EP0685301B1 - 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
EP0685301B1
EP0685301B1 EP95108205A EP95108205A EP0685301B1 EP 0685301 B1 EP0685301 B1 EP 0685301B1 EP 95108205 A EP95108205 A EP 95108205A EP 95108205 A EP95108205 A EP 95108205A EP 0685301 B1 EP0685301 B1 EP 0685301B1
Authority
EP
European Patent Office
Prior art keywords
control
valve
striking
tool according
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95108205A
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German (de)
English (en)
Other versions
EP0685301A1 (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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Publication date
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Publication of EP0685301A1 publication Critical patent/EP0685301A1/fr
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Publication of EP0685301B1 publication Critical patent/EP0685301B1/fr
Anticipated expiration legal-status Critical
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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 the end of the pipe string and the slewing gear for the tubular support housing that one in a Inner bore reciprocable and on the tubing string acts on the percussion piston, via a rotary valve is reversible with a rotary motor, with rotary valve and Rotary motor arranged independently of the percussion piston on or in the housing are.
  • a hydraulic impact device is from DE-OS 22 06 014.6 known. This impact device is for reversing necessary device as the actual percussion piston surrounding Rotary valve designed. Aside from the elaborate Control is a significant disadvantage that alone Due to this design, the entire device has considerable dimensions required. Another disadvantage is that the provided regulation the performance with the change of Number of strokes and also the impact energy changes, so that the overall control is relatively imprecise. Corresponding also applies to the device according to DE-OS 43 28 278.4, in turn the rotary valve the percussion piston is arranged surrounding. It is powered by a rotary motor which is also used for the offset of the pipe string serves, by moving the interlocking Gears also separate the rotary valve drive from the rotating device of the pipe string is possible.
  • the intended The device thus has mechanical connections especially via gears, which in turn increases Manufacturing effort and in particular a certain dependency of impact rate, impact energy and performance with brings itself.
  • extension bores manufacture or different hammers it is not possible to use extension bores manufacture or different hammers to operate with different values because that once appropriately manufactured overall device as such must be operated.
  • a pneumatic impact device US Pat. No. 1,946,989
  • rotary valves and rotary motors attached to the housing and via channels with the percussion piston connected, but so that both at the same time and over the same pressure source are supplied. An independent regulation of stroke frequency and working pressure is not possible.
  • the invention is therefore based on the object Impact device to create a simple and easy to use has different adaptable control requirements.
  • the Rotary vane regardless of the rotary motor here in the form of a hydraulic Drive motor on the one hand via channels with the Pumps and tank connection and on the other hand with trained on both sides Piston surfaces of the percussion piston is connected and that the rotary motor has its own supply line. It differs from the prior art in such a case Construction possible, initially relatively small build because the rotary valve is completely independent of the respective Impact device can be trained and positioned. It surrounds not the percussion piston, but a separate one Component that then only via the corresponding channels and therefore only hydraulically and not mechanically with the Percussion piston is connected. The rotary valve as such is trained so that a changeover or adjustment relatively quickly of the impact device as a whole is possible.
  • a useful embodiment of the invention provides that the rotary valve has a control housing, which is detachable with is connected to the housing.
  • the detachable connection between Control housing and housing or rotary valve and ultimately Percussion pistons can make such a control practical can be attached to each hammer or a company adapted to the respective drilling pattern.
  • the Rotary vane can also be used with large hammers in this way For example, demolition hammers are used he continues to build small and therefore just use it these large devices because it is independent of the respective size of the percussion piston can be realized can. It is also advantageous that extension bores with such an impact device can be made because the striking mechanism advantageously switched off and accordingly fixing or connecting the next drill pipe can be without the percussion Disadvantages can result.
  • Rotary slide valve from a control socket arranged in the control housing is surrounded by those provided in the rotary valve and corresponding control openings designed as control slots trained control openings, which in turn connected to the channels for pump and tank connection are. It is via the control socket surrounding the rotary valve possible to keep the connection to the respective channel, while the rotary valve turns and without leaks or other problems during this time may occur. Rather, it stands with the superior of the respective tax openings in front of the corresponding ones Control openings in the control socket immediately the pressure medium in the corresponding channel or it can be through the corresponding Drain the channel under pressure. This means that very precisely can be controlled very quickly and so that the Performance as such remains constant.
  • Control openings both in the rotary valve and in the control socket also coordinated in terms of dimensions, see above that the initiate and carry out the control process necessary hydraulic quantities are available at short notice stand. Due to the training as control slots in the used control openings the point of contact or the defined opening point can be precisely predetermined.
  • the invention provides that the rotary motor of the rotary valve is releasable with the control housing connected and continuously adjustable. So that can only the rotary motor can be replaced and that in very short time, so that the performance of the the respective rotary valve the respective requirements are good is to be adjusted. Since the rotary motor is infinitely adjustable, the impact device can change relatively easily Conditions to be adjusted.
  • the necessary ones Providing quantities is a rotary valve, in which the control openings on the rotary motor opposite End of the rotary valve that connects this to the channel Connect the percussion piston as a bore.
  • the Holes open somewhat more slowly than the longitudinal slots in the Rotary vane, but that's enough, because first of all the Penetrate hydraulic fluid into the inner channel of the rotary valve must, the inner channel being a blind hole acts in the rotary valve. It also passes through this hole yes the hydraulic fluid from the rotary valve into the channel a, with fluid in the channel either way, so that the necessary pressure builds up relatively quickly can.
  • a percussion piston with the greatest possible impact to specify it is provided that the percussion piston with two in Piston rings formed at a distance from each other is, the opposite of the frustoconical striking end Piston ring has a larger area than the area of the the piston ring facing the striking end, the surface of which the channel is permanently connected to the pump connection.
  • the percussion piston is formed with two piston rings, among other things also specify the length of the percussion piston accordingly to be able to.
  • To the pressure pad in particular on both on both sides of the piston ring assigned to the striking end To be able to dismantle quickly and accurately is on the part of Invention provided 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 bore is provided is.
  • This Pressure relief holes lead into the channel to the tank connection, so that the released liquid is removed for a short time and can be brought out of the housing.
  • the invention also provides for continuous monitoring, if necessary before that the channels for pump and tank connection as well to the percussion piston via stitch holes with the Connect the outer wall of the housing. It can be used here anytime a measuring device can be connected, both the quantities as well as in particular the amount of pressure to be applied can monitor. Such measurements are temporarily not deemed necessary or not desired, it is easily possible, the tap holes on the outer wall of the housing to close, so that then a leak in this Area can be easily prevented. Theoretically conceivable it is natural to have both of these tap holes Connect the hose connection that contains the escaping pressure medium leads back to the tank without any interference the environment can occur.
  • This type of pilot valve is based on a used in principle known element that as self-locking mechanical element originally for aircraft control systems has been developed and used. Cleverly is the restoring force without using ratchets, Jacks, rubbers or the like are automatically blocked, whereby the Self-locking becomes safer the higher the restoring force is. About the locking piece units that can be pushed against each other the tappets or the assigned springs to such an extent that a effective locking even under extreme conditions is.
  • An improved two-speed motor comes for the slewing gear used to create an automatic circuit in each to guarantee cheapest mode by turning the slewing gear for the Pipe string one controlled by a two-speed automatic Rotary motor has a pilot valve associated with a control valve is, through which the control valve constantly with control oil is acted upon and their engine with a control line a pressure switch set to a lower pressure P1 and with a pressure switch set to a higher pressure P2 has, the pressure switches each have a Switching relay with the interposition of an adjustable Self-holding timing relay connected to the control valve are.
  • the control valve will via the pressure switches or the assigned relays in each case addressed exactly at such a point in time, for example the pressure has dropped or risen sharply is, so that a switchover is required.
  • There the individual pressures are set accordingly an appropriate switchover at the optimal time, the negative stop-and-go effect cannot occur, because it is ensured by the self-locking timing relay will that even because of the switching process changing pressure conditions for a certain point in time the switching state once selected is retained. Either when switching to HT / LS as well as in HS / LT mode it does not belong to the described stop-and-go problems come more.
  • Such a version has a hydraulic / electronic Circuit is a purely hydraulic circuit to realize as well what the pressure switches as over the Hydraulic valves adjusted for the force of the springs are connected to the control valve via a hydraulic switch valve connected and which a memory as well as an adjustable Throttle are arranged. With a little more switching effort but with the same certainty is a circuit here too secured at the right time.
  • Such hydraulic motors are in both directions made usable so that it is beneficial and convenient is when a shuttle valve is integrated in the control line is.
  • the pressure can be applied via such a shuttle valve the control line in both directions of rotation of the Hydraulic motor can be guaranteed.
  • a possible changeover of the hydraulic motor by hand is possible because according to training Mode selector switch with automatic and manual switching is provided, the individual switching positions over LEDs are displayed.
  • the invention is characterized in particular by that an impact device is created that is simple in construction and control is very precise and safe.
  • the rotary valve enables stepless regulation of both the beat number like the impact energy with constant performance.
  • On the Small dimensions have already been pointed out these reduced dimensions in particular reveal that the piston outside the housing and thus from Arrange the percussion piston away.
  • This external arrangement also has the advantage already mentioned that so that there is great adaptability beyond that but also advantages for repairs that may become necessary having.
  • any mechanical No connection between the moving parts become. Rather, the control is based solely on non-mechanical connections.
  • the controller as such can be used on practically every hammer drill with different Drilling pattern connected and adjusted accordingly that there is great adaptability.
  • Fig. 1 shows a schematic representation of a Impact device 1
  • the tubing string 2 is only indicated specifically in the form of the pipe string 2 to be connected Impact bar, which is inserted into the housing 3.
  • the slewing gear 5 becomes this pipe string 2 or the impact rod rotated so that at the opposite end of the tubing string located drill bit continuously into another Striking position is brought before the striking mechanism 8 becomes active in each case.
  • the check device is designated and at 6 the so-called two-speed automatic, via which the rotating motor of the slewing gear 5 is controlled.
  • the control is also generally designated 9, those for reversing the percussion piston not shown here is used.
  • 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.
  • the valve designed as a proportional valve 11 regulates the oil quantity for the drive motor of the hammer mechanism control and controls the hydraulic pilot valve 12 turn on the valve 11.
  • FIGS 2 and 3 show a section through the Control 9 with the rotary valve 15, the rotary motor 16, here in Form of a hydraulic drive motor and the one with retaining screws 17 connected to the housing 3 control housing 18th
  • control housing 18 In the control housing 18 is a channel 20 from the pump connection 21 to the control housing 18 or the rotary valve 15 and a channel 22 from the tank connection 23 to the rotary valve 15 trained.
  • a channel 24 connects the rotary valve 15 with the percussion piston 25.
  • the percussion piston 25 in turn is here with two piston rings 26, 28, the end of the striking end 27 facing away piston ring 26 has a larger area than A2 the piston ring 28 with the area A1.
  • the rotary valve 15 is stored in a control bushing 30 which is formed surrounding it in the control housing 18.
  • Control socket 30 and rotary valve 15 are with corresponding control openings 31, 32 and 33, 34 are formed.
  • control openings 31, 32 and 33, 34 are formed on the end 39 opposite the rotary motor 16 as a bore trained control opening 35, 36 provided.
  • control openings 31, 32, 33, 34 are as Control support 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 can.
  • 3 pressure relief holes 41, 42 provided on both sides of the piston ring 28, so when the percussion piston 25 is pushed back and forth to be able to quickly derive the pressure that builds up.
  • the pressure relief holes are therefore with each other and with the channel 22 and thus connected to the tank connection 23.
  • the housing 3 sees several tap holes 43, 44, 45 before, which connects to the outer wall of the housing Bring 46 for channels 20, 21 and 24. This can be done at any time the pressure or the pressure build-up in these channels and are monitored in the area of the percussion piston 25.
  • the rotary motor 16 moves the rotary valve 15 into one Rotational movement. This rotation is over the control slots 37, d. H. via the control openings 33, 34 and the Inner bore 29 creates a connection to the channel 24. Thereby the percussion piston 25 on the surface A2 with pressure acted upon.
  • Fig. 4 shows a circuit diagram, the approximately in the middle Mode selector switch 201 is reproduced, via the several operating modes can be switched on, namely once switch position 1 with manual actuation of the HS / LT Mode and on the other hand switch position 2 with the manual Actuation of HT / LS mode and finally automatic Actuation, referred to here as two-speed automatic 6 is. Be disregarded in the description below the two switch positions 1 and 2 with the manual Actuation, which is only intended for exceptional cases are.
  • the mode selector switch 201 is therefore accordingly switched to the two-speed automatic position. Contacts 214, 215 and 216 and 217 of the mode selector switch 201 are closed, which is clear from FIG. 4 makes. In this switching position, the electromagnet 202 is the Switching valve 203 voltage-free. The switching valve 203 is stopped at rest 204.
  • a free passage of the control oil through the control oil line 205, 206 on the pilot valve 207 of the hydraulic motor 208 is guaranteed.
  • the pilot valve 207 which by the oil the control oil lines 205, 206 are pressurized, switches the hydraulic motor 208 to HS / LT mode, which too can be called rapid run.
  • the torque of the hydraulic motor 208 increases during operation, the hydraulic pressure in the Lines 218, 219 and 220, 221 and thus in the control line 222 depending on the direction of rotation of the hydraulic motor 208.
  • the task of the shuttle valve 223 in the control line 222 is pressurizing line 222 to ensure in both directions of rotation of the hydraulic motor 208.
  • the hydraulic pressure in the control line is reached 222 the pressure P1 set at the pressure switch 224, contacts 225, 226 are closed, relay 227 becomes controlled and closes the contacts 228, 229 and 230, 231. This is indicated by the LED 233.
  • the connection the control oil lines 205, 206 to the pilot valve 207 of the Hydraulic motor 208 is interrupted.
  • the oil of 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 hydraulic motor 208 is depressurized. The hydraulic motor 208 therefore switches to the HT / LS mode.
  • the hydraulic pressure drops in 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 among those set on the pressure switches 224, 234 Press P1 and P2.
  • the pressure drop in the lines is due to the structural structure of such a hydraulic motor 208.
  • the pressure P2 of the pressure switch 34 is at a maximum value corresponding to the system. Of the set pressure P2 is greater than P1.
  • the pressure switch 234 opens the contacts 235, 236 which Voltage at relay 237 drops and opens contacts 238, 239. Contacts 240, 241 and 242, 243 remain closed (Time relay 232 latches).
  • the contacts 225, 226 of the Open pressure switch 224 This causes the voltage at the relay to drop 27 and the contacts 228, 229 and 230, 231 open for the time period T1 (by opening contacts 228, 229 relay 232 timeout enabled). For at least this Period T1 must ensure that relay 232 remains locked be otherwise the voltage at the electromagnet 202 of the switching valve 203 drops and the pilot valve 207 des Hydraulic motor 208 switches back to HS / LT mode.
  • the circuit diagram of the hydraulically switched hydraulic motor 5 largely corresponds to that of FIG. 4.
  • Electromagnet 247 of the switching valve 248 is voltage-free.
  • the Switch valve 248 is in the rest position 249 by spring 277 switched.
  • the operation of the hydraulic motor 208 in the Control line 222 pending hydraulic pressure is blocked.
  • 250 is another switch position, with 251 that Tank line, with 252 a valve, with 253 the rest position and 254 denotes another position.
  • the switching valve 248 namely switches to position 250, valves 203, 252 and 257 are at rest and valve 262 is in the position 263.
  • Lines 268, 269, 270, hydraulic accumulators 271, 272 and the control heads 255, 260 are in the rest position 249 of the switching valve 248 is depressurized via the tank line 251.
  • the springs 258, 279 are the valves 252, 257 brought to rest 253, 258. Through the rest position of the 257 becomes the line 273 and the control head 265 of the valve 262 relieved of pressure via the tank line 261.
  • the valve 262 is switched to position 263 and by the detent 281 fixed.
  • the electromagnet 202 of the switching valve 203 is voltage-free.
  • the valve 203 is in the rest position via the spring 282 204 switched.
  • a free passage of the tax oil to the pilot valve 207, which is controlled by the control oil of the lines 276, 205 and 206 is pressurized, switches the hydraulic motor 208 in the HS / LT mode according to FIG. 5.
  • This pilot control unit 101 consists of the housing 103, from which the plungers 104 protrude, the springs 105 are burdened.
  • the control device is placed on the housing 103 115 with the input lever 106, the locking element 102 and the output lever 107, wherein the input lever 106 on Quadrant 108 is guided and by 25 ° on both sides can be pivoted.
  • the entire control device 115 is encased by a rubber bellows 109, which is once on the holding plate 116 and on the web 119 of the input lever 106 is set.
  • the locking element 102 which is between the input lever 106 and the plunger 104 is arranged consists of several Blocking piece units 110, 111, which via the spring 105 and the Ram 104 are pressed into a locking position so that then actuation of the pilot control unit 101 is not possible unless it is done directly and deliberately using the input lever 106.
  • the locking pieces 110, 111 which are in the locking element 102 are housed that they are in the representation according to FIG. 6 not identifiable will act against each other stored so that they can be pressed against the plunger 104 in the Swivel locked position. They swivel around the pivot point 120, which, as indicated, is relatively far down, so that even with slight movements of the plunger or Tappet 104 engages the locking piece units 110, 111 done safely. This movement is also here compression spring 121 not visible supports, so that already at relatively low restoring forces blocking the pilot control unit or the pilot valve 150.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Automation & Control Theory (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (14)

  1. Appareil de frappe hydraulique (1) comprenant un corps (3) qui reçoit une extrémité de la lire de tubes et qui présente le mécanisme de rotation (5) pour la ligne de tubes (2), corps qui reçoit un piston de frappe (25) mobile a mouvement alternatif dans un perçage intérieur et qui agit sur la lire de tubes (2), et qui peut être inversé au moyen d'un tiroir tournant (15) muni d'un moteur de rotation (16), le tiroir tournant (15) et le moteur de rotation (16) étant agencés sur ou dans le corps (3) indépendamment du piston de frappe (25),
    caractérisé
    en ce que le tiroir tournant (15) est relié, indépendamment du moteur de rotation (16), constitué ici par un moteur d'entraínement hydraulique, d'une part, par des canaux (20, 22, 24), au raccord de pompe et de bâche (21, 23), et, d'autre part, à des surfaces de piston (A1, A2) du piston de frappe (25), qui sont formées sur les deux cotés, et en ce que le moteur de rotation (16) dispose d'une conduite d'alimentation qui lui est propre.
  2. Appareil de frappe selon la revendication 1,
    caractérisé
    en ce que le tiroir tournant (15) présente un corps de commande(18) qui est relié au corps (3) de façon séparable.
  3. Appareil de frappe selon la revendication 1,
    caractérisé
    en ce que le tiroir tournant (15) est entouré d'une fourrure de commande (30) disposée dans le corps de commande (18) et qui présente des ouvertures de commande (31, 33, 35) agencées en correspondance avec les ouvertures de commande (32, 34, 36) prévues dans le tiroir tournant et constituées par des fentes de commande (37), et qui, de leur coté, sont reliées aux canaux (20, 22) pour le raccord de pompe (21) et le raccord de bâche (23).
  4. Appareil de frappe selon la revendication 1 à la revendication 3,
    caractérisé
    en ce que le moteur de rotation (16) du tiroir tournant (15) est relié au corps de commande (18) de façon détachable et réglable sans à-coups.
  5. Appareil de frappe selon la revendication 1 à la revendication 3
    caractérisé,
    en ce que les ouvertures de commande (35, 36) situées à l'extrémité (39) du tiroir tournant (15) qui est à l'opposé du moteur de rotation (16) et qui le relient au canal (24) aboutissant au piston de frappe (25) sont constitués par un perçage (38).
  6. Appareil de frappe selon la revendication 1
    caractérisé
    en ce que le piston de frappe (25) est équipé de deux bagues de piston (26, 28) formées à distance l'une de l'autre, la bague de piston (26) qui est éloignée de l'extrémité de frappe tronconique (27) présentant une plus grande surface (A2) que la surface (A1) de la bague de piston (28) dirigée vers l'extrémité de frappe, dont la surface (A1) est reliée en permanence au raccord de pompe (21) par l'intermédiaire du canal (20).
  7. Appareil de frappe selon la revendication 1,
    caractérisé
    en ce que, sur les deux côtés de la bague de piston (28) qui est relié en permanence au raccord de pompe (21) par l'intermédiaire du canal 20, est prévu un raccordement aboutissant à un perçage (41, 42) de décharge de la pression.
  8. Appareil de frappe selon la revendication 1 et la revendication 3
    caractérisé
    en ce que les canaux (20, 22, 24) aboutissant au raccord de pompe (21) et au raccord de bâche (23) ainsi qu'au piston de frappe (25) sont en supplément en communication avec la paroi extérieure (46) du corps par l'intermédiaire de perçages dérivés (43, 44, 45).
  9. Appareil de frappe selon la revendication 1,
    caractérisé
    en ce que la commande (9) comportant le tiroir tournant (15) et le moteur de rotation (16) est munie d'un graissage central (10) qui est commandé par une soupape (11) munie d'une soupape de pilotage (12) qui présente un levier de sortie (107) disposé entre un levier d'entrée (106) et des poussoirs (104) et qui, d'une part, est constitué de manière à charger les poussoirs (104) et réciproquement à être chargé par ces derniers et, d'autre part, est influencé par un élément d'arrêt (102) guidé le long d'un quadrant (108) et relié au levier d'entrée (106), l'élément d'arrêt (102) étant équipé de plusieurs unités de pièces d'arrêt (110, 111) qu'on peut faire coulisser les unes par rapport aux autres.
  10. Appareil de frappe selon la revendication 1,
    caractérisé
    en ce que le mécanisme de rotation (5) agissant sur la ligne de tubes (2) présente un moteur de rotation réglé par l'intermédiaire d'un dispositif automatique à deux vitesses (6), à la soupape pilote (207) duquel est associée une soupape de commande (203) par l'intermédiaire de laquelle la soupape de commande (203) est chargée en permanence avec de l'huile de commande, et dont le moteur (208) dispose d'une conduite de contrôle (222) munie d'un interrupteur à pression (224) réglé sur une pression inférieure P1 et d'un interrupteur à pression (234) réglé sur une pression supérieure P2, les interrupteurs à pression (224, 234) étant reliés à la soupape de commande (203) chacun par l'intermédiaire d'un relais de commutation (227) avec interposition d'un relais à temps réglable (232, 237) muni d'un auto-maintien.
  11. Appareil de frappe selon la revendication 1,
    caractérisé
    en ce que les interrupteurs à pression (224, 234) sont constitués par des soupapes hydrauliques (252, 257) réglées par l'intermédiaire de la force des ressorts (278, 279), qui sont reliées à la soupape de commande (203) par l'intermédiaire d'une soupape de distribution hydraulique (262) et en amont desquelles sont agencés un accumulateur (272, 271) ainsi qu'un étranglement réglable (283, 284).
  12. Appareil de frappe selon la revendication 10,
    caractérisé
    en ce qu'une soupape à deux voies (223) est intégrée dans la conduite de contrôle (222).
  13. Appareil de frappe selon la revendication 10,
    caractérisé
    en ce que la soupape de commande (203) dispose d'un ressort (282) qui prédétermine la position de repos (204) et d'un électro-aimant (202).
  14. Appareil de frappe selon la revendication 10,
    caractérisé
    en ce qu'il est prévu un commutateur sélecteur de mode de travail (201), avec automatisme et commutation manuelle, et des diodes électroluminescentes (212, 233, 244, 246) qui indiquent les différentes positions de commutation.
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
DE4419499A DE4419499A1 (de) 1994-06-03 1994-06-03 Hydraulisches Schlaggerät mit stufenlos regelbarer Schlagzahl und Schlagenergie
DE4419499 1994-06-03

Publications (2)

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

Family

ID=6519754

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)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102012012297A1 (de) * 2012-03-30 2013-10-02 Atlas Copco Construction Tools Gmbh Ventil
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
AT517385B1 (de) * 2015-06-15 2019-02-15 Fill Gmbh Vorrichtung zum Entkernen

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US1946989A (en) * 1931-12-17 1934-02-13 Ingersoll Rand Co Valve for rock drills
CH559088A5 (fr) * 1971-12-23 1975-02-28 Sig Schweiz Industrieges
CH584591A5 (fr) * 1974-05-20 1977-02-15 Bosch Gmbh Robert
ES464093A1 (es) * 1977-11-12 1978-12-16 Luis Miguel Castejon Castan Perfeccionamientos en los sistemas de fluidos alternantes y aparato para su realizacion.
US4211291A (en) * 1978-03-06 1980-07-08 Smith International, Inc. Drill fluid powered hydraulic system
CH638587A5 (de) * 1979-02-12 1983-09-30 Uster Spindel Motoren Maschf Schlagbohrhammer.
US4694912A (en) * 1984-11-01 1987-09-22 Glendo Corporation Controlled impact power tool
JPH0513509Y2 (fr) * 1986-09-09 1993-04-09
RU1778289C (ru) * 1988-05-04 1992-11-30 Карагандинский политехнический институт Гидравлическа бурильна машина
FR2647870B1 (fr) * 1989-06-06 1991-09-06 Eimco Secoma Appareil de percussion hydraulique avec dispositif d'amortissement des ondes de choc en retour
JPH06108770A (ja) 1992-08-31 1994-04-19 Sig (Schweiz Ind Ges) ロックドリル用ドリル装置
DE4322014C2 (de) 1993-07-02 1995-06-22 Daimler Benz Ag Verfahren zum Ansteuern einer Zündspule einer Zündeinrichtung für Brennkraftmaschinen und Schaltungsanordnung zur Durchführung des Verfahrens

Also Published As

Publication number Publication date
JPH0886182A (ja) 1996-04-02
US5667022A (en) 1997-09-16
EP0685301A1 (fr) 1995-12-06
ATE188159T1 (de) 2000-01-15
PL308855A1 (en) 1995-12-11
PL177496B1 (pl) 1999-11-30
DK0685301T3 (da) 2000-06-13
DE4419499A1 (de) 1995-12-07
PT685301E (pt) 2000-05-31
ES2142425T3 (es) 2000-04-16
JP3419591B2 (ja) 2003-06-23
DE59507505D1 (de) 2000-02-03

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