EP1058600B1 - Druckflüssigkeitsbetriebenes werkzeug - Google Patents

Druckflüssigkeitsbetriebenes werkzeug Download PDF

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Publication number
EP1058600B1
EP1058600B1 EP99902647A EP99902647A EP1058600B1 EP 1058600 B1 EP1058600 B1 EP 1058600B1 EP 99902647 A EP99902647 A EP 99902647A EP 99902647 A EP99902647 A EP 99902647A EP 1058600 B1 EP1058600 B1 EP 1058600B1
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EP
European Patent Office
Prior art keywords
cylinder
fluid
piston
tool
valve
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.)
Revoked
Application number
EP99902647A
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English (en)
French (fr)
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EP1058600A1 (de
Inventor
George Naismith
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.)
Caldervale Engineering Services Ltd
Original Assignee
Caldervale Engineering Services Ltd
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
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Application filed by Caldervale Engineering Services Ltd filed Critical Caldervale Engineering Services Ltd
Publication of EP1058600A1 publication Critical patent/EP1058600A1/de
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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
    • B25D9/16—Valve arrangements therefor
    • B25D9/20—Valve arrangements therefor involving a tubular-type slide valve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D2209/002—Pressure accumulators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D2209/005—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously having a tubular-slide valve, which is coaxial with the piston

Definitions

  • This invention relates to a fluid actuated tool, and in particular but not exclusively to a hydraulic percussive tool, such as a hammer.
  • the invention also relates to a method of controlling the operation of a fluid actuated tool.
  • Hydraulic percussive tools such as hammers
  • hammers are used in many applications, primarily in breaking up hard surfaces or structures.
  • Larger hammers may be mounted on the arm of an excavator or on the backhoe of a tractor.
  • a hammer comprises a body containing a reciprocating piston which strikes an anvil or tool piece, hereinafter referred to as the chisel.
  • the flow of pressurised hydraulic fluid to the hammer is controlled by valves contained within a valve body mounted externally of the hammer body, facilitating access to the valves for maintenance and repair.
  • the valve body is vulnerable to damage and increases the mass and volume occupied by the hammer.
  • a number of sleeve valves have been proposed which, in use, are concentrically aligned with the piston, inside the tool body.
  • a sleeve valve is disclosed in FR 2328547 wherein a valve is axially movable inside the body of a percussive tool by a fluid pressure differential between opposite ends of the valve.
  • the sleeve valve controls the direction of movement of a piston assembly by opening and closing fluid ports in the tool body.
  • a similar valve is disclosed in US 1,516,566, which valve also ensures that the piston has performed its full stroke before the valve redirects the working fluid to return the piston. This particular valve minimises the recoil forces experienced by the percussive tool.
  • Such valves offer no control over the speed of the piston, particularly at the end of the stroke when large impulse forces are imparted at the tool.
  • a fluid actuated tool comprising:
  • the invention also relates to a method of controlling the actuation of a fluid actuated tool utilising a sleeve valve.
  • the tool may be a hydraulic hammer, in which the piston impacts on a chisel bit.
  • the fluid outlet defines flow restrictions for controlling the flow of fluid from the cylinder, to control the rate of movement of the piston in the cylinder on the exhaust or return stroke.
  • the flow restrictions are orifices, and may be adjustable to vary the rate of fluid flow therethrough.
  • valve sleeve defines fluid ports and fluid ports are also provided in the cylinder wall for communication with one or both of the fluid inlet and fluid outlet; when the ports are in alignment fluid may flow through the ports into or from the cylinder.
  • fluid communicating bores extend through the body for providing fluid communication between the cylinder ports and the fluid inlet and fluid outlet. Most preferably, the bores also provide fluid communication between axially spaced cylinder ports.
  • the piston starts to move on its power stroke prior to the valve moving on its power stroke, and the piston and valve move together on the exhaust stroke.
  • the valve and piston are locatable in initial power positions in which a sleeve inlet port is aligned with a cylinder inlet port so that high pressure fluid may flow from a fluid source into the cylinder, to act on the piston.
  • the valve and piston are moveable from the initial power positions to exhaust positions in which the cylinder inlet port is closed and a cylinder exhaust port is open.
  • the valve closes the cylinder inlet port and exposes a cylinder exhaust port so that fluid may exhaust from the cylinder as the piston returns to the initial position.
  • the valve may be moveable from the initial power position by application of fluid pressure to a portion of the sleeve.
  • the sleeve defines an annular piston face positioned in an annular portion of the cylinder and application of fluid pressure to the face causes the sleeve to move in the cylinder.
  • the sleeve and piston occupy a fluid transfer position in which a sleeve transfer port is aligned with a cylinder transfer port, the aligned transfer ports permitting high pressure fluid communication with the annular portion of the cylinder where the fluid acts on the annular piston face defined by the sleeve, to induce movement of the sleeve relative to the cylinder and piston.
  • the piston initially moves on its power stroke relative to the valve and subsequently uncovers the transfer ports to allow high pressure fluid communication with the annular portion of the cylinder to induce movement of the valve.
  • the valve is movable from its initial position to close the cylinder inlet port and limit or prevent further flow of high pressure fluid into the cylinder.
  • the piston defines a return piston face, preferably annular in form, which is positioned in a high pressure chamber and normally exposed to high pressure fluid, tending to return the piston and valve to the initial position.
  • a return piston face preferably annular in form
  • the piston moves downwards in the cylinder beyond a predetermined relative position an opposite face moves into the chamber and is also exposed to said high pressure fluid, such that the piston remains stationary in the cylinder.
  • the piston may be "reset” simply by applying a load to the piston to move the opposite face from the chamber.
  • a fluid actuated tool comprising:
  • the invention also relates to a method of controlling the actuation of a fluid actuated tool utilising an exhaust orifice.
  • FIG. 1 of the drawings illustrates a fluid actuated tool in the form of a hydraulic hammer 20 in accordance with a preferred embodiment of the present invention.
  • the hammer 20 comprises a body 22, a cylinder 26 and a chuck body 28.
  • Mounted on the cylinder 26 is a transfer plate 30 and an accumulator 32.
  • Mounted within the cylinder 26 is a piston 34 which, while the hammer 20 is in use, moves in a reciprocal manner within the cylinder 26 and impacts on a chisel 36 mounted in the chuck body 28.
  • the movement of the piston 34 within the cylinder 26 is achieved by the controlled supply of high pressure hydraulic fluid from a suitable high pressure source (not shown), typically a hydraulic pump on a tractor or tracked vehicle which supports the hammer 20.
  • a suitable high pressure source typically a hydraulic pump on a tractor or tracked vehicle which supports the hammer 20.
  • the flow of hydraulic fluid into and from the cylinder 26 is controlled by the interaction of an apertured distributor valve sleeve 38 ( Figure 2) located in the upper part of the cylinder 26 wich a number of cylinder ports 40 communicating with a series of axial fluid carrying bores 42, as may be seen more clearly in Figures 3 and 4 of the drawings.
  • the interaction between the valve 38 and the cylinder 26 will now be described in detail, with reference to Figures 5 through 12 of the drawings, which illustrate the relative positions of the piston 34 and the distributor valve 38 during a power stroke and a return exhaust stroke of the piston 34.
  • FIG. 5 of the drawings illustrates the starting point in the operating cycle when the piston 34 and the distributor valve 38 are both at the top of their strokes.
  • High pressure hydraulic fluid is being supplied from an appropriate source through a fluid inlet 44, the high pressure fluid charging the accumulator 32 and also pressurising six of the axial fluid bores 46, all of which communicate with the accumulator 32, and five of which extend axially through the cylinder 36 below the fluid inlet 44.
  • the bores 46 are intersected by slots 48, 50, 52 and at various points along the length of the cylinder and which slots extend to intersect the cylinder and define fluid inlet ports.
  • the first set of slots 48 are directly adjacent the fluid inlet 44.
  • the slots 48 are aligned with slots 54 in the distributor valve 38.
  • the intermediate set of slots 50 communicate with an annular groove 56 within the cylinder allowing fluid communication with the cylinder via holes 58 in the lower part of the distributor valve 38.
  • the holes 58 allow high pressure fluid to fill part of an annular chamber 60 formed between the piston head 62 and an annular piston face 64 formed on the piston 34, the upper end of the chamber 60 being closed by a solid section 66 of the distributor valve, and the lower end of the chamber 60 being sealed by a solid section 68 of the distributor valve which includes an inner collar 70 in contact with the piston 34.
  • the lower set of slots 52 provide communication with a return chamber 72 defined by the cylinder wall below a further annular piston 74.
  • the piston 34 is accelerated very rapidly downward due to the combined flow from the pump and the accumulator 32.
  • the distributor 38 is held at the top of its stroke due to the differential pressure created by the areas of the distributor 38 exposed to the high pressure fluid.
  • the distributor 38 As the distributor 38 continues to move downwards as illustrated in Figure 9 of the drawings, it first closes off the flow from the high pressure fluid inlet 44 as the distributor slots 54 are moved out of alignment with the cylinder slots 48. Continued downward movement of the distributor 38, as illustrated in Figure 10, then opens a fluid outlet 92 as the upper end of the distributor 38 uncovers three cylinder slots 94 which intersect three of the axial bores 95 which act as low pressure exhausts. A further set of slots 98 intersect the lower end of the bores 96, opening into an annular groove 100 in the cylinder wall, which provides communication with the lower part of the chamber 60. A further lower set of slots 101 is, at this stage, located opposite the piston 64.
  • Uncovering the slots 94 causes the collapse of the high pressure regime in the upper part of the main cylinder chamber 78.
  • the distributor 38 and the piston 34 continue on their downward travel, the piston 34 due to its momentum and the distributor 38 due to the high pressure which continues to act on the upper surface of the collar 70.
  • the piston distributor return is effected by the continual high pressure feed to the return chamber 72 acting on the annular piston 74, as illustrated in Figure 11 of the drawings. This supplies the returning force, in addition to any rebound after the impact with the chisel 36.
  • a similar high pressure feed is maintained to the annular chamber 60, as illustrated in Figure 12 of the drawings, and the high pressure fluid acts as a fluid spring which serves to reseat the distributor 38 on top of the piston head 62 before the piston 34 has reached the top of its stroke, thus preparing the hammer for the next firing stroke.
  • the main low pressure drain provided by the slots 94, is closed.
  • the fluid remaining in the chamber between the piston 34 and the distributor 38 is then only able to discharge via orifices 102 in the transfer plate 30 and into the transfer bores 84 and then into the low pressure bores 96 via the slots 88, 101 and the annular piston groove 104 between the annular pistons 64, 74. This ensures that a low pressure regime exists in the transfer bores, ensuring correct seating of the distributor 38 prior to the next firing point.
  • the orifices 102 in the transfer plate 30 effectively control the return speed of the piston 34 and the distributor 38 and also provide damping at the end of the stroke.
  • the axial extent of the piston 74 is such that the upper face of the piston 74 will move into the return chamber 72 if the chisel 36 is not in contact with, for example, a hard surface which is being broken up.
  • the piston 74 moves into the chamber 72, the axial pressure forces acting on the piston 74 are balanced, such that there is no upward axial pressure force acting on the piston 34, and the piston 34 therefore remains stationary.
  • a distributor valve 38 in the form of a sleeve, mounted within the cylinder and around the piston, provides a simple and effective means of controlling the flow of hydraulic fluid into the cylinder, and thus controlling actuation of the piston 34.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Nozzles (AREA)
  • Catching Or Destruction (AREA)

Claims (19)

  1. Fluidbetätigtes Werkzeug, das aufweist:
    einen Körper (22), der einen Zylinder (26) definiert;
    einen Kolben (34), der im Zylinder (26) hin- und hergehend beweglich ist;
    einen Fluideintritt (44) für das Bereitstellen einer Fluidverbindung zwischen einer Fluidquelle und dem Zylinder (26);
    einen Fluidaustritt (92) für das Bereitstellen einer Verbindung zwischen dem Zylinder (26) und einem Fluidauslaß; und
    ein Buchsenventil (38) um mindestens einen Abschnitt des Kolbens (34) im Zylinder (26) herum, wobei das Buchsenventil (38) axial beweglich ist, um den Strom des Fluids zwischen dem Fluideintritt (44) und dem Zylinder (26) und zwischen dem Fluidaustritt (92) und dem Zylinder (26) zu steuern,
       wobei der Fluidaustritt (92) und das Buchsenventil (38) zusammenwirken, um die Geschwindigkeit der Bewegung des Kolbens (34) im Zylinder (26) beim Auslaßhub oder Kolbenrückgang zu steuern.
  2. Werkzeug nach Anspruch 1, bei dem das Werkzeug ein hydraulischer Hammer ist, bei dem der Kolben (34) auf einen Flachmeißel (36) auftrifft.
  3. Werkzeug nach Anspruch 1 oder 2, bei dem der Fluidaustritt (92) Durchflußdrosselungen für das Steuern des Stromes des Fluids vom Zylinder (26) definiert.
  4. Werkzeug nach Anspruch 3, bei dem die Durchflußdrosselungen Austrittsöffnungen (102) sind.
  5. Werkzeug nach Anspruch 3 oder 4, bei dem die Durchflußdrosselungen regulierbar sind, um die Geschwindigkeit des Fluidstromes dort hindurch zu variieren.
  6. Werkzeug nach vorhergehenden Ansprüchen, bei dem das Buchsenventil (38) Fluidöffnungen (58, 80) definiert, und Fluidöffnungen (40) sind ebenfalls in der Zylinderwand für eine Verbindung mit einem oder beiden von Fluideintritt (44) und Fluidaustritt (92) vorhanden.
  7. Werkzeug nach Anspruch 6, bei dem sich Fluidverbindungsbohrungen (46, 84, 96) durch den Körper (22) erstrecken, um eine Fluidverbindung zwischen den Zylinderöffnungen (40) und dem Fluideintritt (44) und Fluidaustritt (92) bereitzustellen.
  8. Werkzeug nach Anspruch 7, bei dem die Bohrungen (46, 84, 96) ebenfalls eine Fluidverbindung zwischen axial beabstandeten Zylinderöffnungen bereitstellen.
  9. Werkzeug nach vorhergehenden Ansprüchen, bei dem sich der Kolben (34) bei seinem Arbeitshub zu bewegen beginnt, bevor sich das Ventil (38) bei seinem Arbeitshub bewegt, und der Kolben (34) und das Ventil (38) sich zusammen beim Auslaßhub bewegen.
  10. Werkzeug nach vorhergehenden Ansprüchen, bei dem das Ventil (38) und der Kolben (34) in Ausgangsarbeitspositionen angeordnet werden können, bei denen eine Buchseneintrittsöffnung (54) mit einer Eintrittsöffnung (44) des Zylinders ausgerichtet ist, so daß ein Hochdruckfluid von einer Fluidquelle in den Zylinder (26) strömen kann, um auf den Kolben zu wirken.
  11. Werkzeug nach Anspruch 10, bei dem das Ventil (38) und der Kolben (34) aus den Ausgangsarbeitspositionen in Auslaßpositionen beweglich sind, bei denen die Eintrittsöffnung (44) des Zylinders geschlossen und eine Auslaßöffnung (92) des Zylinders offen ist.
  12. Werkzeug nach Anspruch 11, bei dem in der Auslaßposition das Ventil (38) die Eintrittsöffnung (44) des Zylinders verschließt und eine Auslaßöffnung (92) des Zylinders freigibt, so daß das Fluid aus dem Zylinder (26) austreten kann, während der Kolben (34) in die Ausgangsposition zurückkehrt.
  13. Werkzeug nach einem der Ansprüche 10 bis 12, bei dem das Ventil (38) aus der Ausgangsarbeitsposition durch Anwendung des Fluiddruckes auf einen Abschnitt der Buchse (38) beweglich ist.
  14. Werkzeug nach Anspruch 13, bei dem die Buchse (38) eine ringförmige Kolbenfläche definiert, die in einem ringförmigen Abschnitt des Zylinders (26) positioniert ist, und bei der die Anwendung des Fluiddruckes auf die Fläche bewirkt, daß sich die Buchse (38) im Zylinder (26) bewegt.
  15. Werkzeug nach Anspruch 14, bei dem zwischen der Ausgangsarbeitsposition und der Auslaßposition die Buchse (38) und der Kolben (34) eine Fluidtransportposition einnehmen, in der eine Buchsentransportöffnung (80) mit einer Zylindertransportöffnung (82) ausgerichtet ist, wobei die ausgerichteten Transportöffnungen eine Hochdruckfluidverbindung mit dem ringförmigen Abschnitt des Zylinders (26) gestatten, wobei das Fluid auf die ringförmige Kolbenfläche wirkt, die durch die Buchse (38) definiert wird, um eine Bewegung der Buchse relativ zum Zylinder (26) und Kolben (34) hervorzurufen.
  16. Werkzeug nach Anspruch 15, bei dem sich der Kolben (34) anfangs aus der Ausgangsarbeitsposition bei seinem Arbeitshub relativ zum Ventil (38) bewegt und folglich die Transportöffnungen (80) freilegt, um eine Hochdruckfluidverbindung mit dem ringförmigen Abschnitt des Zylinders (26) zu gestatten, um die Bewegung des Ventils (38) hervorzurufen.
  17. Werkzeug nach Anspruch 16, bei dem das Ventil (38) aus seiner Ausgangsposition beweglich ist, um die Eintrittsöffnung (44) des Zylinders zu verschließen, und um einen weiteren Strom des Hochdruckfluids in den Zylinder (26) zu begrenzen oder zu verhindern.
  18. Werkzeug nach Anspruch 17, bei dem der Kolben (34) eine Fläche des Rücklaufkolbens (74) definiert, die in einer Hochdruckkammer (72) positioniert ist und normalerweise dem Hochdruckfluid ausgesetzt ist, was dazu neigt, daß der Kolben (34) und das Ventil (38) in die Ausgangsposition zurückkehren, und bei dem sich, wenn sich der Kolben (34) im Zylinder (26) nach unten über eine vorgegebene relative Position hinaus bewegt, eine gegenüberliegende Fläche in die Kammer (72) bewegt und ebenfalls dem Hochdruckfluid ausgesetzt wird, so daß der Kolben (34) im Zylinder (26) stationär bleibt.
  19. Fluidbetätigtes Werkzeug, das aufweist:
    einen Körper (22), der einen Zylinder (26) definiert;
    einen Kolben (34), der im Zylinder (26) bei den Arbeits- und Auslaßhüben hinund hergehend beweglich ist;
    einen Fluideintritt (44) für das Bereitstellen einer Fluidverbindung zwischen einer Fluidquelle und dem Zylinder (26);
    einen Fluidaustritt (92) für das Bereitstellen einer Verbindung zwischen dem Zylinder (26) und einem Fluidauslaß; und
    ein Ventil (38), um den Strom des Fluids zwischen dem Fluideintritt (44) und dem Zylinder (26) und zwischen dem Fluidaustritt (92) und dem Zylinder (26) zu steuern,
       wobei der Fluidaustritt (92) und das Ventil (38) zusammenwirken, um die Geschwindigkeit der Bewegung des Kolbens (34) im Zylinder (26) beim Auslaßhub zu steuern.
EP99902647A 1998-01-31 1999-01-29 Druckflüssigkeitsbetriebenes werkzeug Revoked EP1058600B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB9802034 1998-01-31
GBGB9802034.0A GB9802034D0 (en) 1998-01-31 1998-01-31 Fluid actuated tool
PCT/GB1999/000133 WO1999038655A1 (en) 1998-01-31 1999-01-29 Fluid actuated tool

Publications (2)

Publication Number Publication Date
EP1058600A1 EP1058600A1 (de) 2000-12-13
EP1058600B1 true EP1058600B1 (de) 2002-08-14

Family

ID=10826186

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99902647A Revoked EP1058600B1 (de) 1998-01-31 1999-01-29 Druckflüssigkeitsbetriebenes werkzeug

Country Status (6)

Country Link
EP (1) EP1058600B1 (de)
AT (1) ATE222160T1 (de)
AU (1) AU2286799A (de)
DE (1) DE69902517D1 (de)
GB (1) GB9802034D0 (de)
WO (1) WO1999038655A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AUPR430201A0 (en) * 2001-04-09 2001-05-17 Russell Mineral Equipment Pty Ltd Linerbolt removing tool

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2259379A (en) * 1939-02-04 1941-10-14 Stahlwerk Mark Wengern A G Pneumatic percussion tool with slide valve control gear
FI56430C (fi) * 1975-10-20 1982-08-09 Tampella Oy Ab Slaganordning driven av en tryckvaetska
DE3400302A1 (de) * 1984-01-03 1985-08-29 Mannesmann AG, 4000 Düsseldorf Hydraulisch betaetigte schlagvorrichtung

Also Published As

Publication number Publication date
EP1058600A1 (de) 2000-12-13
DE69902517D1 (de) 2002-09-19
GB9802034D0 (en) 1998-03-25
WO1999038655A1 (en) 1999-08-05
AU2286799A (en) 1999-08-16
ATE222160T1 (de) 2002-08-15

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