WO2015142259A1 - Vanne de distribution et machine de forage de roche - Google Patents

Vanne de distribution et machine de forage de roche Download PDF

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Publication number
WO2015142259A1
WO2015142259A1 PCT/SE2015/050299 SE2015050299W WO2015142259A1 WO 2015142259 A1 WO2015142259 A1 WO 2015142259A1 SE 2015050299 W SE2015050299 W SE 2015050299W WO 2015142259 A1 WO2015142259 A1 WO 2015142259A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
end wall
valve body
plunger
chamber
Prior art date
Application number
PCT/SE2015/050299
Other languages
English (en)
Inventor
Ulf Nilsson
Thomas Johansson
Original Assignee
Atlas Copco Rock Drills 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 Rock Drills Ab filed Critical Atlas Copco Rock Drills Ab
Publication of WO2015142259A1 publication Critical patent/WO2015142259A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/04—Construction of housing; Use of materials therefor of sliding valves
    • F16K27/041—Construction of housing; Use of materials therefor of sliding valves cylindrical slide valves
    • 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
    • B25D9/16—Valve arrangements therefor
    • B25D9/20—Valve arrangements therefor involving a tubular-type slide valve
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B1/00—Percussion drilling
    • E21B1/12—Percussion drilling with a reciprocating impulse member
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B1/00—Percussion drilling
    • E21B1/12—Percussion drilling with a reciprocating impulse member
    • E21B1/24—Percussion drilling with a reciprocating impulse member the impulse member being a piston driven directly by fluid pressure
    • E21B1/26—Percussion drilling with a reciprocating impulse member the impulse member being a piston driven directly by fluid pressure by liquid pressure
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • 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
    • B25D2209/007—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 not coaxial with the piston

Definitions

  • the invention relates to a distribution valve for controlling hydraulic flows to different consumers, wherein the distribution valve includes a valve body being arranged movable to and fro in axial directions in a valve chamber, and wherein the valve chamber is limited in axial directions by a first and a second valve end wall.
  • the invention also concerns a hydraulic rock drilling machine including such a device.
  • Distribution valves for intermittently providing pressure fluid to different kinds of consumers as well as evacuating them are previously known for the use in a broad range of technical fields.
  • the distribution valve aims to provide intermittent pressurizing of the drive chambers for the percussive piston for achieving the desired percussive effect.
  • the to and fro movable valve body is controlled with the aid of pilot pressure so as to transmit drive pressure to the drive chambers of the rock drilling machine.
  • valve body includes a central bore hole extending in axial direction which cooperates with a plunger being adjoining to the second valve end wall for forming of a pressurizable space
  • the plunger includes an outer piston portion having reduced diameter and being directed from the second valve end wall, which in an end position region of the valve body is arranged, together with a portion of the bore hole having corresponding reduced diameter, to cooperate in order to establish a damping chamber for end position damping of the valve body.
  • the impact force on a valve end wall will be lower.
  • the strain on associated components will thereby be lower.
  • the end position damping is advantageously provided for movements in directions of the most sensitive parts of the distribution valves that might risk to be damaged at impact with full speed of a valve body.
  • the valve body can be allowed to have higher speed than otherwise during the main part of its movement between the end positions .
  • damping chamber being arranged to work with a constantly pressurized medium, damping will be obtained that is predictable and repeatedly securely calculated with an advantageously small damping chamber volume.
  • the valve according to the invention can be simply and economically produced. Finishing machining of the valve body can be made in one machine set up which results in faster and more secure manufacture and achieving required tolerances more securely.
  • the portions of the bore hole as well as the portions of the plunger are circular cylindrical.
  • a damping slot advantageously exists between the outer piston portion and the portion of the bore hole having reduced diameter.
  • the damping slot there is a transformation of kinetic energy in through- flowing hydraulic medium into thermal energy in the hydraulic medium, which results in desired energy absorption.
  • the person skilled in the art is within normal activities capable of dimensioning the damping slot for adaption to existing parameters such as speed and used hydraulic medium in order to secure that desired damping distance and damping characteristics are obtained.
  • the valve in or in the region of the first valve end wall, the valve includes a pressurizable chamber which receives a central end piston portion belonging to the valve body and being provided with an end surface for, in a
  • pressurized state of the chamber driving the valve body in the direction of the second valve end wall. It is particularly preferred that in pressurized state of the space and pressureless state of the chamber, it is arranged for driving the valve body in the direction towards the second valve end wall .
  • the plunger is free from the second valve end wall.
  • the plunger will then be pressed for lying against the second valve end wall by the pressure in said bore hole in the valve body and be allowed to be free from side force influence from the second valve end wall and instead be entirely guided by the bore hole. This results in minimized seize risk, since the plunger in a preferred manner is guided in radial direction against the valve body which in turn is guided by a valve lining/a valve housing, without creating any radial relative forces between the plunger and the valve body. This also allows manufacture with reduced tolerance
  • the plunger can however be connected to the second valve end wall while allowing a relative movement in a radial direction in respect of the second valve end wall. Through this mutual mobility, it is allowed that the plunger to a certain extent can follow the movements of the valve body in a radial direction which at least reduces the seize risk. It is thinkable, but in most cases not suitable, that the plunger and the second valve end wall are rigidly immovably joined to each other. This is not preferred since with this solution there is a risk of seizing tendencies.
  • the bore hole there is preferably arranged at least one hole in a wall of the valve body in order to allow permanent pressurization of the space so as to facilitate permanent pressurization directly from one of the ports of the distribution valve.
  • the permanent pressurization is preferably provided by a system pressure source being connected to the distribution valve.
  • the person skilled in the art suitably dimensions a relation cross section area/initial damping chamber volume (at just established damping chamber) after requirements and field of use for obtaining desired speed reduction at the same time as desired length of the damping distance.
  • the invention also concerns a hydraulic rock drilling machine with a machine housing which receives a working cylinder with a to and fro movable percussive piston wherein the rock drilling machine includes a valve according to the above .
  • the distribution valve has an axis, preferably being parallel to an axis of the working cylinder, giving the possibility of building the rock drilling machine slim and space- saving.
  • the rock drilling machine includes a housing end wall for the working cylinder, said housing end wall also closing a space receiving the
  • Fig. 1 shows a rock drilling machine equipped with a distribution valve according to the invention in an axial section
  • Fig. 2 shows an enlarged section of a distribution valve according to the invention in a first position
  • Figs. 3a and 3b show an enlarged section and a part enlargement of the distribution valve in Fig. 2 in a second position
  • Fig. 4 shows an enlarged section of the distribution valve in Fig. 2 in a third position.
  • Fig. 1 is thus shown in an axial section a rock drilling machine 1 including a machine housing 2, wherein a percussive piston 3 is axially movable to and fro inside a cylinder space comprising a working cylinder 4.
  • the percussive piston 3 performs impacts in an impact direction R against a shank adapter 5 in a per se previously known manner.
  • a distribution valve 7 for distributing pressure fluid to the drive chambers of the rock drilling machine for driving the percussive piston 3 to and fro.
  • Fig. 1 the distribution valve 7 is shown with its valve axis parallel to the axis of the percussive piston 3 and the working cylinder 4, being the axis of the percussion device of the rock drilling machine 1.
  • This embodiment has the advantage that the rock drilling machine can be made slim and space saving at its rear part .
  • the distribution valve 7 is shown in an enlarged scale, whereby is clarified that the distribution valve 7 has a valve body 8 being movable to and fro inside a valve lining 9, the valve body being movable between two end positions defined by stops against a first valve end wall 10 and a second valve end wall 11.
  • the valve lining 9 delimits a valve chamber 33 for receiving the valve body 8 and has the usual bores comprising channel ports for channels being connected to the distribution valve 7.
  • the valve lining 9 is arranged with accurately defined control edges for cooperation with corresponding control lands on the valve body 8.
  • valve body 8 of the distribution valve 7 is positioned in a first end position with a first contact end 21 abutting against a first end stop 17 on the first valve end wall 10 of the valve body 8.
  • the valve body 8 is in this position with a second contact end 22 at a distance from a second end stop 34 on the second valve end wall 11.
  • valve body in Fig. 2 The position of the valve body in Fig. 2 occurs because of a chamber 14, which receives a central end piston portion
  • a space 16 is arranged inside the valve body 8. Said space 16 is during operation permanently pressurized via holes 27 in the wall of the valve body from an equally permanently pressurized valve port.
  • the pressure in the space 16 acts against the end surface
  • the permanently pressurized space 16 is defined by a bore extending coaxially with the axis of the valve body.
  • the axially second end of the space 16, opposite to the end surface 24, is limited by a plunger 35 extending sealingly into the bore hole, said plunger being pressed against the second valve end wall 11 by the pressure existing inside the space 16.
  • valve body furthermore, through a snug slit, sealing cooperation while allowing the valve body to be axially movable in respect of the second valve end wall and to the plunger.
  • the chamber 14 is pressurized such that a hydraulic pressure acts on the end surface 15 of the central end piston portion 23 of the valve body 8. Because of the area of the end surface 15 being greater than the area of the end surface 24 and typically the same pressure prevails in the chamber 14 and in the space 16, the valve body starts to be driven in the direction of its second end position and will after a certain time period be in the position shown in Fig. 3a.
  • an outer piston portion 36 of the plunger 35 With the valve body in the position shown in Fig. 3a, an outer piston portion 36 of the plunger 35, said outer piston portion 36 having a smaller diameter d compared to a larger diameter D of a main portion 37 of the plunger, has just reached a portion 38 of the bore hole with essentially the smaller diameter d (deviates somewhat because of a slot existing between the elements) .
  • the main portion 37 of the plunger is in fact always in a portion 39 of the bore hole having (essentially) the greater diameter D (deviates somewhat because of a slot existing between the elements) .
  • a damping chamber 40 In this position of the valve body, through cooperation with the outer piston portion 36 and the portion 38 of the bore hole having the smaller diameter d, it is arranged that a damping chamber 40 will be established.
  • the damping chamber is as is shown in the detail enlargement in Fig. 3b essentially limited by:
  • the hydraulic medium will thereby leak out through the damping slot 41 against the pressure inside the permanently pressurized space 16 inside the valve body 8.
  • the damping is effected by the kinetic energy in the valve body being transformed to heat absorbed by the hydraulic medium during the passage thereof through the damping slot. Hydraulic medium inside the damping chamber will
  • valve body 8 In the second end position of the valve body 8 shown in Fig. 4, the valve body 8 is in contact with the second contact end 22 against the second end stop 34 on the second valve end wall 11.
  • a damping throttle 47 is arranged which can be fixed or adjustable. This gives the possibilities of control and reduces requirements for dimensioning the damping slot.
  • a pressure source P for supplying hydraulic medium with the same pressure as prevails in the space 16 to the damping chamber In order to reduce tendencies of cavitation, it is possible but not preferred to connect a pressure source P for supplying hydraulic medium with the same pressure as prevails in the space 16 to the damping chamber.
  • a pressure source P for supplying hydraulic medium In a channel 48
  • the first as well as the second valve end wall 10, 11 can be movable such that both valve end walls can be pressed against stops in the direction of each other for defining two defined end positions for the valve body 8. It is however within the scope of the invention that the valve end walls are attached to the valve housing in a conventional manner through for example screwing, bolting, being inserted and locked cross wise etc.
  • the distribution valve 7 can be manufactured also without a specific valve lining 9.
  • valve end wall is to be understood an end wall of a valve chamber.
  • pressureless state of the chamber 14 is intended that the chamber is disconnected from high pressure/ system pressure and instead has been connected to low pressure or atmosphere pressure.
  • the invention has been described at the background of a hydraulic rock drilling machine but the person skilled in the art of control technology realizes that the invention is applicable for distribution valves for controlling hydraulic flows to different consumers also within other technical fields besides rock drilling.
  • the invention is therefore valuable within all kinds of technical fields where the advantages mentioned in the general part of the description above can be exploited such as for example: lower degree of strain during operation, higher switching speed, lower risk of cavitation, predictable damping, small volume of the damping chamber, good production economy.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Geochemistry & Mineralogy (AREA)
  • General Engineering & Computer Science (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Lift Valve (AREA)
  • Multiple-Way Valves (AREA)
  • Earth Drilling (AREA)

Abstract

Vanne de distribution (7) destinée à commander des écoulements hydrauliques jusqu'à différents consommateurs, la vanne de distribution comprenant un corps (8) de vanne mobile d'avant en arrière. Le corps (8) de vanne comprend un trou de forage central (38, 39) s'étendant dans la direction axiale qui coopère avec un piston plongeur (35) et entraîne le corps (8) de vanne dans un état de mise sous pression. Le piston plongeur comprend une partie extérieure (36) de piston ayant un diamètre réduit (d), qui dans une région de position d'extrémité du corps de vanne est conçu, conjointement avec une partie (38) du trou de forage ayant le diamètre réduit (d), pour établir une chambre d'amortissement (40) pour l'amortissement de position d'extrémité du corps (8) de vanne. L'invention concerne en outre une machine de forage de roche.
PCT/SE2015/050299 2014-03-18 2015-03-17 Vanne de distribution et machine de forage de roche WO2015142259A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE1450300A SE538091C2 (sv) 2014-03-18 2014-03-18 Fördelningsventil och bergborrmaskin
SE1450300-7 2014-03-18

Publications (1)

Publication Number Publication Date
WO2015142259A1 true WO2015142259A1 (fr) 2015-09-24

Family

ID=54145054

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2015/050299 WO2015142259A1 (fr) 2014-03-18 2015-03-17 Vanne de distribution et machine de forage de roche

Country Status (2)

Country Link
SE (1) SE538091C2 (fr)
WO (1) WO2015142259A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4084486A (en) * 1975-06-26 1978-04-18 Linden-Alimak Ab Hydraulically driven striking device
US4474248A (en) * 1981-04-23 1984-10-02 Giovanni Donadio Hydraulic demolishing rock drill
US4756330A (en) * 1986-03-21 1988-07-12 Zahnradfabrik Friedrichshafen, Ag. Flow divider valve
JP4514900B2 (ja) * 2000-05-31 2010-07-28 古河機械金属株式会社 油圧打撃装置の緩衝機構
WO2014084776A1 (fr) * 2012-11-28 2014-06-05 Atlas Copco Rock Drills Ab Dispositif dans une machine de forage rocheux et machine de forage rocheux
SE1350104A1 (sv) * 2013-01-30 2014-07-31 Atlas Copco Rock Drills Ab Förfarande för dämpning vid en borrmaskin samt en borrmaskin

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4084486A (en) * 1975-06-26 1978-04-18 Linden-Alimak Ab Hydraulically driven striking device
US4474248A (en) * 1981-04-23 1984-10-02 Giovanni Donadio Hydraulic demolishing rock drill
US4756330A (en) * 1986-03-21 1988-07-12 Zahnradfabrik Friedrichshafen, Ag. Flow divider valve
JP4514900B2 (ja) * 2000-05-31 2010-07-28 古河機械金属株式会社 油圧打撃装置の緩衝機構
WO2014084776A1 (fr) * 2012-11-28 2014-06-05 Atlas Copco Rock Drills Ab Dispositif dans une machine de forage rocheux et machine de forage rocheux
SE1350104A1 (sv) * 2013-01-30 2014-07-31 Atlas Copco Rock Drills Ab Förfarande för dämpning vid en borrmaskin samt en borrmaskin

Also Published As

Publication number Publication date
SE538091C2 (sv) 2016-03-01
SE1450300A1 (sv) 2015-09-19

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