EP0672506B1 - Marteau à percussion hydraulique - Google Patents

Marteau à percussion hydraulique Download PDF

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Publication number
EP0672506B1
EP0672506B1 EP94117814A EP94117814A EP0672506B1 EP 0672506 B1 EP0672506 B1 EP 0672506B1 EP 94117814 A EP94117814 A EP 94117814A EP 94117814 A EP94117814 A EP 94117814A EP 0672506 B1 EP0672506 B1 EP 0672506B1
Authority
EP
European Patent Office
Prior art keywords
pressure
line
working piston
piston
working
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
EP94117814A
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German (de)
English (en)
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EP0672506A1 (fr
Inventor
Emil Dipl.-Ing. Weber
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Individual
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Individual
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Publication of EP0672506A1 publication Critical patent/EP0672506A1/fr
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Publication of EP0672506B1 publication Critical patent/EP0672506B1/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
    • 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

Definitions

  • the invention relates to a hydraulic hammer, especially for advancing objects in the Ground.
  • the pressure-controlled Valve connects the rear space of the working cylinder the supply line when the working piston is its has reached the front end position. During the return stroke the pressure in the working area increases. If this pressure exceeds a certain value, then connects the pressure-controlled valve to the rear area with the return line. In this way the Working piston pumped hydraulic fluid and a certain Exchange of the amount of liquid contained in the rear area causes. The main part of the impact energy is through the Pressure gas accumulator applied. The fact that from the Back space of the working piston pressure fluid is drained when the pressure in this back space is at its maximum has reached, some of the printing energy is lost, which deteriorates the efficiency of the hammer.
  • the invention has for its object a hydraulic To create a hammer in which the ratio improved from impact energy to power consumption is.
  • a particular advantage is that none Print energy is lost.
  • increased pressure force of the working piston will, however, this additional energy will be used recovered on the working stroke when the Pressure gas accumulator relaxed.
  • the hammer drill overall no higher consumption of hydraulic Pressure energy has as a hammer drill without compressed gas storage.
  • the impact energy that comes with Support is achieved through the compressed gas storage much larger than in a system without compressed gas storage.
  • the pressure controlled valve ensures that at the beginning of the return stroke in the rear area of the working cylinder there is a defined pressure. During the return stroke of the working piston increases this Pressure steadily because the working piston turns into a complete closed system, from which no hydraulic fluid escapes. Therefore also find no energy losses take place, with the exception of friction losses. It is also achieved that the compressed gas storage a defined braking energy for the return stroke applies, the braking force with the return stroke of the Working piston increases steadily without pressure surges or shock.
  • the efficiency is particularly good if the Compressed gas storage in connection with a hammer is used, in which the return displacement constantly the is exposed to high delivery pressure.
  • the hydraulic fluid which displaces from the back area during the working stroke will remain under pressure and will not be in the tank relaxed into it.
  • the invention is generally for advancing objects, e.g. Spuntbohlen can be used, but is suitable also for rock breakers and drilling devices.
  • the hammer is preferably at the rear end of the item arranged as an external hammer, but it can also be designed as a deep hole hammer.
  • the hammer drill shown in Fig. 1 has a hammer housing 20 on that to a pressure line 10 and to a unpressurized return line 12 is connected, and in which a working cylinder 21 is included.
  • the working piston 22 In the working cylinder 21, the working piston 22 is guided.
  • the front end of the working piston 22 strikes one Anvil surface 23 of an adapter 24 in the hammer housing 20 is guided longitudinally within limits.
  • the adapter 24 is with the object to be driven coupled.
  • the working piston 22 has a forward facing annular return stroke surface RF on the annular front cylinder space (return stroke space) 26 limited.
  • This Cylinder chamber 26 is always connected via a line 27 the pressure line 10 connected.
  • the return stroke area RF delimits a thickened section 28 of the working piston.
  • the other limitation of section 28 is of an annular surface 29 is formed, to which a thinner Section 30 joins. Behind the thinner section 30 again follows a thicker section 31, the rear End is formed by a work surface AF.
  • the working area AF limits the rear cylinder space 33 of the working cylinder 21.
  • the working surface AF is greater than by a factor of 2 to 3 the return stroke area RF.
  • the return stroke surface RF moves along several Control grooves 34a, 34b, 34c in the front cylinder space 26.
  • the annular surface 29 moves along a control groove 35.
  • Die Control grooves 34a, 34b, 34c are connected to a control line 37 connected. There are two of these connections closed with locking devices 32 while one is open.
  • the control groove 35 is always with the Control line 37 connected.
  • the rear cylinder space 33 of the working cylinder is to an operational management 38 connected.
  • the control of the working piston 22 is carried out by the Control piston 41, which is movable in the control cylinder 40 is.
  • the control piston 41 is designed as a hollow sleeve. Since the control cylinder 40 with the pressure line 27th is connected, there is inside the control piston 41 always the full hydraulic pressure.
  • the control piston 41 has a first work surface A1 at one end, which is constantly under pressure and radial grooves has, so that the pressure can attack her.
  • a second work surface A2 At the opposite end of the working piston a second work surface A2 that is smaller than that Work area A1.
  • the control piston is with an annular collar 42 provided at one end by a Control surface A3 and at the opposite end an always unpressurized area A4 is limited, which with the return line 12 is connected.
  • the control surface A3 is exposed to the pressure of the control line 37.
  • the Control piston 41 is also provided with an annular groove 43, which in any position of the working piston with the Return line 12 is connected.
  • the pressure line 27 is a compressed gas storage 44, which acts as a buffer connected to smooth the hydraulic pressure surges is.
  • the operational management is in the state shown in FIG. 1 38 about the inside of the control piston 41 connected to the pressure line 27 so that on the work surface AF the full pressure works. Because the work surface AF is larger than the return stroke area RF on which The working piston also guides the full pressure 22 from its forward working stroke the end of which he strikes the anvil surface 23. As soon as the return stroke area RF passes the open control groove 34b has, the control line 37 from the pressure line 27th severed. If the control surface 29, the control groove 35 has passed, the control line 37 is via the groove 35 connected to line 36 and thereby depressurized. Thus acts on the control surface A3 of the control piston 41 no more pressure.
  • the control piston is moved back because the force exerted on the work surface A1 will exceed the force exerted by the same pressure the work surface A2 is exercised. If the control piston has reached its upper end position, the Operating line 38 separated from the delivery pressure and connected to the return line 12 via the annular groove 43. As a result, the return stroke of the working piston 22 causes. As soon as the groove 35 thickened on the return stroke Piston part 28 is shut off and the groove 34 from the return stroke area RF is released, arises in the Control line 37 the full pressure on the control surface A3 acts and the spool in the lower end position drives. The sum of the control areas A2 and A3 is larger than the control area A1.
  • This back room 50 is closed on all sides and with a compressed gas storage 52 connected.
  • the compressed gas storage 52 contains a gas filling in a gas space 53.
  • the gas space 53 is limited by a flexible membrane 54 which is gas impermeable and which closes the rear space 50.
  • An inflow line leads laterally into the rear space 50 55 leads in and on the opposite side an outflow line 56 out of the rear space.
  • the Outlet line 56 contains a throttle point 57 and it is connected to the return line 12.
  • the inflow pipe 55 contains a pressure control valve 58, which with the Flow line 10 is connected.
  • the pressure control valve 58 generates a pressure of 20 in the inflow line 55 bar.
  • the working pressure supplied to the feed line 10 is 180 bar.
  • the pressure of the pressure control valve 58 is dimensioned so that an increase in pressure during the return stroke of the working piston to this value (45 bar). This applies to the maximum working stroke, i.e. if the Control grooves 34a and 34b closed and the control groove 34c is open.
  • FIG. 2 The embodiment of FIG. 2 is largely the same 1, so that the following description limited to the differences.
  • FIG. 3 differs of that of Fig. 2 in that the inflow line blocked by the approach 51 of the working piston and is released, as is the case in FIG. 1 is.
  • the outflow line 56b in FIG. 3 not controlled by the working piston. It is constant connected to the rear space 50, as shown in FIG. 2 the case is.
  • the control piston 41 is reversed into that Position corresponding to the working stroke of the working piston 22 corresponds to the pressure in the outflow line 56a and 56b.
  • This pressure changes depending on from the return stroke position, that of the working piston 22 each takes and depending on the pressure that generated by the pressure control valve 58 in the rear space 50 has been while the piston is in the extreme feed position was.
  • This pressure the the pressure control valve 58 is generated in the rear space 50 is called a form.
  • the path length of the working piston at Return stroke can be set at which the pressure in the Outflow line 56a (Fig. 2) or 56b (Fig. 3) as large is that it can switch the control piston 41.
  • the size of the piston stroke of the working piston By Changing the admission pressure from the pressure control valve 58 is generated, the size of the piston stroke of the working piston to be changed. If the form is small, the working piston goes through a long return stroke, until the pressure in the discharge line 56a or 56b so has grown large that the control piston 41 switched becomes. Because of the large stroke length of the working piston there is a lower number of strokes per minute and an increase in the impact energy. Is on the pressure control valve 58 the form in the back 50 on one large value is set, the reversal of the Control piston even with a small stroke length of the Working piston. In this case, the working piston does Blows with high impact frequency and low impact energy.
  • a change in stroke rate and energy can in the embodiments of FIGS. 2 and 3 also take place in that the delivery pressure, the Pressure line 10 is fed, is varied while the pre-pressure generated by the pressure control valve 58 is kept constant becomes.
  • the control piston 41 forms one Pressure compensator, on the one hand the full high pressure of the Pressure line 10 (on the end faces A1 and A2) exposed and on the other hand the pressure in the discharge line 56a (Fig. 2) or 56b (Fig. 3), which on the Control surface A3 acts. If the delivery pressure is reduced, the stroke frequency of the working piston is increased and the impact energy is reduced. If the delivery pressure is increased, the stroke rate is reduced and the Impact energy increased.
  • a change in stroke rate can be dependent of how far the object is carried out is already driven into the ground.
  • Driving an object into the ground is first worked at a high frequency. Is the Soil is already advanced, a higher feed rate will be achieved reached when the stroke rate decreases and the energy of the single blows is increased.
  • the Beat frequency can also be dependent automatically of the feed force acting on the hammer to be changed.
  • the rear space 50 during the return stroke of the working piston locked that the working piston the lines 55 and 56 cordoned off.
  • the closing of the rear space 50 takes place on the one hand through the check valve 60 and on the other hand in that the one connected to the discharge line 56a Annular groove 35 is closed by the piston part 28, while the control line 37 one to the control cylinder 40 leading dead end forms.
  • the rear space is closed 50 in that the line 55 from the working piston is closed and that with the discharge line 56b connected annular groove 35 closed by the piston part 28 becomes, while the control line 37 a dead end forms.
  • the Return stroke area RF be larger than in the case that on no gas cushion at the rear end of the working cylinder is available.
  • the larger return stroke area RF is necessary because more force has to be applied to the gas in the Compressed gas storage 52 to compress.
  • the enlarged Return stroke area RF has the consequence that the oil volume in the front cylinder chamber 26 becomes larger.
  • the return stroke surface RF is constantly Exposed to high pressure, it remains under pressure standing oil volume, which displaces from the cylinder chamber 26 was received under pressure. This volume of oil need not be supplemented by the external hydraulic pressure source become.

Claims (12)

  1. Marteau à percussion hydraulique équipé d'un carter de marteau (20) raccordé à une conduite sous pression (10) et une conduite de retour (12), lequel contient un cylindre de travail (21), dans lequel un piston de travail (22) peut se déplacer, et un espace de retour (50), dans lequel se déplace l'extrémité arrière du piston de marteau,
    et équipé d'un système de commande (40, 41) pour permettre l'introduction de fluide sous pression dans le cylindre de travail (21) de telle sorte que le piston de travail (22) exécute alternativement des courses de travail dirigées vers l'avant et des courses de retour,
    le piston de travail (22) tapant lors de la course de travail contre une surface d'enclume (23),
    et un accumulateur de gaz sous pression (52) étant raccordé à l'espace de retour (50) et l'espace de retour (50) étant relié à une source de pression par une conduite d'arrivée (55) contenant une soupape (58) commandée par pression,
       caractérisé en ce que la soupape (58) commandée par pression fournit une pression constante qui est inférieure à la pression dans la conduite sous pression (10), et en ce que les conduites reliées à l'espace de retour (50) sont commandées de telle manière que l'espace de retour (50) reste fermé après le début de la course de retour du piston de travail (22).
  2. Marteau à percussion selon la revendication 1, caractérisé en ce que l'espace de retour est raccordé à une conduite d'évacuation (56 ; 56a, 56b), qui est reliée à la conduite de retour (12) pour permettre la traversée de l'espace de retour (50) dans les cas où le piston de travail (22) se trouve à proximité de sa position de fin de course avant.
  3. Marteau à percussion selon la revendication 2, caractérisé en ce que la conduite d'arrivée (55) et la conduite d'évacuation (56a, 56b) ne sont ouvertes que lorsque le piston de travail (22) se trouve à proximité de sa position de fin de course avant.
  4. Marteau à percussion selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la conduite d'arrivée (55) et/ou la conduite d'évacuation (56) débouche(nt) dans l'espace de retour (50) dans la zone que l'extrémité arrière du piston de travail balaie, de telle sorte que la conduite d'arrivée (55) et/ou la conduite d'évacuation (56) puisse(nt) être obturée(s) par le piston de travail.
  5. Marteau à percussion selon l'une quelconque des revendications 2 à 4, caractérisé en ce que la conduite d'évacuation (56) contient une section d'étranglement (57) ou une soupape.
  6. Marteau à percussion selon l'une quelconque des revendications 2 à 5, caractérisé en ce que la conduite d'évacuation (56a, 56b) est raccordée à une conduite de commande (37) qui est hors pression dans la position de fin de course avant du piston de travail (22) et est séparée de la conduite de retour (12) par le piston de travail lors de la course de retour.
  7. Marteau à percussion selon la revendication 6, caractérisé en ce que la conduite de commande (37) contrôle le système de commande (40, 41).
  8. Marteau à percussion selon l'une quelconque des revendications 1 à 7, caractérisé en ce que le piston de travail (22) présente une surface de course de retour (RF) exposée constamment à la pression élevée.
  9. Marteau à percussion selon l'une quelconque des revendications 1 à 8, caractérisé en ce qu'une soupape antiretour (60) ouvrant vers l'espace de retour (50) est incluse dans la conduite d'arrivée (55).
  10. Marteau à percussion selon l'une quelconque des revendications 1 à 9, caractérisé en ce que l'inversion de marche du système de commande (40, 41) intervient dans les cas où, à la fin de la course de retour, un équilibre de forces s'est établi sur le piston de travail (12) entre la pression agissant sur la surface de course de retour (RF) et la pression agissant sur la surface frontale (SF).
  11. Marteau à percussion selon l'une quelconque des revendications 1 à 10, caractérisé en ce que la pression de la soupape (58) commandée par pression est réglable pour modifier la longueur de la course de retour du piston de travail (22).
  12. Marteau à percussion selon l'une quelconque des revendications 1 à 11, caractérisé en ce que le niveau de la pression fournie amenée à la conduite sous pression (10) est réglable pour modifier la longueur de la course de retour du piston de travail (22).
EP94117814A 1994-02-19 1994-11-11 Marteau à percussion hydraulique Expired - Lifetime EP0672506B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4405381 1994-02-19
DE4405381 1994-02-19

Publications (2)

Publication Number Publication Date
EP0672506A1 EP0672506A1 (fr) 1995-09-20
EP0672506B1 true EP0672506B1 (fr) 2001-07-11

Family

ID=6510691

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94117814A Expired - Lifetime EP0672506B1 (fr) 1994-02-19 1994-11-11 Marteau à percussion hydraulique

Country Status (6)

Country Link
US (1) US5718297A (fr)
EP (1) EP0672506B1 (fr)
JP (1) JPH08509431A (fr)
AT (1) ATE202963T1 (fr)
DE (1) DE59409798D1 (fr)
WO (1) WO1995022442A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19652079C2 (de) * 1996-12-14 1999-02-25 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk
DE10003415B4 (de) * 2000-01-27 2005-06-16 Carl Freudenberg Kg Hydraulikhammer mit einem Druckgasspeicher
US20040045727A1 (en) * 2002-09-11 2004-03-11 Allums Jeromy T. Safe starting fluid hammer
SE528081C2 (sv) * 2004-08-25 2006-08-29 Atlas Copco Constr Tools Ab Hydraulisk slagmekanism
SE528745C2 (sv) * 2005-06-22 2007-02-06 Atlas Copco Rock Drills Ab Ventilanordning för slagverk och slagverk för bergborrmaskin
FR3037345B1 (fr) * 2015-06-11 2017-06-23 Montabert Roger Appareil hydraulique a percussions
US11084155B2 (en) * 2016-08-31 2021-08-10 Furukawa Rock Drill Co., Ltd. Hydraulic striking device
KR102425266B1 (ko) * 2017-01-12 2022-07-25 후루까와 로크 드릴 가부시끼가이샤 액압식 타격장치

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1281370B (de) * 1963-09-06 1968-10-24 Krupp Gmbh Schlaggeraet mit hydraulisch hin- und herbewegten Kolben
FI72908C (fi) * 1979-06-29 1987-08-10 Rammer Oy Hydraulisk slagmaskin.
US4474248A (en) * 1981-04-23 1984-10-02 Giovanni Donadio Hydraulic demolishing rock drill
US4466493A (en) * 1981-12-17 1984-08-21 Hed Corporation Reciprocating linear fluid motor
SE462117B (sv) * 1984-05-24 1990-05-07 Atlas Copco Mct Ab Hydraulisk ackumulator vid ett hydrauliskt slagverk
RU1778289C (ru) * 1988-05-04 1992-11-30 Карагандинский политехнический институт Гидравлическа бурильна машина
JPH03208215A (ja) * 1990-01-10 1991-09-11 Izumi Seiki Seisakusho:Kk 油圧式ブレーカー
FR2676953B1 (fr) * 1991-05-30 1993-08-20 Montabert Ets Appareil hydraulique a percussions.
JP3378029B2 (ja) * 1991-08-08 2003-02-17 丸善工業株式会社 油圧ブレーカ

Also Published As

Publication number Publication date
EP0672506A1 (fr) 1995-09-20
WO1995022442A1 (fr) 1995-08-24
ATE202963T1 (de) 2001-07-15
JPH08509431A (ja) 1996-10-08
US5718297A (en) 1998-02-17
DE59409798D1 (de) 2001-08-16

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