EP0847836B1 - Appareil à percussion mû par un fluide sous pression - Google Patents

Appareil à percussion mû par un fluide sous pression Download PDF

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Publication number
EP0847836B1
EP0847836B1 EP97121702A EP97121702A EP0847836B1 EP 0847836 B1 EP0847836 B1 EP 0847836B1 EP 97121702 A EP97121702 A EP 97121702A EP 97121702 A EP97121702 A EP 97121702A EP 0847836 B1 EP0847836 B1 EP 0847836B1
Authority
EP
European Patent Office
Prior art keywords
control slide
control
pressure
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
EP97121702A
Other languages
German (de)
English (en)
Other versions
EP0847836A1 (fr
Inventor
Heinz-Jürgen Dr.-Ing. Prokop
Marcus Dr.-Ing. Geimer
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.)
Construction Tools GmbH
Original Assignee
Krupp Berco Bautechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Krupp Berco Bautechnik GmbH filed Critical Krupp Berco Bautechnik GmbH
Publication of EP0847836A1 publication Critical patent/EP0847836A1/fr
Application granted granted Critical
Publication of EP0847836B1 publication Critical patent/EP0847836B1/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
    • B25D9/06—Means for driving the impulse member
    • B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
    • 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 fluid-powered hammer mechanism with a in a working cylinder movable percussion piston striking a tool as well a control with a control slide movable with respect to a housing, wherein the percussion piston has two piston surfaces of different sizes, from which the smaller piston area effective in the direction of the return stroke is always present a pressure line under working pressure and the larger one, towards the Effective piston strokes alternate with the control via the control Pressure line and a drain line is connected.
  • control spool points in mutually opposite direction effective slide surfaces that such are trained and pressurized that the spool with the approach of the percussion piston during the return stroke to the top dead center in the Toggle working stroke position, in which also on the larger piston area Working pressure is applied, and with the approach of the percussion piston during the Working strokes are transferred to the point of impact in the return stroke position, in which the application of pressure to the larger piston area is interrupted and a connection to the drain line is established.
  • a fluid-powered percussion mechanism of the type mentioned at the outset is in the publication DE-C2-34 43 542 described above.
  • the Control spool two differently sized, in opposite directions of movement effective slide surfaces, the smaller, in the direction of the return stroke position of the control spool constantly acting on this spool surface the pressure line and its larger slide area as a control surface by means of a Control line via a circumferential groove arranged between the piston surfaces only temporarily and alternately with the pressure line or one pressurized return line is connected.
  • the document DE-C2-30 23 600 describes a hydraulic percussion rotary drilling device with a bush-like control slide which is hydraulically controlled via the percussion piston and is movably supported both on this and within the working cylinder.
  • the disadvantage of the known rotary impact drilling device is that it requires a double fit in the area of the control slide, ie the control slide must have very little play in the outer and inner diameter area in order to ensure proper functioning.
  • the invention has for its object a different in terms of control to develop trained, fluid-powered percussion.
  • the Control can also be designed in such a way that it without constant exposure with high pressure (i.e. with the one necessary for the operation of the striking mechanism Working pressure) and without mechanical force, in particular also through the percussion piston, is functional.
  • the control slide has a control surface which is effective in the direction of the working stroke position and which - depending on the position of the percussion piston - is temporarily connected to a pressure-free return line or to the pressure line via a circumferential groove arranged between the piston surfaces.
  • the control spool is equipped with a total effective area (formed from the difference between the control spool end faces), which - when the control surface is relieved of pressure - is under a variable pressure during the return stroke, which is proportional to the pressure on the larger piston area - the control spool in the return stroke position toggles.
  • the control slide forms a socket-like switching element, via the cavity of which the rear cylinder chamber section containing the larger piston area is connected either in the return stroke position to the discharge line or in the working stroke position to the pressure line, in the return stroke position the fluid against an outflow resistance from the rear cylinder chamber section (into the drain pipe already mentioned) emerges.
  • the outflow resistance serves to generate and maintain a sufficient pressure level in the rear cylinder chamber section during the return stroke, which pressure acts on the total effective area and results in an adjustment force effective in the direction of the return stroke position.
  • a mechanical reset can also be provided be (claim 2); in the simplest case, this consists of a spring unit.
  • control surface of the control slide - seen in cross section - on a radially projecting outward Heel formed, the counter surface without pressure via a relief line is held (claim 3).
  • control slide has two different sizes End faces, the larger of which faces the control surface (claim 4).
  • control slide must be arranged and designed such that in the return stroke position it releases a connection between the rear cylinder chamber section and the drain line, for example by means of a recess or a recess.
  • control slide can be designed such that the connection to the drain line is established via a transverse bore formed in the control slide (claim 5).
  • the outflow resistance can either be in the transverse bore be arranged itself or in the drain line (claim 6).
  • the transverse bore is preferably arranged in the vicinity of the larger end face (Claim 7).
  • control slide can be designed in such a way that the according to Art an annular groove formed the mouth of the pressure line in the return stroke position of the spool by means of the spool section - the completion of which forms smaller end face - closed in the direction of the rear cylinder section is (claim 8).
  • control can in principle be arranged separately from the working cylinder.
  • control slide is arranged in the rear cylinder section coaxially to the longitudinal axis of the working cylinder (claim 9).
  • the outflow resistance can in particular be designed as an orifice 10), which works essentially independent of viscosity.
  • the subject of the invention differs from the known state of the art in that the control slide is only temporarily acted upon by the working pressure via its control surface, the working pressure then also being present in the cavity of the control slide taking up the working stroke position.
  • the fluid surrounding the control slide represents a drive means, under the influence of which the control slide moves into the return stroke position and is held in this position as long as its control surface is not subjected to the working pressure.
  • the striking mechanism has, in addition to the lines and drive and control elements still to be described, a working cylinder 2, in which a percussion piston 3 is held to move back and forth in the longitudinal direction.
  • This has two piston collars 3a and 3b lying in the cylinder space of the working cylinder, which are separated from one another by a circumferential groove 3c.
  • the outwardly directed piston surface A1 and A2 of the piston collar 3b and 3a defines with the working cylinder 2 a rear and front cylinder space section 2a and 2b, the piston surface A1 being dimensioned smaller than the piston surface A2.
  • the percussion piston 3 merges into a piston tip 3d, which is opposite a tool in the form of a chisel 4.
  • the movement of the percussion piston 3 in the direction of the working stroke is indicated by an arrow 3e. 1 shows the striking mechanism 1 in a state immediately after the impact piston 3 strikes the chisel 4; the percussion piston therefore assumes the intended impact position.
  • the smaller piston area A1 is over a return line 5 constantly pressurized with the working pressure (system pressure); this is generated by an energy source in the form of a hydraulic pump 6 and via a pressure line 7 extending from this (among other things) into the return line 5 fed.
  • the mouth 5a of the return line 5 is in relation to the Working cylinder 2 arranged so that it is outside the piston collar in any case 3b and thus lies within the front cylinder space section 2b.
  • the control, generally designated 8, for switching the movement of the percussion piston 3 into the working cylinder 2 is integrated, ie it is located in the region of the rear cylinder chamber section 2a inside the working cylinder 2nd
  • the control has a control slide 9 which is movable with respect to a housing, the housing (as already mentioned) in the present case consisting of part of the working cylinder 2.
  • the control slide 9 is designed like a bush and is arranged in such a way that lying coaxially to the percussion piston 3 surrounds it at a distance in the region of the rear cylinder chamber section 2a. Accordingly, the internal cavity of the control slide simultaneously forms part of the rear cylinder chamber section 2a.
  • the control slide 9 itself has two differently sized end faces - namely a smaller, front end face S1 and a rear, larger end face S2.
  • the two end faces S1 and S2 mentioned limit the axial freedom of movement of the control slide 9 in the direction of the working stroke (arrow 3e) or in the direction of the return stroke. Accordingly, the control slide can assume two end positions - namely the return stroke position indicated at the top left in FIG. 1, in which the control slide is supported by the smaller end face S1 on a front stop surface 2c of the working cylinder, and the working stroke position indicated at the top right in FIG. 1 which abuts the larger end surface S2 on a rear stop surface 2d.
  • the control slide 9 has a transverse bore 11 in the vicinity of its larger end face S2, via which a connection between the rear cylinder chamber section 2a and a drain line 12 can be made, if necessary - ie depending on the position of the control slide 9; the latter is equipped with an outflow resistance in the form of an orifice 13 and merges in the direction of the control slide 9 into an opening 12a which is also in the form of an annular groove.
  • the drain line 12 is connected to a tank 15 via a return line 14 which is kept pressureless.
  • the control slide 9 is - seen in the axial direction - in the area between the both end faces S1 and S2 continue with one in the direction of the working stroke position of the spool effective control surface SF equipped, which - in cross section seen - is formed as a radially projecting shoulder and one Opposite face GF; the latter is connected to the return line 14 connected pressure relief line 16.
  • the control surface SF of the control slide can be acted upon or relieved of the working pressure via a control line 17 - which is connected to the interior of the working cylinder 2 in the area between the openings 10a and 5a; the working cylinder 2 is also connected to the tank 15 via a return line 18 which merges into the return line 14.
  • the orifices 17a and 18a of the lines 17 and 18 are arranged such that they are connected to one another in the impact position of the percussion piston 3 (indicated in FIG. 1) via the circumferential groove 3c between the piston collars 3a and 3b; this mutual assignment has the result that the control surface SF is relieved of pressure at this time via the control line 17, the annular groove 3c and the return line 18.
  • connection between the lines 17 and 18 is first interrupted by the piston collar 3b before it finally clears the mouth 17a again and thereby - via the front cylinder space section 2b - creates a connection between the lines 17 and 5.
  • This connection has the consequence that the control surface SF is now acted upon by the working pressure generated by the hydraulic pump 6.
  • the striking mechanism 1 works as follows: As soon as a connection between lines 5 and 17 is established via the front cylinder space section 2b during the return stroke of the percussion piston 3 (counter to the working stroke movement according to arrow 3e), the control slide 9 moves under the action of the control surface SF which is subjected to the working pressure into the one shown in FIG. 2a shown working stroke position, whereby on the one hand the connection between the transverse bore 11 and the drain line 12 is interrupted and on the other hand a connection between the supply line 10 and the rear cylinder chamber section 2a is established via the released junction 10a. Accordingly, the working pressure is now also present on the larger piston surface A2, so that the percussion piston - against the restoring force emanating from the smaller piston surface A1 - begins to perform a working stroke in the direction of arrow 3e.
  • the striking mechanism 1 can also have a control 8, which - as shown in FIG. 3 - is arranged separately from the working cylinder 2.
  • the control slide 9 is held axially movable in its own control housing 19, its cavity 9a being connected to the rear via a connecting line 20 - in the vicinity of the rear stop surface 2d (cf. FIGS. 1 and 2a, b) Cylinder chamber section 2a communicates.
  • control 8 can also be designed such that the outflow resistance is integrated in the control slide 9. This can be achieved in a simple manner in that the diaphragm 13 - as also shown in FIG. 3 - is installed in the transverse bore 11. In this embodiment, the drain line 12 accordingly has no specially designed, additional outflow resistance.
  • FIGS. 1 and 2a, b in the frame also be designed according to the invention, i.e. have a controller 8, in which the outflow resistance is not part of the drain line 12, but is integrated in the control slide 9.
  • control 8 can also be additionally equipped with a mechanical reset, preferably in the form of a spring unit, which supports the reversal of the control slide 9 in the direction of the return stroke position.
  • the spring unit can in particular be arranged and designed such that it engages the larger end surface S2 and / or the counter surface GF.
  • the control slide 9 is supported via its larger end surface S2 on a prestressed spring unit 21, which in turn is arranged in a projecting recess 2e of the rear stop surface 2d. Under the action of this mechanical reset, the control slide 9 tends to assume the return stroke position shown.
  • the advantage achieved by the invention is that with simple means and without mechanical entrainment by the percussion piston, the necessary reversal between work and return stroke can be realized, the control if necessary, can also be integrated into the existing cylinder can.
  • the newly proposed striking mechanism also does not require a double fit in the sense of the prior art mentioned above, since the control slide is supported only on its outer surface to the environment.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Earth Drilling (AREA)
  • Operation Control Of Excavators (AREA)

Claims (10)

  1. L'appareil à percussion (1) mû par un fluide avec un piston frappeur (3) déplaçable dans un cylindre de travail (2) et frappant sur un outil (4), et avec une commande (8) avec un tiroir (9) mobile par rapport à un boitier (2) respectivement (19), où le piston frappeur (2) présente deux faces de piston de grandeur différente (A1, A2) dont la face de piston plus petite (A1) active en direction de la course de retour est reliée continuellement à un conduit sous pression (7) se trouvant en pression de travail et la face de piston plus grande (A2) active en direction de la course de travail (3e) est reliée par la commande (8) alternativement au conduit sous pression (7) et à un conduit d'écoulement (12),
       où le tiroir (9) présente des faces de tiroir (S1 ; S2 ; SF) actives dans des directions opposées l'une à l'autre qui sont réalisées et chargées en pression de façon que le tiroir, lors de l'approche du piston frappeur (3) pendant la course de retour au point mort haut commute en position de course de travail dans laquelle la pression de travail s'applique également à la face de piston plus grande (A2) et, à l'approche du piston frappeur pendant la course de travail au point de frappe, est commuté en position de course de retour dans laquelle la sollicitation de la face de piston plus grande (A2) en pression de travail est interrompue et une liaison est réalisée avec le conduit d'écoulement (12),
       caractérisé par les caractéristiques suivantes :
    le tiroir (9) présente une face de commande (SF) active en direction de la position de la course de travail qui, dépendamment de la position du piston frappeur (3), est en liaison temporairement par une rainure périphérique (3c) ménagée entre les faces de piston (A1, A2) avec un conduit de retour sans pression (18) respectivement avec le conduit sous pression (7) ;
    de plus, le tiroir (9) est équipé d'une face active totale (différence des faces frontales S2 et S1) qui, lors d'une face de commande détendue (SF) pendant la course de retour sous une pression variable qui est proportionnelle à la pression sur la face de piston plus grande (A2), commute le tiroir de commande en position de course de retour ;
    le tiroir (9) forme un élément de commutation en forme de manchon par l'espace creux duquel (2a) respectivement (9a), le tronçon arrière (2a) de l'enceinte cylindrique contenant la face de piston plus grande (A2) est raccordé soit en position de course de retour au conduit d'écoulement (12) soit en position de course de travail au conduit sous pression (7), où en position de course de retour, le fluide sort contre une résistance à l'écoulement (13) du tronçon arrière (2a) de l'enceinte cylindrique.
  2. Dispositif selon la revendication 1, caractérisé en ce que le tiroir (9) présente de plus un rappel mécanique (21) actif en direction de la position de course de retour.
  3. Dispositif selon au moins l'une des revendications précédentes, caractérisé en ce que la face de commande (SF), vue en section transversale, est réalisée à un gradin faisant radialement saillie vers l'extérieur dont la contre-face (GF) est maintenue sans pression par un conduit de détente (16).
  4. Dispositif selon au moins l'une des revendications précédentes, caractérisé en ce que le tiroir (9) présente deux faces frontales (S1, S2) de grandeur différente dont la face frontale plus grande (S2) est opposée à la face de commande (SF).
  5. Dispositif selon au moins l'une des revendications précédentes, caractérisé en ce que la liaison au conduit d'écoulement (12) est réalisée par un perçage transversal (11) ménagé dans le tiroir (9).
  6. Dispositif selon la revendication 5, caractérisé en ce que soit le perçage transversal (11) soit le conduit d'écoulement (12) est équipé d'une résistance à l'écoulement (13).
  7. Dispositif selon au moins l'une des revendications 5 et 6, caractérisé en ce que le perçage transversal (11) est ménagé au voisinage de la face frontale plus grande (S2).
  8. Dispositif selon au moins l'une des revendications 5 à 7, caractérisé en ce que l'embouchure du conduit sous pression (conduit d'alimentation 10) réalisée à la manière d'une rainure annulaire, en position de course de retour du tiroir (9), est fermée au moyen du tronçon du tiroir, dont la terminaison forme la face frontale plus petite (S1), en direction du tronçon arrière (2a) de l'enceinte cylindrique.
  9. Dispositif selon au moins l'une des revendications précédentes, caractérisé en ce que le tiroir (9) est disposé dans le tronçon arrière (2a) de l'enceinte cylindrique coaxialement à l'axe longitudinal du cylindre de travail (3).
  10. Dispositif selon au moins l'une des revendications précédentes, caractérisé en ce que la résistance à l'écoulement est réalisée comme obturateur (13) .
EP97121702A 1996-12-14 1997-12-10 Appareil à percussion mû par un fluide sous pression Expired - Lifetime EP0847836B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19652079A DE19652079C2 (de) 1996-12-14 1996-12-14 Fluidbetriebenes Schlagwerk
DE19652079 1996-12-14

Publications (2)

Publication Number Publication Date
EP0847836A1 EP0847836A1 (fr) 1998-06-17
EP0847836B1 true EP0847836B1 (fr) 2001-02-28

Family

ID=7814724

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97121702A Expired - Lifetime EP0847836B1 (fr) 1996-12-14 1997-12-10 Appareil à percussion mû par un fluide sous pression

Country Status (5)

Country Link
US (1) US5960893A (fr)
EP (1) EP0847836B1 (fr)
JP (1) JP3908362B2 (fr)
DE (1) DE19652079C2 (fr)
ES (1) ES2154443T3 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6491114B1 (en) 2000-10-03 2002-12-10 Npk Construction Equipment, Inc. Slow start control for a hydraulic hammer
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
US20060003869A1 (en) * 2004-07-02 2006-01-05 Johnson Tech. Co., Ltd. Folding treadmill
US20060180314A1 (en) * 2005-02-17 2006-08-17 Control Flow Inc. Co-linear tensioner and methods of installing and removing same
ITBA20050012A1 (it) * 2005-03-16 2006-09-17 Eutecna S R L Soc Macchina oleodinamica a percussione con un cassetto di distribuzione di tipo on-off e pistone pilota
SE529615C2 (sv) * 2006-02-20 2007-10-09 Atlas Copco Rock Drills Ab Slagverk och bergborrmaskin samt förfarande för att styra slagkolvens slaglängd
KR102317232B1 (ko) 2020-01-08 2021-10-22 주식회사 현대에버다임 유압 브레이커

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DE551138C (de) * 1928-10-25 1932-05-27 Chicago Pneumatik Tool Company Steuerung fuer Druckluftschlagwerkzeuge
FI50390C (fi) * 1973-09-14 1976-03-10 Murskauskone Oy Hydraulisesti käytetty iskulaite
FI751895A (fr) * 1975-06-26 1976-12-27 Xandor Ag
FI58675C (fi) * 1979-06-26 1981-03-10 Tampella Oy Ab Hydraulisk borranordning
GB2100364B (en) * 1981-04-23 1985-01-09 Musso Mario A hydraulic percussive drill
DE3400302A1 (de) * 1984-01-03 1985-08-29 Mannesmann AG, 4000 Düsseldorf Hydraulisch betaetigte schlagvorrichtung
DE3443542A1 (de) * 1984-11-29 1986-06-05 Fried. Krupp Gmbh, 4300 Essen Hydraulische schlagvorrichtung
AU578147B2 (en) * 1985-03-26 1988-10-13 Steel Engineering Company Limited; The Hydraulic percusive machine
SE461711B (sv) * 1989-01-16 1990-03-19 Atlas Copco Tools Ab Utloppsorgan foer ett tryckluftdrivet maskinverktyg
FR2647870B1 (fr) * 1989-06-06 1991-09-06 Eimco Secoma Appareil de percussion hydraulique avec dispositif d'amortissement des ondes de choc en retour
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
DE4131070C2 (de) * 1991-09-18 1993-11-18 Ingenieurkontor Fuer Maschinen Hydraulisch getriebener Schlagbohrhammer
JP2677751B2 (ja) * 1993-03-11 1997-11-17 株式会社テイサク 打撃装置
DE4343589C1 (de) * 1993-12-21 1995-04-27 Klemm Guenter Fluidbetätigter Schlaghammer
DE59409798D1 (de) * 1994-02-19 2001-08-16 Klemm Guenter Hydraulischer Schlaghammer

Also Published As

Publication number Publication date
JPH10184262A (ja) 1998-07-14
US5960893A (en) 1999-10-05
JP3908362B2 (ja) 2007-04-25
DE19652079A1 (de) 1998-06-18
EP0847836A1 (fr) 1998-06-17
ES2154443T3 (es) 2001-04-01
DE19652079C2 (de) 1999-02-25

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