EP0161227A1 - Hydraulisches Schlaggerät - Google Patents

Hydraulisches Schlaggerät Download PDF

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Publication number
EP0161227A1
EP0161227A1 EP85850135A EP85850135A EP0161227A1 EP 0161227 A1 EP0161227 A1 EP 0161227A1 EP 85850135 A EP85850135 A EP 85850135A EP 85850135 A EP85850135 A EP 85850135A EP 0161227 A1 EP0161227 A1 EP 0161227A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
distribution valve
control
piston hammer
control chamber
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.)
Withdrawn
Application number
EP85850135A
Other languages
English (en)
French (fr)
Inventor
Bror Haldo Hansson
Bertil Torbjörn Jakobsson
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.)
Atlas Copco AB
Original Assignee
Atlas Copco AB
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 Atlas Copco AB filed Critical Atlas Copco AB
Publication of EP0161227A1 publication Critical patent/EP0161227A1/de
Withdrawn legal-status Critical Current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
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof

Definitions

  • This invention relates to an hydraulic percussive machine,in particular a rock drill, comprising a piston hammer reciprocable in a cylinder for repetitively impacting upon an anvil, a distribution valve coupled to an inlet, to an outlet and to a connection conduit that leads to a cylinder chamber formed between the piston hammer and the cylinder, said distribution valve having a first position for pressurizing said connection conduit and a second position for draining same, a first control piston surface in a first control chamber arranged to switch over the distribution valve into said first position when pressurized, a second control chamber arranged to switch over the distribution valve into said second position when pressurized, a piston hammer controlled first control passage between the cylinder and said first control chamber for pressurizing the latter when the piston hammer reaches a predetermined position and a piston hammer controlled second control passage between the cylinder and said second control chamber for pressurizing the latter when the piston hammer reaches a predetermined position.
  • the stroke of the hammer piston can for example be varied between 60 and 30 wm and the impact frequency will then vary for example between 30 and 60 Hz.
  • high frequences and short strokes cannot be achieved.
  • the rock drill illustrated on the drawings comprises a housing 11 forming a stepped cylinder 12 for a piston hammer 13 that has a single land 14.
  • a front cylinder chamber 15 and a rear cylinder chamber 16 are formed between the cylinder 12 and the piston hammer 13.
  • the annular front surface 17 of the land 14 is located in the front cylinder chamber 15 and the annular rear surface 18 of the land 14 is located in the rear cylinder chamber 16.
  • the area of the surface 18 is usually greater than the area of the surface 17.
  • the piston hammer is driven by the alternating pressure in the cylinder chambers 15, 16.
  • the piston hammer 13 impacts on an anvil formed by the upper end face 19 of a drill string adapter 20 that is operatively coupled to the drive shaft 21 of a non-illustrated hydraulic motor through a chuck 22 (Fig 2).
  • the chuck 22 has a bushing 23 that is in splined connection with the chuck.
  • the adapter 20 has a widened portion 24 that is in splined connection with the chuck bushing 23.
  • the rear end faces of the splines of the widened portion 24 of the adapter takes support on a recoil damping piston 26.
  • the damping piston 26 is forced forwardly into its foremost position, in which it is shown, by the hydraulic pressure in a cylinder chamber 27 that is constantly pressurized through a passage 28.
  • the damping piston 26 yields from its illustrated position if the drill string and its adapter 20 recoils but it returns immediately to its illustrated position because of the pressure in the cylinder chamber 27.
  • the actual design of the recoil damper can advantageously be as described in EP-A-58650.
  • a distribution valve 31 with a valving spool 32 is connected to pump (not shown) and to tank (not shown) through an inlet 33 and two outlets 34 respectively, and it is connected to the front cylinder chamber 15 and the rear cylinder chamber 16 through two connection conduits 35, 36 respectively.
  • the two outlets 3 4 can be coupled to a common drain conduit that leads to the tank.
  • the valving spool 32 has two plungers 37, 38 with end faces 39, 40 in control chambers 41, 42.
  • the control chamber 41 is connected to eight discrete ports into the cylinder 12 via a control passage 43, 44 that is branched into eight branches forming the above mentioned discrete ports. Only the two axially outermost branches 45, 46 are shown. The branches between them are only indicated by their center lines (shown by chain lines).
  • the control chamber 42 is also connected to eight discrete ports into the cylinder 12 via a control passage 47, 48 that is branched into eight branches forming the ports. Only the two axially outermost branches 49, 50 are shown. Tne branches between them are only indicated by their center lines (shown by chain lines). The axial distances between the ports in the two sets of eight ports are smaller than the diameter of the ports. Therefore, the branches are arranged in three rows, but this is trivial and not illustrated in the drawings.
  • the two sets of branches 45, 46 and 49, 50 are controlled by a selector valve in the form of an axially displaceable spool 51 with two recesses 52, 53.There are non-illustrated means for holding the spool 51 fixed in pre-selected axial positions.
  • the ports of the two branches 45, 49 are selected to convey pressure signals from the cylinder chambers 15, 16 to the control chambers 41, 42.
  • the axially discplaceable selector valve 51 another pair of branches can be selected to convey the pressure signals.
  • the selector valve 51 the length of the piston hammer stroke can be pre-selected as described in EP-A-35005 and EP-A-112810.
  • control passages 43, 44 and 47, 48 there is an auxiliary valve 54 with a valving spool 55.
  • the control passages thus comprises portions 43 and 47 between the distribution valve 31 and the auxiliary valve 54, portions 44, 48 between the auxiliary valve 54 and the selector valve 51 and the two sets of branches 45, 46 and 49, 50 between the selector valve 51 and the cylinder 12.
  • the spool 55 of the auxiliary valve 54 has plungers 56, 57 with piston surfaces 58, 59 in branches 60, 61 of the connection conduits 35, 36.
  • a drain passage 62 leads from the auxiliary valve to the tank. The drain passage 62 is not connected to the main drains 34.
  • the spool 32 of the distribution valve 31 has two annular piston surfaces 62, 63, the areas of which are only a fraction of the areas of the end faces 39, 40 of the plungers 37, 38. Bores 64, 65 in the valving spool 32 lead to the annular piston surfaces 62, 63.
  • Figs 3-6 For clarity, the selector valve 51 is not shown in the figures and only the two branches 45, 49 of the two sets of branches 45, 46 and 49, 50 are shown, which are made operative by the selector valve 51 when the latter is fixed in its position shown in Fig 1. In Figs 3-6, only a selection of the reference numerals of Fig 1 is shown. Reference numerals which are net necessary for the understanding of the operation as described are left out.
  • the piston hammer 13 has just struck the adapter 20.
  • the distribution valve spool 32 is in its left hand position in which it pressurizes the front cylinder chamber 15 through the connection passage 35 and drains the rear cylinder chamber 16 through the connection passage 36.
  • the auxiliary valve spool 55 is in its right hand position because of the pressure acting on its piston surface 58. In this position, it connects the two parts 43 and 44, 45 of the control passage 43, 44 whereas it blocks the part 48, 49, 50 of the control passage 47, 48 and connects the other part 47 to drain.
  • the distribution valve spool 32 is positively held in position because of the pressure conveyed through the bore 65 and acting on its annular piston surface 63.
  • the piston hammer 13 moves rearwardly (to the right in Fig 3) after impacting on the adapter 20.
  • the hammer piston land 14 uncovers the port of the control passage 43, 44 as shown in Fig 4, the pressure from the pressurized cylinder chamber 15 is conveyed to the control chamber 41 of the distribution valve 31 so that the distribution valve spool 32 switches over into its position shown in Fig 5.
  • the distribution valve spool 32 is shown in the middle of its movement. In its position shown in Fig 5, the distribution valve 31 pressurizes the connection conduit 36.
  • auxiliary valve spool 55 Since there will be pressure on the piston surface 59 of the auxiliary valve spool 55 as soon as the distribution valve spool 32 has switched over to its position of Fig 5, the auxiliary valve spool 55 will also switch over to its position of Fig 5 and drain the control chamber 41. There will, however, be pressure on the holding surface 62 because of the bore 64 and the distribution valve spool 32 will therefore be positively held in position.
  • the piston hammer 13 Because of the pressure in the cylinder chamber 16, the piston hammer 13 will decelerate to stop and then accelerate forwardly in its working stroke. Just prior to impacting on the adapter 20, the piston hammer 13 will uncover the port of the control passage 47, 48 as shown in Fig 6 and the pressure in the cylinder chamber 16 will be conveyed to the control chamber 42 so that the distribution valve spool 32 will switch over to its position of Fig 3. In Fig 6, the distribution valve spool 32 is shown in its transient middle position during its movement to the left in the figure. The pressure will reach the cylinder chamber 15 just when the piston hammer 13 strucks the adapter 20. The auxiliary valve spool 55 switches again over to its position of Fig 3 when the connection conduit 35 is pressurized. The piston hammer 13 starts another return stroke and the cycle is repeated.
  • the distribution valve spool 32 shifts position and pressurizes one of the connection conduits 35, 36. Then, the rapid auxiliary valve spool 55 shifts position so that it drains the control chamber 41, 42 that was last D ressurized and effected the distribution valve 32 to shift position.
  • the draining of one of the control chambers 41, 42 takes place well in advance of the pressurization of the other control chamber, which permits for a high impact frequency and a selection of short piston hammer strokes.
  • the stroke is a direct function of which of the passages 45-46, 49-50 are opened by the selector valve 51. When the stroke is short the impact frequency is high and vice versa.
  • the stroke can for example be varied between 7 mm and 60 mm by means of the selector valve 51 when the piston hammer is 40-60 cm long and weighs for example 70 kg and the impact frequency can accordingly vary between 150 Hz and 50 Hz. Since the branches 45-46 and 49-50 are not used to drain the control chambers but are temporarily blocked by the auxiliary valve spool 55, any pressure peaks occuring in the cylinder chambers 15, 16 when the latter are connected to the tank via the outlets 34 can not reach the control chambers 41, 42. Therefore these pressure peaks can not influence the distribution valve spool 32. Thus, the operation of the distribution valve 31 will be very reliable and the holding surfaces 62, 63 can be made comparatively small.
  • the two cylinder chambers 15, 16 are alternatingly pressurized and drained through the distribution valve 31.
  • one of the cylinder chambers 15, 16 can be constantly pressurized whereas the distribution valve 31 alternatingly pressurizes and drains the other cylinder chamber in order to effect reciprocation of the piston hammer 13.
  • the valve 54 can be arranged to drain both control chambers 41, 41 but it would also be possible to have the valve 54 drain only the control chamber that opens into the alternatingly pressurized cylinder chamber prcvided that the valve switching area of this control chamber is greater than the corresponding area of the control chamber that opens into the constantly pressurized cylinder chamber.
  • other modifications can be made within the scope of the claims.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Earth Drilling (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
EP85850135A 1984-04-24 1985-04-22 Hydraulisches Schlaggerät Withdrawn EP0161227A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8402232A SE442100B (sv) 1984-04-24 1984-04-24 Hydrauliskt slagverk for bergborrmaskin som medger stort regleromrade for slaglengd och frekvens
SE8402232 1984-04-24

Publications (1)

Publication Number Publication Date
EP0161227A1 true EP0161227A1 (de) 1985-11-13

Family

ID=20355651

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85850135A Withdrawn EP0161227A1 (de) 1984-04-24 1985-04-22 Hydraulisches Schlaggerät

Country Status (2)

Country Link
EP (1) EP0161227A1 (de)
SE (1) SE442100B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2618092A1 (fr) * 1987-07-17 1989-01-20 Montabert Ets Distributeur hydraulique pour appareil a percussions mu par un fluide incompressible sous pression
WO2008103095A1 (en) 2007-02-23 2008-08-28 Atlas Copco Rock Drills Ab Method in respect of a percussive device, percussive device and rock drilling machine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2517243A (en) * 1944-02-26 1950-08-01 Alco Valve Co Pressure controlled pump operating valve mechanism
FR1007678A (fr) * 1948-03-19 1952-05-08 Dispositif de contrôle pour les dispositifs de commande oscillants actionnés par échappement d'air
FR2004864A1 (de) * 1968-03-27 1969-12-05 Krupp Gmbh
DE2849292A1 (de) * 1978-03-22 1979-09-27 Dobson Park Ind Schlagendes oder stossendes handgeraet
US4172411A (en) * 1976-06-09 1979-10-30 Mitsui Engineering & Shipbuilding Co., Ltd. Hydraulic hammer

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2517243A (en) * 1944-02-26 1950-08-01 Alco Valve Co Pressure controlled pump operating valve mechanism
FR1007678A (fr) * 1948-03-19 1952-05-08 Dispositif de contrôle pour les dispositifs de commande oscillants actionnés par échappement d'air
FR2004864A1 (de) * 1968-03-27 1969-12-05 Krupp Gmbh
US4172411A (en) * 1976-06-09 1979-10-30 Mitsui Engineering & Shipbuilding Co., Ltd. Hydraulic hammer
DE2849292A1 (de) * 1978-03-22 1979-09-27 Dobson Park Ind Schlagendes oder stossendes handgeraet

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2618092A1 (fr) * 1987-07-17 1989-01-20 Montabert Ets Distributeur hydraulique pour appareil a percussions mu par un fluide incompressible sous pression
EP0300929A1 (de) * 1987-07-17 1989-01-25 Etablissements Montabert Hydraulischer Verteiler für eine Schlagvorrichtung
WO2008103095A1 (en) 2007-02-23 2008-08-28 Atlas Copco Rock Drills Ab Method in respect of a percussive device, percussive device and rock drilling machine
EP2118427A1 (de) * 2007-02-23 2009-11-18 Atlas Copco Rock Drills AB Verfahren bezüglich einer schlagvorrichtung, schlagvorrichtung und gesteinsbohrmaschine
EP2118427A4 (de) * 2007-02-23 2014-05-14 Atlas Copco Rock Drills Ab Verfahren bezüglich einer schlagvorrichtung, schlagvorrichtung und gesteinsbohrmaschine

Also Published As

Publication number Publication date
SE8402232L (sv) 1985-10-25
SE8402232D0 (sv) 1984-04-24
SE442100B (sv) 1985-12-02

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Effective date: 19860714

RIN1 Information on inventor provided before grant (corrected)

Inventor name: JAKOBSSON, BERTIL TORBJOERN

Inventor name: HANSSON, BROR HALDO