EP0183093A1 - Dispositif hydraulique de percussion - Google Patents

Dispositif hydraulique de percussion Download PDF

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Publication number
EP0183093A1
EP0183093A1 EP85114037A EP85114037A EP0183093A1 EP 0183093 A1 EP0183093 A1 EP 0183093A1 EP 85114037 A EP85114037 A EP 85114037A EP 85114037 A EP85114037 A EP 85114037A EP 0183093 A1 EP0183093 A1 EP 0183093A1
Authority
EP
European Patent Office
Prior art keywords
control
line
valve
connection
return line
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
EP85114037A
Other languages
German (de)
English (en)
Other versions
EP0183093B1 (fr
Inventor
Friedrich-Karl Dr.-Ing. Arndt
Karlheinz Fritz
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.)
Fried Krupp AG
Original Assignee
Fried Krupp AG
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 Fried Krupp AG filed Critical Fried Krupp AG
Priority to AT85114037T priority Critical patent/ATE40067T1/de
Publication of EP0183093A1 publication Critical patent/EP0183093A1/fr
Application granted granted Critical
Publication of EP0183093B1 publication Critical patent/EP0183093B1/fr
Expired 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 device according to the preamble of claim 1.
  • Such devices are e.g. known from DE-AS 24 28 236.
  • the percussion piston triggers a control pulse shortly before reaching its two end positions, which initiates the reversal of the control valve, which in turn causes the forces acting on the percussion piston to be reversed.
  • the control pulses dependent on the piston stroke of the percussion piston are selected such that the percussion piston comes to rest at the intended upper reversal point, taking into account the switching time of the control valve, and then begins its working stroke and, on the other hand, experiences the forces causing the return stroke after the piston hits the chisel.
  • the invention has for its object to design a striking device in such a way that in the event that the impact energy is reflected back from the chisel tip to the striking piston, the number of strokes is not reduced and the smoothness is not impaired.
  • the device according to the invention thus enables the reflection energy to be recovered.
  • the striking device 1 has a working cylinder 2 in which a striking piston 3 is movably guided. At its lower end, the striking device 1 is provided with a chisel 4, which is slidable in a known manner by a certain amount. The end of the working cylinder 2 facing the chisel 4 is connected via a flow or pressure line 5 to a pressure source with the working pressure Po . An annular groove 6 is provided for the mouth of the supply or pressure line 5 in the working cylinder 2. The impact device 1 is also equipped with a pressure accumulator 8 which is connected to the pressure line 5.
  • the impact device 1 also contains a control valve 10 with a control cylinder 11 and a sleeve-like control slide 12 movable therein.
  • the control cylinder 11 has three cylindrical parts 11a, 11b, 11c, the middle part 11b having the largest diameter and the lower part 11c the smallest diameter and the upper part 11a has a diameter which lies between the other two diameters.
  • the front end of the lower cylindrical part 11c of the control cylinder 11 is connected to the pressure line 5 via a branch line 13.
  • the upper end of the control cylinder 11 is connected via a groove 15 and a line 16 to the return line 17 (hereinafter also referred to as “return line” for short), which leads to the connection on the low-pressure side (symbol: PT ).
  • the lower part 11c of the control cylinder 11 is also connected via a lateral line 18 to the upper part of the working cylinder 2, a groove 19 being provided in the control cylinder 11 for the opening of the line 18 and a groove 20 in the working cylinder 2. In the vicinity of the groove 19, the control cylinder 11 is connected directly to the return line 17 via a groove 22.
  • a further groove 23 is provided between the grooves 6 and 20 in the working cylinder 2 and is connected to the return line 17 via two lines 24, 25.
  • the working cylinder 2 has a control groove 26 through which the working cylinder 2 is connected to the control cylinder 11 via a control channel or a control line 27.
  • the control line 27 is formed by the two lines or line sections 27a and 27b. In the control cylinder, the control line 27 opens into a groove 29 which is located between the grooves 15 and 22.
  • the four grooves 15, 29, 22 and 19 of the control cylinder 11 define its three cylindrical parts as follows: the upper cylindrical part 11a lies above the groove 15, the central cylindrical part 11b is delimited by the two grooves 15 and 29, and the lower cylindrical part 11c extends from the lower edge of the groove 29 to below the groove 19.
  • the groove 22 lies within the lower cylindrical part 11c.
  • the two line sections 27a and 27b are connected to one another by a holding valve 30 provided with three connections, the third connection being connected to the return line 17 via a line section 31 and the line 25.
  • the percussion piston 3 each has a tapered front or lower and rear or upper section 32 or 33, the diameter of the front section 32 being larger than that of the rear section 33.
  • the tapered sections 32 and 33 each create one small or large annular surface 34 or 35 formed on the percussion piston 3.
  • a recess or circumferential groove 36 is arranged between the two ring surfaces 34, 35, through which two piston collars 37 and 38 are formed.
  • the small annular surface 34 is constantly acted upon by the oil or hydraulic medium through the pressure line 5 when it is ready for operation.
  • the piston collar 37 forms one with its end adjoining the circumferential groove 36 upper control edge 39 and with the end given by the small annular surface 34 a lower control edge 40.
  • the control slide 12 has at its lower end facing the branch line 13 a first tapered cylindrical section 41 with an end face 42 and at its opposite end a further cylindrical section 43 with an end face 44.
  • the diameter of the first section 41 is smaller than that of the second section 43, so that the first end face 42 is also smaller than the second end face 44.
  • Both end faces 42 and 44 are constantly pressurized in the event of readiness for operation, so that there is always one over these faces downward force F acts on the control spool 12, which results from the area difference (A44 - A42) multiplied by the working pressure p D.
  • the space between the groove 15 of the control cylinder 11 and the second cylindrical section 43 of the control slide 12 is constantly connected to the return line 17.
  • the first section 41 of the control slide 12 is guided in the lower and the second section 43 in the upper cylindrical part 11c and 11a of the control cylinder 11.
  • the piston collar 45 slides in the central cylindrical part 11b of the control cylinder 11.
  • the first cylindrical section 41 has a circumferential groove 49 and - between this and the control surface 47 - a small radial auxiliary bore 51.
  • the length of the order catch groove 49 is greater than the distance between the two grooves 19 and 22 in the control cylinder 11.
  • the holding valve 30 is shown in FIG. 2 on an enlarged scale. It consists of a hollow cylindrical part or a bore 53 and a valve body 54 designed as a ball.
  • the cylindrical part 53 has a valve seat 55 on its end face connected to the return line 17 via the line section 31 and a valve seat 55 on its other end face connected to the line section 27a a valve seat 56.
  • the line section 27b of the control line 27 opens radially into the hollow cylindrical part 53. Its central axis goes - when the ball 54 abuts the valve seat 55 - through the half of the ball 54 facing this valve seat.
  • the diameter of the ball 54 is smaller than the diameter of the cylindrical part 53, so that the pressure or hydraulic medium through the the ball 54 and the cylindrical part 53 formed gap 58 can flow.
  • FIG. 1 shows the striking device during the working stroke of the striking piston 3 indicated by an arrow.
  • the space of the cylinder 2 above the large annular surface 35 is connected to the pressure line 5 via the line 18 and the branch line 13.
  • the percussion piston 3 is thus accelerated in the direction of the chisel 4, which is multiplied by the area difference ( A 35 - A34) of the ring surfaces 35 and 34 gives the working pressure p 0 .
  • the control slide 12 is in the upper position facing away from the high-pressure line 5 or the branch line 13.
  • the upper control edge 39 reaches the control groove 26.
  • the circumferential groove 36 connects the line section 27a - and thus the entire control line 27 - via the line 24 to the return line 17, which creates the space under the control surface 47 becomes depressurized. It is therefore only the force acting on the control spool 12 over the partial surface or surface difference (A 44 - A 42 ) and pushes it into its lower end position in the valve or control time t st specified by the design.
  • the pressure difference occurring at the gap 58 drives the ball 54 to the right on the valve seat 56.
  • the hydraulic medium flowing through the line section 27b can briefly flow both via the line section 31 and via the line section 27a and the line 24 flow to line 25 and thus to return line 17. If the ball 54 abuts the valve seat 56 and the line section 27a and the line 24 are thus blocked for the hydraulic medium flowing out of the line section 27b, the hydraulic medium displaced by the control surface 47 and fed in via the auxiliary bore 51 can continue to prevent a small pressure drop in the line section Drain off to line 25 and thus to return line 17.
  • the auxiliary bore 51 is covered on the one hand by the part of the control cylinder 11 located between the grooves 29 and 22 and on the other hand by the circumferential groove 49 the annular surface 35 of the piston 3 via the grooves 22 and 19 and the Line 18 connected to the return line 17 (see FIG. 3).
  • the upper, large annular surface 35 is thus relieved and the percussion piston 3 is accelerated upward by the force acting on the lower small annular surface 34 for the return stroke.
  • the lower control edge 40 given by the small annular surface 34 reaches the control groove 26 and thus (again) establishes a connection between the pressure line 5 and the line section 27a of the control line 27: the ball 54 is pressed against the left valve seat 55 ( see Fig. 4), and the entire control line 27 and the space under the control surface 47 is pressurized so that the control slide 12 is moved back to its upper position, in which it leads the line 18 to the cylinder 2 again via the connecting line 13 connects to the pressure line 5 and a new working stroke is initiated.
  • the piston 3 is suddenly accelerated by the reflection pulse in the direction of the return stroke in such a way that the time between the release or the opening of the control groove 26 during the downward stroke of the piston 3 and the reclosing of the control groove 26 by the upper control edge 39 is too short to bring the control slide 12 into its lower position.
  • control slide 12 Any small movement of the control slide 12 which may have been initiated is reversed - with the control groove 26 closed - by feeding pressure medium through the auxiliary bore 51 into the space under the control surface 47.
  • valve time t st which also corresponds to the time that passes in order to separate the annular surface 35 from the pressure line 5 and to connect it to the return line 17, is chosen in such a way that the reflection energy can be fully used by displacing the pressure oil in front of the annular surface 35 through the lines 18 and 13 in the pressure accumulator 8.
  • the pressure oil flowing into the pressure accumulator 8 is available for the next stroke and has the effect of increasing the delivery quantity Q 0 . Since the number of strokes Z of the impact piston 3 is proportional to the delivery quantity Q 0 , the utilization of or recovery of the reflection energy also increases the number of strokes Z and thus the overall performance of the impact device 1.
  • control slide 12 can also be acted upon by a compression spring in the direction of its lower position, as is described, for example, in EP-A1-0 070 246.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP85114037A 1984-11-29 1985-11-05 Dispositif hydraulique de percussion Expired EP0183093B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85114037T ATE40067T1 (de) 1984-11-29 1985-11-05 Hydraulische schlagvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3443542 1984-11-29
DE19843443542 DE3443542A1 (de) 1984-11-29 1984-11-29 Hydraulische schlagvorrichtung

Publications (2)

Publication Number Publication Date
EP0183093A1 true EP0183093A1 (fr) 1986-06-04
EP0183093B1 EP0183093B1 (fr) 1989-01-18

Family

ID=6251484

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85114037A Expired EP0183093B1 (fr) 1984-11-29 1985-11-05 Dispositif hydraulique de percussion

Country Status (5)

Country Link
US (1) US4646854A (fr)
EP (1) EP0183093B1 (fr)
JP (1) JPH0671714B2 (fr)
AT (1) ATE40067T1 (fr)
DE (1) DE3443542A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU567427B2 (en) * 1986-03-11 1987-11-19 Nittetsu Jitsugyo Co., Ltd. Hydraulic breaker
EP0486898A1 (fr) * 1990-11-20 1992-05-27 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Procédé et dispositif pour ajustage des caractéristiques de travail d'un mécanisme à coup à la dureté des materiaux à broyer
EP0847836A1 (fr) * 1996-12-14 1998-06-17 Krupp Bautechnik GmbH Appareil à percussion mû par un fluide sous pression
EP0933169A2 (fr) * 1998-02-03 1999-08-04 Krupp Berco Bautechnik GmbH Dispositif de percussion actionné par un fluide

Families Citing this family (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR900003145B1 (ko) * 1986-08-12 1990-05-09 이교일 유 · 공압 브레이커
JPH0513509Y2 (fr) * 1986-09-09 1993-04-09
US4828048A (en) * 1986-11-10 1989-05-09 Mayer James R Hydraulic Percussion tool
JPS63256378A (ja) * 1986-12-04 1988-10-24 日本ニユ−マチツク工業株式会社 油圧衝撃動工具
FR2618092B1 (fr) * 1987-07-17 1989-11-10 Montabert Ets Distributeur hydraulique pour appareil a percussions mu par un fluide incompressible sous pression
DE3913866A1 (de) * 1989-04-27 1990-10-31 Krupp Maschinentechnik Hydraulisches schlagwerk
US4930584A (en) * 1989-05-04 1990-06-05 Easy Industries Co., Ltd. Cracking device
EP0447552A4 (en) * 1989-07-11 1991-12-18 Petr Yakovlevich Fadeev Striking device
US5022309A (en) * 1989-08-17 1991-06-11 Ingersoll-Rand Company Variable frequency control for percussion actuator
DE3939785A1 (de) * 1989-12-01 1991-06-06 Krupp Maschinentechnik Automatische schmiereinrichtung fuer den meissel eines hydraulischen schlagwerks
JPH03208215A (ja) * 1990-01-10 1991-09-11 Izumi Seiki Seisakusho:Kk 油圧式ブレーカー
US5064005A (en) * 1990-04-30 1991-11-12 Caterpillar Inc. Impact hammer and control arrangement therefor
ES2084033T3 (es) * 1990-07-12 1996-05-01 G Drill Ab Taladro hidraulico para perforar rocas hasta agujerearlas.
US5775196A (en) * 1994-02-28 1998-07-07 Atlas Copco Berema Ab Valve arrangement in compressed air driven motors
US5680904A (en) * 1995-11-30 1997-10-28 Patterson; William N. In-the-hole percussion rock drill
DE19545708A1 (de) 1995-12-07 1997-06-12 Krupp Bautechnik Gmbh Verfahren zur Beeinflussung des Betriebsverhaltens eines fluidbetriebenen Schlagwerks und zur Durchführung des Verfahrens geeignetes Schlagwerk
US6152013A (en) * 1996-07-25 2000-11-28 Komatsu Ltd. Hydraulically actuated breaker with lost-motion prevention device
DE19636659C2 (de) * 1996-09-10 2000-11-23 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk mit automatischer Hubumschaltung
US6058632A (en) * 1997-11-07 2000-05-09 Hawkins; Peter Arthur Taylor Tool holder with percussion member
FI107891B (fi) * 1998-03-30 2001-10-31 Sandvik Tamrock Oy Painenestekäyttöinen iskulaite
CA2295463C (fr) 1999-01-27 2008-04-29 William N. Patterson Marteau perforateur hydraulique de roche fond de trou
US6155361A (en) * 1999-01-27 2000-12-05 Patterson; William N. Hydraulic in-the-hole percussion rock drill
US6464023B2 (en) 1999-01-27 2002-10-15 William N. Patterson Hydraulic in-the-hole percussion rock drill
DE19923680B4 (de) * 1999-05-22 2004-02-26 Atlas Copco Construction Tools Gmbh Verfahren zur Ermittlung der Betriebsdauer und des Einsatz-Zustands eines hydraulischen Schlagaggregats, insbesondere Hydraulikhammer, sowie Vorrichtung zur Durchführung des Verfahrens
US6631787B2 (en) 1999-12-27 2003-10-14 Lincoln Industrial Corporation Lubrication system
KR100400385B1 (ko) * 2001-07-11 2003-10-08 주식회사 코막 유압 브레이커의 유압 컨트롤밸브
FI114290B (fi) * 2003-02-21 2004-09-30 Sandvik Tamrock Oy Ohjausventtiili ja järjestely iskulaitteessa
SE528033C2 (sv) * 2004-03-12 2006-08-15 Atlas Copco Constr Tools Ab Hydraulslagverk
DE102004035306A1 (de) * 2004-07-21 2006-03-16 Atlas Copco Construction Tools Gmbh Druckmittelbetriebene Schlagvorrichtung insbesondere Hydraulikhammer
SE528745C2 (sv) * 2005-06-22 2007-02-06 Atlas Copco Rock Drills Ab Ventilanordning för slagverk och slagverk för bergborrmaskin
DE102006026274A1 (de) 2006-06-02 2007-12-06 Willy Vogel Ag Selbsttätige Schmierpumpe mit doppelt wirkendem Antriebskolben
US7681664B2 (en) * 2008-03-06 2010-03-23 Patterson William N Internally dampened percussion rock drill
SE537608C2 (sv) * 2013-11-01 2015-07-28 Tools Pc Ab Const Pneumatisk slaganordning och förfarande vid pneumatisk slaganordning
EP3100829B1 (fr) * 2014-01-30 2022-08-24 Furukawa Rock Drill Co., Ltd. Dispositif de martelage hydraulique
ES2927066T3 (es) * 2016-08-31 2022-11-02 Furukawa Rock Drill Co Ltd Dispositivo percutor hidráulico
US20180133882A1 (en) * 2016-11-16 2018-05-17 Caterpillar Inc. Hydraulic hammer and sleeve therefor
PT3417951T (pt) * 2017-06-19 2022-07-08 Eurodrill Gmbh Dispositivo e método para a produção de impulsos de impacto ou vibrações para uma máquina de construção
KR102317232B1 (ko) * 2020-01-08 2021-10-22 주식회사 현대에버다임 유압 브레이커

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR404176A (fr) * 1908-10-12 1909-11-24 Ernst Flottmann Machine ou frappeur à air comprimé
US1832432A (en) * 1928-10-01 1931-11-17 Chicago Pneumatic Tool Co Pneumatic hammer
US2302018A (en) * 1940-12-30 1942-11-17 Independent Pneumatic Tool Co Distributing valve for pneumatic hammering tools

Family Cites Families (8)

* 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
US4172411A (en) * 1976-06-09 1979-10-30 Mitsui Engineering & Shipbuilding Co., Ltd. Hydraulic hammer
DE2658455C3 (de) * 1976-12-23 1981-01-22 Fried. Krupp Gmbh, 4300 Essen Druckmittelbetriebenes Schlagwerk
SE420057B (sv) * 1980-02-20 1981-09-14 Atlas Copco Ab Hydrauliskt slagverk med mojlighet att reglera slagenergin
US4425835A (en) * 1981-01-26 1984-01-17 Ingersoll-Rand Company Fluid actuator
FR2509217A1 (fr) * 1981-07-10 1983-01-14 Montabert Ets Appareil a percussions mu par un fluide sous pression
SU1084435A1 (ru) * 1982-06-25 1984-04-07 Калининский Экскаваторный Завод Устройство ударного действи
SU1102935A1 (ru) * 1982-12-23 1984-07-15 Карагандинский Ордена Трудового Красного Знамени Политехнический Институт Гидропневматическое ударное устройство

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR404176A (fr) * 1908-10-12 1909-11-24 Ernst Flottmann Machine ou frappeur à air comprimé
US1832432A (en) * 1928-10-01 1931-11-17 Chicago Pneumatic Tool Co Pneumatic hammer
US2302018A (en) * 1940-12-30 1942-11-17 Independent Pneumatic Tool Co Distributing valve for pneumatic hammering tools

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU567427B2 (en) * 1986-03-11 1987-11-19 Nittetsu Jitsugyo Co., Ltd. Hydraulic breaker
EP0486898A1 (fr) * 1990-11-20 1992-05-27 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Procédé et dispositif pour ajustage des caractéristiques de travail d'un mécanisme à coup à la dureté des materiaux à broyer
EP0847836A1 (fr) * 1996-12-14 1998-06-17 Krupp Bautechnik GmbH Appareil à percussion mû par un fluide sous pression
EP0933169A2 (fr) * 1998-02-03 1999-08-04 Krupp Berco Bautechnik GmbH Dispositif de percussion actionné par un fluide
EP0933169A3 (fr) * 1998-02-03 2000-11-15 Krupp Berco Bautechnik GmbH Dispositif de percussion actionné par un fluide

Also Published As

Publication number Publication date
DE3443542C2 (fr) 1990-07-26
US4646854A (en) 1987-03-03
ATE40067T1 (de) 1989-02-15
DE3443542A1 (de) 1986-06-05
JPH0671714B2 (ja) 1994-09-14
EP0183093B1 (fr) 1989-01-18
JPS61131877A (ja) 1986-06-19

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