 (fr) * 2021-12-10 2023-06-15 Sandvik Mining And Construction Oy Système hydraulique, véhicule de travail et procédé

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