EP0685301A1 - Dispositif à percussion hydraulique avec réglage continu du nombre et de l'intensité des coups - Google Patents

Dispositif à percussion hydraulique avec réglage continu du nombre et de l'intensité des coups Download PDF

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Publication number
EP0685301A1
EP0685301A1 EP95108205A EP95108205A EP0685301A1 EP 0685301 A1 EP0685301 A1 EP 0685301A1 EP 95108205 A EP95108205 A EP 95108205A EP 95108205 A EP95108205 A EP 95108205A EP 0685301 A1 EP0685301 A1 EP 0685301A1
Authority
EP
European Patent Office
Prior art keywords
control
valve
impact device
rotary
housing
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.)
Granted
Application number
EP95108205A
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German (de)
English (en)
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EP0685301B1 (fr
Inventor
Dieter Güde
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.)
Deilmann Haniel GmbH
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Deilmann Haniel GmbH
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Filing date
Publication date
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Publication of EP0685301A1 publication Critical patent/EP0685301A1/fr
Application granted granted Critical
Publication of EP0685301B1 publication Critical patent/EP0685301B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/26—Lubricating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/16—Valve arrangements therefor
    • B25D9/22—Valve arrangements therefor involving a rotary-type slide valve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
    • 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

Definitions

  • the invention relates to a hydraulic impact device with a housing receiving the end of the pipe run and having the slewing gear for the pipe run, which receives a reciprocating piston which can be moved back and forth in an inner bore and is controlled by a control with a rotary valve driven by a rotary motor and acts on the pipe run .
  • Such a hydraulic impact device is known from DE-OS 22 014.6.
  • the device required for reversing is designed as a rotary valve surrounding the actual impact piston.
  • the entire device requires considerable dimensions simply because of this design alone.
  • the output changes with the change in the number of blows and also the impact energy, so that the control as a whole is relatively imprecise.
  • the device according to DE-OS 43 28 278.4 in which in turn the rotary valve is arranged surrounding the percussion piston.
  • the proposed device thus has mechanical connections, in particular also via gearwheels, which in turn entails increased production expenditure and, in particular, a certain dependency on the number of blows, energy and power.
  • extension bores it is not possible to use extension bores to produce or operate different hammers with different values, because the overall device once manufactured must also be operated as such.
  • the invention is therefore based on the object of providing an impact device which has a simple and easy control which can be adapted to different requirements.
  • the rotary valve and the associated rotary motor are arranged independently of the percussion piston on or in the housing and are only connected via channels to the pump and tank connection or the piston surfaces on both sides.
  • the rotary valve can be designed and positioned completely independently of the respective impact device. It does not surround the percussion piston, but represents a separate component which is then only connected to the percussion piston hydraulically and not mechanically via the corresponding channels.
  • the rotary valve as such is designed so that a change or adjustment of the impact device as a whole is relatively quickly possible.
  • the rotary valve can be used to continuously control the number of blows and energy at constant power. This means that such a striking device is not only very versatile, but is also characterized by a very practical and effective control.
  • the rotary slide valve has a control housing which is detachably connected to the housing. Due to the detachable connection between the control housing and the housing or rotary slide valve and ultimately the percussion piston, such a control can be attached to practically any hammer or an operation can be carried out. adapted to the respective drilling pattern.
  • the rotary valve can also be used with large hammers, for example demolition hammers, whereby it continues to be small and thus enables use with these large devices, since it can be implemented independently of the respective size of the percussion piston.
  • extension bores can be carried out with such a striking device, since the striking mechanism can advantageously be switched off and the fixing or connection of the next drill pipe can accordingly be carried out without the striking mechanism causing disadvantages.
  • the rotary valve is surrounded by a control bushing arranged in the control housing, which has control openings corresponding to the control openings provided in the rotary valve and designed as control slots, which in turn are connected to the channels for the pump and tank connection.
  • a control bushing arranged in the control housing, which has control openings corresponding to the control openings provided in the rotary valve and designed as control slots, which in turn are connected to the channels for the pump and tank connection.
  • Via the control bushing surrounding the rotary slide valve it is possible to provide the connection to the respective channel, so to speak, while the rotary slide valve is rotating and without any leaks or other problems occurring during this time.
  • the pressure medium is immediately in the corresponding channel or it can flow through the corresponding channel in a pressure-relieved manner.
  • control openings in the rotary valve as well as in the control bushing are also matched to one another in terms of their dimensions, so that the hydraulic quantities required to initiate and carry out the control process are available at short notice.
  • the response point or the defined opening point can be precisely predetermined for the control openings used.
  • the invention provides that the rotary motor of the rotary valve is detachably connected to the control housing and is continuously adjustable. This means that only the rotary motor can be replaced in a very short time, so that the performance of the respective rotary valve can also be adapted to the respective requirements. Since the rotary motor is infinitely adjustable, the impact device can be adapted relatively easily to changing circumstances.
  • a rotary slide valve in which the control openings at the end of the rotary slide valve opposite the rotary motor, which connect it to the channel to the percussion piston, are designed as a bore.
  • the holes open a little more slowly than the longitudinal slots in the rotary valve, but this is enough because the hydraulic fluid must first penetrate into the inner channel of the rotary valve, the inner channel being a blind hole in the rotary valve.
  • the pressure fluid from the rotary valve enters the channel through this bore, pressure fluid being present in the channel one way or the other, so that the necessary pressure can build up relatively quickly.
  • the percussion piston is equipped with two piston rings spaced apart from one another, the piston ring facing away from the truncated cone-shaped striking end having a larger area than the area of the piston ring facing the striking end, the area of the striking piston is permanently connected to the pump connection.
  • This special design and the constant connection to the pump connection ensures that the percussion piston quasi automatically after reaching the lower working position is always pushed back into the upper working position because the pump pressure has a corresponding short-term effect.
  • the percussion piston itself has a correspondingly large length and is nevertheless light and can also be locked in relatively short ways if the piston rings are arranged and designed correspondingly to one another.
  • the two piston rings also have the advantage that, while maintaining virtually the bore diameter within the housing, only the upper end piece of the piston has to be slightly tapered in order to make the different surfaces available.
  • the percussion piston is designed with two piston rings in order, among other things, to specify the length of the percussion piston accordingly.
  • the invention provides that on both sides of the piston ring, which is permanently connected to the pump connection via the channel, a connection to a pressure relief hole is provided.
  • the invention provides that the channels for the pump and tank connection and for the striking piston are additionally connected to the outer wall of the housing via tap holes.
  • a measuring device can be connected at any time, which can precisely monitor both the quantities and, in particular, the level of the pressure present. If such measurements are temporarily not considered necessary or not desired, it is easily possible to close the tap holes on the outer wall of the housing so that leakage in this area can then be prevented without any problems.
  • control with rotary valve and rotary motor is provided with central lubrication, which is controlled via a valve with a pilot valve, which has an output lever between the input lever and the plunger, which on the one hand alternately loads the plunger or from this is designed to be loaded and on the other hand influenced by a locking element guided on a quadrant and connected to the input lever, the locking element being equipped with a plurality of locking piece units which can be displaced relative to one another.
  • a control device is installed on this or on this pilot control unit, which is designed such that self-adjustment cannot occur even with the strongest vibrations.
  • the output lever is locked via the force occurring on the tappet and the spring, so that the valve can no longer be adjusted unconsciously. Rather, it is necessary to operate the input lever to release the lock on the output lever and then to consciously adjust the pilot valve.
  • This type of pilot valve uses a known element, which was originally developed and used as a self-locking mechanical element for aircraft control systems.
  • the restoring force is automatically blocked without the use of ratchets, pawls, rubbers or similar, whereby the higher the restoring force, the safer the self-locking is.
  • Via the locking piece units which can be pushed against each other, the targeted locking by the plunger or the associated springs takes place to such an extent that there is effective locking even under extreme conditions.
  • An improved two-speed motor is used for the slewing gear, in order to guarantee automatic switching to the most favorable mode in each case, since the slewing gear for the tubing string has a rotating motor controlled by a two-speed automatic system, the pilot valve of which is assigned a control valve , via which the control valve is constantly supplied with control oil and whose motor has a control line with a pressure switch set to a lower pressure P1 and with a pressure switch set to a higher pressure P2, the pressure switches each having a switching relay with the interposition of an adjustable time relay are connected to the control valve with self-holding.
  • the control valve is addressed via the pressure switches or the assigned relays at precisely such a time in which, for example, the pressure has dropped sharply or has risen sharply, so that a switchover is necessary. Since the individual pressures are set accordingly, a corresponding switchover takes place at the optimum time, the negative stop-and-go effect cannot occur because the self-latching time relay ensures that pressure conditions for changing due to the switchover process the switching state once selected is maintained at a certain point in time. When switching to HT / LS as well as HS / LT mode, the described stop-and-go problems can no longer occur.
  • Such a design has a hydraulic / electronic circuit, a purely hydraulic circuit can also be implemented, for which purpose the pressure switches are designed as hydraulic valves set via the force of the springs, which are connected to the control valve via a hydraulic switch valve and to which a memory and an adjustable throttle are arranged . With a little more switching effort but with the same security, a circuit is secured at the right time.
  • Hydraulic motors of this type are manufactured so that they can be used in both directions of rotation, so that it is advantageous and expedient if a shuttle valve is integrated in the control line. Such a change-over valve can ensure that the control line is pressurized in both directions of rotation of the hydraulic motor.
  • control valve which is important for the application and which is assigned to the pilot valve, can advantageously be realized in that the control valve has a spring which specifies the rest position and an electromagnet. About the corresponding spring, the control valve is automatically brought into the respective position, a uniform application of control oil to the pilot valve is ensured, while when a current is applied to the electromagnet, the valve is switched against the force of the spring, so that the control oil then does not act on the pilot valve can, so that the change in hydraulic setting results automatically.
  • a possibly necessary switchover of the hydraulic motor by hand is possible because, according to one design, an operating mode selector switch with automatic and manual switching is provided, the individual switching positions being indicated by light-emitting diodes.
  • the invention is particularly characterized in that an impact device is created which is simple in structure and control is very precise and safe.
  • the rotary slide valve enables continuous control of both the number of blows and the energy of the blows while maintaining the same performance. Attention has already been drawn to the small dimensions, these reduced dimensions also resulting in particular from the fact that the piston must be arranged outside the housing and thus away from the percussion piston.
  • This external arrangement also has the advantage already mentioned that it is highly adaptable, but also has advantages in the case of repairs that may become necessary. Any mechanical connection between the moving parts can advantageously be dispensed with. Rather, the control is based solely on non-mechanical connections. The control as such can be connected to practically any hammer drill with a different drilling pattern and adapted accordingly, so that there is great adaptability.
  • central lubrication which can be controlled by a valve with a pilot valve, is also provided, so that self-adjustment of the regulating device or pilot unit cannot occur even in the event of strong vibrations.
  • This is a special design of the automatic system, in which the output lever already acts on the plunger via the spring is locked in such a way that the valve cannot be adjusted unintentionally.
  • the slewing gear of the tubing string which ensures a smooth turning of the tubing string, is equipped with a secured two-speed automatic system, so that an automatic changeover is ensured at the most favorable printing time.
  • Fig. 1 shows a schematic representation of an impact device 1, the tubing string 2 is only indicated and here in the form of the impact bar to be connected to the tubing string 2, which is inserted into the housing 3.
  • This tubular string 2 or the impact rod is rotated via the rotating mechanism 5, so that the drill bit located at the opposite end of the tubular string is continuously brought into a different impact position, namely before the impact mechanism 8 becomes active.
  • the non-return device is designated by 7 and the so-called two-speed automatic system by which the rotary motor of the rotating mechanism 5 is regulated.
  • the controller 9 which is used for reversing the percussion piston, which is not shown here.
  • the controller 9 consists of the control housing, the rotary valve and the rotary motor.
  • the central lubrication 10 serves to lubricate the impact device 1.
  • FIGS. 2 and 3 show a section through the control 9 with the rotary slide valve 15, the rotary motor 16, here in the form of a hydraulic drive motor and the control housing 18 connected to the housing 3 via retaining screws 17.
  • a channel 20 is formed in the control housing 18 from the pump connection 21 to the control housing 18 or the rotary slide valve 15, and a channel 22 from the tank connection 23 to the rotary slide valve 15.
  • a channel 24 connects the rotary valve 15 to the percussion piston 25.
  • the percussion piston 25 for its part is formed here with two piston rings 26, 28, the piston ring 26 facing away from the striking end 27 having a larger area A2 than the piston ring 28 with the area A1.
  • the rotary slide valve 15 is supported in a control bush 30 which is formed in the control housing 18 surrounding it.
  • Control bush 30 and rotary valve 15 are formed with corresponding control openings 31, 32 and 33, 34.
  • a control opening 35, 36 designed as a bore is provided at the end 39 opposite the rotary motor 16.
  • control openings 31, 32, 33, 34 are designed as control supports 37 opposite the bore 38 in the form of the control opening 35, 36, these control slots 37 or the corresponding elongated holes have the advantage that a very precise or defined opening point can be specified.
  • 3 pressure relief bores 41, 42 are provided in the housing, namely on both sides of the piston ring 28, in order to be able to quickly derive the pressure that builds up when the percussion piston 25 is pushed back and forth.
  • the pressure relief bores are therefore connected to one another and to the channel 22 and thus to the tank connection 23.
  • the housing 3 provides a plurality of tap holes 43, 44, 45, which connect the outer wall 46 of the housing for the channels 20, 21 and 24.
  • the pressure or pressure build-up in these channels and in the area of the percussion piston 25 can be monitored at any time.
  • the pressure present at the pump connection 21 and thus at the channel 20 moves the percussion piston 25 into the upper position by pressurizing the surface A1. At the same time, the pressure is applied to the rotary valve 15.
  • the rotary motor 16 sets the rotary valve 15 in a rotational movement.
  • the control slots 37 i. H.
  • a connection to the channel 24 is created via the control openings 33, 34 and the inner bore 29.
  • the percussion piston 25 is pressurized on the surface A2.
  • the percussion piston 25 Since hydraulic pressure is constantly present on the surface A1, the percussion piston 25 is moved into the upper position. Moved at the appropriate speed. With the corresponding speed of the rotary slide valve 15, the number of blows and the impact energy of the percussion piston 25 are changed continuously, with a constant output of the hydraulic hammer mechanism.
  • the upper end of the percussion piston 25 in a chamber 48 which is filled with nitrogen as usual.
  • the nitrogen is under around 10 bar pressure.
  • Fig. 4 shows a circuit diagram, in which the mode selector switch 201 is shown approximately in the middle, via which several operating modes can be switched on, namely switch position 1 with the manual actuation of the HS / LT mode and on the other hand switch position 2 with the manual actuation of the HT / LS mode and finally the automatic actuation, which is referred to here as two-speed automatic 6.
  • the following description disregards the two switch positions 1 and 2 with manual actuation, which are only intended for exceptional cases.
  • the operating mode selector switch 201 is accordingly switched to the two-speed automatic position.
  • the contacts 214, 215 and 216 and 217 of the operating mode selector switch 201 are closed, which makes FIG. 4 clear.
  • the electromagnet 202 of the switching valve 203 is voltage-free.
  • the switching valve 203 is in the idle position 204.
  • a free passage of the control oil via the control oil line 205, 206 to the pilot valve 207 of the hydraulic motor 208 is ensured.
  • the pilot valve 207 which is pressurized by the oil in the control oil lines 205, 206, switches the hydraulic motor 208 into the HS / LT mode, which can also be referred to as high speed.
  • the hydraulic pressure in the lines 218, 219 or 220, 221 and thus in the control line 222 increases, depending on the direction of rotation of the hydraulic motor 208.
  • the task of the shuttle valve 223 in the control line 222 is to ensure that line 222 is pressurized in both directions of rotation of hydraulic motor 208.
  • the pressure P2 set on the pressure switch 234 is reached as the pressure on the hydraulic motor 208 increases due to increasing pressure, this switches the contacts 235, 236. This is indicated by the LED 244.
  • the timing relay 237 is switched. Contacts 238, 239 are closed. This energizes the timing relay 232 and closes the contacts 240, 241 and 242, 243 (latching of the timing relay 232). Since the contacts 214, 215 and 216, 217 of the operating mode selector switch 201 are closed, the electromagnet 202 of the switching valve 203 is now connected to the mains voltage.
  • the switching valve 203 switches to position 211. This is indicated by the light-emitting diode 212.
  • the connection of the control oil lines 205, 206 to the pilot valve 207 of the hydraulic motor 208 is interrupted.
  • the oil in the control oil line 206 between the switching valve 203 and the pilot valve 207 of the hydraulic motor 208 is discharged to the tank 213.
  • the pilot valve 207 of the hydraulic motor 208 is depressurized. The hydraulic motor 208 therefore switches to the HT / LS mode.
  • the hydraulic pressure falls into the Lines 218, 219 and 220, 221 (depending on the direction of rotation of the hydraulic motor 208) and the control line 222 for the period T1 under the pressures P1 and P2 set at the pressure switches 224, 234.
  • the pressure drop in the lines is determined by the structural structure of such a hydraulic motor 208.
  • the pressure P2 of the pressure switch 34 is set to a maximum value corresponding to the system.
  • the set pressure P2 is greater than P1.
  • the pressure switch 234 opens the contacts 235, 236, the voltage at the relay 237 drops and opens the contacts 238, 239.
  • the contacts 240, 241 and 242, 243 remain closed (latching of the timing relay 232).
  • the voltage at relay 27 drops and contacts 228, 229 and 230, 231 open for the period T1 (opening of contacts 228, 229 activates the timing of relay 232).
  • Relay 232 must be maintained for at least this time period T1, since otherwise the voltage at electromagnet 202 of switching valve 203 drops and pilot valve 207 of hydraulic motor 208 switches back to HS / LT mode.
  • This switchover process from HT / LS to HS / LT mode and vice versa would be repeated continuously (stop-and-go effect). Continuous drilling would not be possible. However, the stop-and-go effect is prevented by the integrated self-retention.
  • the latching is achieved by the time relay 232, which has a time setting.
  • the circuit diagram of the hydraulically switched hydraulic motor according to FIG. 5 largely corresponds to that according to FIG. 4.
  • the electromagnet 247 of the switching valve 248 is voltage-free when the HS / LT mode is operated manually.
  • the switching valve 248 is switched into the rest position 249 by the spring 277.
  • the hydraulic pressure present in the control line 222 when the hydraulic motor 208 is operating is blocked.
  • the switching valve 248 switches to position 250, the valves 203, 252 and 257 are in the rest position and the valve 262 in the position 263.
  • the lines 268, 269, 270, the hydraulic accumulators 271, 272 and the control heads 255, 260 are in the rest position 249 of the switching valve 248 is relieved of pressure via the tank line 251.
  • the valves 252, 257 are brought into the rest position 253, 258 by the springs 278, 279. Due to the rest position of the 257, the line 273 and the control head 265 of the valve 262 are relieved of pressure via the tank line 261.
  • the valve 262 is switched to the position 263 and fixed by the catch 281.
  • the electromagnet 202 of the switching valve 203 is voltage-free.
  • the valve 203 is switched to the rest position 204 via the spring 282.
  • a free passage of the control oil onto the pilot valve 207 which is pressurized by the control oil of the lines 276, 205 and 206, switches the hydraulic motor 208 into the HS / LT mode according to FIG. 5.
  • This pilot control unit 101 consists of the housing 103, from which the plungers 104 protrude, which are loaded by springs 105.
  • the control device 115 with the input lever 106, the locking element 102 and the output lever 107 is placed on the housing 103, the input lever 106 being guided on the quadrant 108 and being pivotable by 25 ° to either side.
  • the entire control device 115 is encased by a rubber bellows 109, which is fixed on the holding plate 116 and on the web 119 of the input lever 106.
  • the locking element 102 which is arranged between the input lever 106 and the plungers 104, consists of a plurality of locking piece units 110, 111 which are pressed into a locking position via the spring 105 and the plungers 104, so that actuation of the pilot control unit 101 is then not possible unless it is done directly and deliberately via the input lever 106.
  • the locking pieces 110, 111 which are accommodated in the locking element 102 in such a way that they cannot be identified in the illustration according to FIG. 6, are mounted so as to act counter to one another, so that when they are pressed against the plunger 104, they pivot into the locking position. They pivot about the pivot point 120, which, as indicated, is placed relatively far downward, so that even with slight movements of the tappet or the tappet 104, the locking piece units 110, 111 are securely engaged. This movement is supported by a compression spring 121, which is likewise not visible here, so that the pilot control unit or pilot valve 150 is blocked even at relatively low restoring forces.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Automation & Control Theory (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
EP95108205A 1994-06-03 1995-05-30 Dispositif à percussion hydraulique avec réglage continu du nombre et de l'intensité des coups Expired - Lifetime EP0685301B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4419499 1994-06-03
DE4419499A DE4419499A1 (de) 1994-06-03 1994-06-03 Hydraulisches Schlaggerät mit stufenlos regelbarer Schlagzahl und Schlagenergie

Publications (2)

Publication Number Publication Date
EP0685301A1 true EP0685301A1 (fr) 1995-12-06
EP0685301B1 EP0685301B1 (fr) 1999-12-29

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP95108205A Expired - Lifetime EP0685301B1 (fr) 1994-06-03 1995-05-30 Dispositif à percussion hydraulique avec réglage continu du nombre et de l'intensité des coups

Country Status (9)

Country Link
US (1) US5667022A (fr)
EP (1) EP0685301B1 (fr)
JP (1) JP3419591B2 (fr)
AT (1) ATE188159T1 (fr)
DE (2) DE4419499A1 (fr)
DK (1) DK0685301T3 (fr)
ES (1) ES2142425T3 (fr)
PL (1) PL177496B1 (fr)
PT (1) PT685301E (fr)

Cited By (2)

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WO2013143520A1 (fr) * 2012-03-30 2013-10-03 Atlas Copco Construction Tools Gmbh Vanne
CN107743424A (zh) * 2015-06-15 2018-02-27 费尔有限公司 用于除芯的设备

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DE19836389C1 (de) 1998-08-12 2000-04-13 Deilmamm Haniel Maschinen Und Bohrvorrichtung mit Doppelschlagsystem
US6557652B2 (en) * 2000-05-18 2003-05-06 Guenter Klemm Method for performing ground or rock work and hydraulic percussion device
US7008340B2 (en) * 2002-12-09 2006-03-07 Control Flow Inc. Ram-type tensioner assembly having integral hydraulic fluid accumulator
US6968900B2 (en) * 2002-12-09 2005-11-29 Control Flow Inc. Portable drill string compensator
FI116513B (fi) * 2003-02-21 2005-12-15 Sandvik Tamrock Oy Iskulaite
DE102004035306A1 (de) * 2004-07-21 2006-03-16 Atlas Copco Construction Tools Gmbh Druckmittelbetriebene Schlagvorrichtung insbesondere Hydraulikhammer
US20060180314A1 (en) * 2005-02-17 2006-08-17 Control Flow Inc. Co-linear tensioner and methods of installing and removing same
FR2902821B1 (fr) * 2006-06-22 2008-08-22 Montabert Soc Par Actions Simp Appareil rotopercutant hydraulique du type perforatrice
KR100891189B1 (ko) * 2007-02-22 2009-04-06 정영재 브레이커 밸브장치의 밸브실 구조
EP2140833A1 (fr) * 2008-07-03 2010-01-06 Curozone USA Inc. Appareil de traitement dentaire
FR2983760B1 (fr) * 2011-12-09 2014-08-15 Montabert Roger Procede de commutation de la course de frappe d'un piston de frappe d’un appareil a percussions
FR3007154B1 (fr) * 2013-06-12 2015-06-05 Montabert Roger Procede de commande de l’energie d’impact d’un piston de frappe d’un appareil a percussions
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system

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WO2013143520A1 (fr) * 2012-03-30 2013-10-03 Atlas Copco Construction Tools Gmbh Vanne
CN104145121A (zh) * 2012-03-30 2014-11-12 建筑工具有限公司 阀
CN107743424A (zh) * 2015-06-15 2018-02-27 费尔有限公司 用于除芯的设备

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ES2142425T3 (es) 2000-04-16
EP0685301B1 (fr) 1999-12-29
PT685301E (pt) 2000-05-31
DK0685301T3 (da) 2000-06-13
US5667022A (en) 1997-09-16
PL308855A1 (en) 1995-12-11
DE59507505D1 (de) 2000-02-03
JPH0886182A (ja) 1996-04-02
JP3419591B2 (ja) 2003-06-23
DE4419499A1 (de) 1995-12-07
PL177496B1 (pl) 1999-11-30
ATE188159T1 (de) 2000-01-15

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