EP0426928A1 - Procédé pour ajuster automatiquement des paramètres de fonction d'un appareil à percussion - Google Patents

Procédé pour ajuster automatiquement des paramètres de fonction d'un appareil à percussion Download PDF

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Publication number
EP0426928A1
EP0426928A1 EP89830451A EP89830451A EP0426928A1 EP 0426928 A1 EP0426928 A1 EP 0426928A1 EP 89830451 A EP89830451 A EP 89830451A EP 89830451 A EP89830451 A EP 89830451A EP 0426928 A1 EP0426928 A1 EP 0426928A1
Authority
EP
European Patent Office
Prior art keywords
distributor
piston
ring
pressure
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.)
Granted
Application number
EP89830451A
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German (de)
English (en)
Other versions
EP0426928B1 (fr
Inventor
Mauro Vitulano
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.)
Individual
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Individual
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 Individual filed Critical Individual
Priority to EP89830451A priority Critical patent/EP0426928B1/fr
Priority to DE68928143T priority patent/DE68928143T2/de
Priority to AT89830451T priority patent/ATE154774T1/de
Priority to ES89830451T priority patent/ES2103711T3/es
Publication of EP0426928A1 publication Critical patent/EP0426928A1/fr
Application granted granted Critical
Publication of EP0426928B1 publication Critical patent/EP0426928B1/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
    • B25D9/14—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

  • the present invention is applied to percussion hydraulic appliances used in both the demolition of very hard materials - such as concrete, reinforced concrete, rocks, frozen surfaces, etc. - and the digging of particularly hard soils, mine marking and extraction, etc.
  • the alternate movement of the piston which strikes the tool in a hydraulic appliance or by incompressible fluid is obtained as a distributor which alternately places the chamber over the piston, in communication with a high-pressure circuit to give it impact power, and with a low-pressure circuit to bring the piston back to the upper dead centre.
  • the commonest distributor consists of a cylindrical tubular component whose external diameter - with the adequate tolerance margin - is equal to the internal diameter of the cylinder where the piston moves: along one of its circular edges, it is connected to a ring plate like to a flange, which runs vertically into a ring chamber coaxial to the cylinder, within the limits prefixed by the height of the same ring chamber.
  • the distributor internal diameter is smaller than the piston head external diameter; in others, the internal diameter is equal to the piston head external diameter, as in the European Patent No. 0085269 by the same applicant.
  • the piston head instead of striking the opposite end of the tubular components forming the distributor, moves inside it, in the opposite direction: in this case, the difference between the diameter of the cylindrical chamber and that of the piston is twice the distributor radial thickness.
  • a common drawback to all the devices causing the piston alternate movement is the lack of capability to adapt the striking rate and power per blow to the hardness of the material to crumble in real time.
  • the device causing the striking mass alternate movement also includes a unidirectional valve which guarantees the fluid passage from the cylindrical chamber over the piston towards the high-pressure circuit and devices which guarantee a quick, subsequent displacement of the distributor, so to rapidly interrupt the connection with the high-pressure circuit and to slowly connect the chamber placed over the piston with the low-pressure circuit.
  • the unidirectional valve permits the passage of the ultracompressed fluid into the cylindrical chamber over the piston, in the fraction of time during which this chamber is isolated from both the low-pressure and the high-pressure circuits, the maximum retrieval of reaction energy should be possible; the piston greater reversal velocity would cause - for a given oil supply - a shorter duration of every cycle of the appliance, as well as an increase in the impact pressure, parallel to the increase in blows frequency.
  • such a device would cause an increase in blows frequency and impact power, which would be higher if the material to crumble is harder, without calling for a greater power i.e. a greater pressure of the oil to the digger or the shovel coupled to the breaker.
  • Such working method is irrational, as the breaking of scarcely compact soils should have a low velocity, although needing a smaller impact power: in other words, and contrarily to any logic, concrete, rocks and very hard materials would be crumbled more rapidly than normally-­compact soils.
  • the appliance where the above-mentioned device is applied absorbs reaction energy, it still undergoes high strains owing to the incompressibility of the fluid.
  • the aim of this invention is to adapt in real time the power and frequency of a percussion appliance to the hardness of the material where it works, avoiding the above-mentioned drawbacks caused by the appliance as in the French Patent No. 8114043.
  • This invention as characterized by our claims - solves the problem to vary the piston stroke and impact energy in real time, in inverse function to the blows frequency, so to adapt the latter to the resistance of the material to crumble, without varying the hydraulic power averagely absorbed by the appliance, i.e. the absorbed power.
  • this invention solves the problem of working on very hard materials such as rocks, concrete, etc., with a lower frequency of greater intensity blows and - on less hard materials - with a greater frequency of lower intensity blows.
  • the advantages obtained through the present invention mainly consist by the fact that the supplied power maintains on an average constant and that therefore the strains that the appliance undergoes when working on very hard materials, and the consequent wear of the tools are smaller.
  • the appliance request a smaller working and maintenance expenditure, and operate by a greater velocity on less hard materials.
  • fig. 3 shows the appliance with the piston at the upper dead centre when the rebound energy is feeble, at the moment when the percussion stroke starts;
  • fig. 4 shows the appliance with the piston at the upper dead centre when the rebound energy is strong, at the moment when the percussion stroke starts;
  • fig. 5 shows the appliance with the piston during the percussion phase and the distributor moving upwards to obstruct the high-pressure oil inlet port;
  • fig. 6 shows the appliance with the piston at the lower dead centre
  • the device according to the invention consists in the combination of the means forming the distributor as in the European Patent No. 0085279 by the same applicant, with the means limiting the distributor upwards stroke during the piston upwards movement, so that the piston start of percussion is anticipated when compared to the upper dead centre, when the material hit by the tool is scarcely hard, whereas, when the material is very hard - i.e. rocks, concrete, etc. - the piston start of percussion occurs exactly at the upper dead centre: the upper dead centre is fixed by stop corner 16.
  • the distributor is made up of a cylindrical tubular component 1, one of whose ends is connected to a flange-type ring plate, which can move with the protruding part 1a having width d1, in a ring chamber having height h and width d1, equal to the width d1 of the flange protruding part.
  • the upwards movements of distributor 1 are caused by differences in pressure on faces 1b and 1c of distributor itself, during the down stroke of piston, the downwards movements of distributor solely by the pressure on face 1b during the up stroke of piston: this is possible because, during the upward movement, piston 3, whenever the contact occurs between its circular edge 3a and the distributor circular edge 1d, compresses the oil of the cylindrical chamber 4 which is placed over the piston surface 3b , provoking the distributor downwards movement, whereas during the blow, when the distributor is in the positions showed in figures 5 and 6, the piston provokes the distributor upwards movement when the latter circular edge 3 - moving downwards - protrudes from the distributor cylindrical cavity anc goes beyond its edge 1d, due to the effect of high pressure on the distributor edge 1c.
  • the annular grove 5 coaxial to the axis of the cylindrical chamber where the piston moves during the downstroke of piston, allows the oil under pressure to push on the distributor face 1c, having width d3, greater than the one of face 1b whose width d2 is smaller then d3, provoking its upward movement: this is made easier because the basis of the ring grove 2 gives a stop edge 2a having width d4, so that d3 - d4 > d2.
  • Duct 9 below ring grove 2 being connected to the low­pressure circuit, aims at creating the differences in downward movement when the high-pressure oil inlet ports 7a must be opened.
  • the above-mentioned means are combined to means permitting different velocities of the oil outlet from the ring chamber 2c, which the protruding ring plate 1a of distributor 1 forms in the upper part of ring grove 2.
  • These means are made up of a gauged duct 11 having a small diameter or, in general, of a duct where a pressure valve is inserted, which communicates chamber 2c with exhaust duct 10, to bring about an exhaust velocity proportional to the pressure exerted by the distributor protruding plate 1a, that also depends on the piston rebound energy and velocity.
  • the distributor cannot get to the stroke-end fixed by the ring grove 2 upper head 2b, that is, it does not run the grove entire height h; therefore, the piston circular edge 3a anticipatedly touches the distributor circular edge 1d, so that the latter can move downwards, anticipatedly reopening the high-pressure oil inlet ports 7a: this brings about a decrease in the piston percussion stroke and, consequently, a decrease in the displacement, i.e. the volume of the cylindrical chamber where the pressurized oil operates, in order to push the piston downwards.
  • this decrease in volume corresponds to an increase in the piston blows frquency: indeed, as the hydraulic power transmitted to the piston is equal to the oil flow Q multiplied by oil pressure p (Q x p), if the pressure and oil flow remain firm and if decreases the volume of the cylindrical chamber where the pressurized oil operates, it takes place an increase in the piston blow frequency.
  • the piston greater stroke upwards provokes an increase in the volume of the cylindrical chamber where the pressurized oil operates to push the piston downwards and, consequently, an increase in the push that the highpressure oil exerts on the piston face 3b.
  • the device also includes a maximum pressure valve 21, which discharges the oil into the high-pressure circuit if the piston rebound energy exceeds certain limits, so to further compress the gas contained in the accumulator 13 (i.e. nitrogen) through membranee 13a.
  • a maximum pressure valve 21 which discharges the oil into the high-pressure circuit if the piston rebound energy exceeds certain limits, so to further compress the gas contained in the accumulator 13 (i.e. nitrogen) through membranee 13a.
  • Valve 12 also works as a safety valve.
  • Figures 3 to 11 show the application of the distribution device according to the invention (EPC Rule 30a), to the percussion appliance according to the European Patent No. 0085279.
  • the device according to the invention can be applied only to appliances of the type described in the European Patent No. 0085279, i.e. to appliances where distributor 1 moves to open or to close the high-pressure oil inlet ports 7a and the low-pressure oil discharge ports, only as an effect of the pressures transmitted by the piston movements to the distributor ring faces 1b and 1c through the oil.
  • the distributor moves in the opposite direction of the piston which runs coaxially inside it, that is downwards to open the high-pressure oil inlet ports 7a immediately after the contact between the upward-moving piston ring edge 3a and the distributor ring edge 1d or, alternatively, upwards to close these ports 7a when, during its percussion stroke, the piston ring edge 3a passes the distributor ring edge 1d.
  • the height h of ring grove 2 depends on either a greater or a smaller stroke allowed to distributor 1; similarly, the gauged duct 11 section or the pressure valve replacing its function, must be chosen according to the performance desired from the appliance.
  • the mechanical stroke-end 16 limits the piston upwards maximum stroke.
  • the push for the piston upward movement is permanently applied to the ring surface 3d1 having width s, and it has an effect only when the high-pressure oil inlet ports 7a are closed.
  • C1 and c2 indicate the axial length of the chamber 4, which is placed above the piston head.

Landscapes

  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Lock And Its Accessories (AREA)
  • Polyesters Or Polycarbonates (AREA)
EP89830451A 1989-10-18 1989-10-18 Procédé pour ajuster automatiquement des paramètres de fonction d'un appareil à percussion Expired - Lifetime EP0426928B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP89830451A EP0426928B1 (fr) 1989-10-18 1989-10-18 Procédé pour ajuster automatiquement des paramètres de fonction d'un appareil à percussion
DE68928143T DE68928143T2 (de) 1989-10-18 1989-10-18 Verfahren zum automatischen Anpassen der Funktionsparameter eines Schlagapparates
AT89830451T ATE154774T1 (de) 1989-10-18 1989-10-18 Verfahren zum automatischen anpassen der funktionsparameter eines schlagapparates
ES89830451T ES2103711T3 (es) 1989-10-18 1989-10-18 Metodo para ajustar automaticamente los parametros funcionales de un aparato hidraulico de percusion.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP89830451A EP0426928B1 (fr) 1989-10-18 1989-10-18 Procédé pour ajuster automatiquement des paramètres de fonction d'un appareil à percussion

Publications (2)

Publication Number Publication Date
EP0426928A1 true EP0426928A1 (fr) 1991-05-15
EP0426928B1 EP0426928B1 (fr) 1997-06-25

Family

ID=8203241

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89830451A Expired - Lifetime EP0426928B1 (fr) 1989-10-18 1989-10-18 Procédé pour ajuster automatiquement des paramètres de fonction d'un appareil à percussion

Country Status (4)

Country Link
EP (1) EP0426928B1 (fr)
AT (1) ATE154774T1 (fr)
DE (1) DE68928143T2 (fr)
ES (1) ES2103711T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000078510A2 (fr) * 1999-06-22 2000-12-28 Priver Industriale S.R.L. Machine a percussion a pression dynamique innovante fonctionnant a pression hydraulique constante
US6877569B2 (en) 2001-05-09 2005-04-12 Sandvik Tamrock Oy Method for controlling operating cycle of impact device, and impact device
WO2005065891A1 (fr) * 2003-12-19 2005-07-21 Clark Equipment Company Outil d'impact
ITBA20120055A1 (it) * 2012-09-24 2014-03-25 Tecna Group Srl Demolitore per escavatori con pistone e circuito idraulico ottimizzato
WO2019190381A1 (fr) 2018-03-28 2019-10-03 Epiroc Rock Drills Aktiebolag Dispositif de percussion et procédé de commande de mécanisme de percussion d'un dispositif de percussion

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2509217A1 (fr) * 1981-07-10 1983-01-14 Montabert Ets Appareil a percussions mu par un fluide sous pression
EP0085279A1 (fr) * 1982-01-22 1983-08-10 Mauro Vitulano Valve pour commander le mouvement alternatif d'un piston de machine hydraulique à percussion, en particulier pour marteaux hydrauliques
EP0256955A1 (fr) * 1986-08-07 1988-02-24 Etablissements Montabert Procédé de régulation des paramètres de percussion du piston de frappe d'un appareil mû par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procédé

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2509217A1 (fr) * 1981-07-10 1983-01-14 Montabert Ets Appareil a percussions mu par un fluide sous pression
EP0085279A1 (fr) * 1982-01-22 1983-08-10 Mauro Vitulano Valve pour commander le mouvement alternatif d'un piston de machine hydraulique à percussion, en particulier pour marteaux hydrauliques
EP0256955A1 (fr) * 1986-08-07 1988-02-24 Etablissements Montabert Procédé de régulation des paramètres de percussion du piston de frappe d'un appareil mû par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procédé

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000078510A2 (fr) * 1999-06-22 2000-12-28 Priver Industriale S.R.L. Machine a percussion a pression dynamique innovante fonctionnant a pression hydraulique constante
WO2000078510A3 (fr) * 1999-06-22 2001-07-19 Priver Ind S R L Machine a percussion a pression dynamique innovante fonctionnant a pression hydraulique constante
US6877569B2 (en) 2001-05-09 2005-04-12 Sandvik Tamrock Oy Method for controlling operating cycle of impact device, and impact device
EP1964647A2 (fr) 2001-05-09 2008-09-03 Sandvik Mining and Construction Oy Procédé pour le contrôle d'un cycle de fonctionnement d'un dispositif d'impact et dispositif d'impact
WO2005065891A1 (fr) * 2003-12-19 2005-07-21 Clark Equipment Company Outil d'impact
US7156190B2 (en) 2003-12-19 2007-01-02 Clark Equipment Company Impact tool
ITBA20120055A1 (it) * 2012-09-24 2014-03-25 Tecna Group Srl Demolitore per escavatori con pistone e circuito idraulico ottimizzato
WO2014045264A1 (fr) * 2012-09-24 2014-03-27 Tecna Group Srl Concasseur pour excavatrices à circuit hydraulique optimisé
WO2019190381A1 (fr) 2018-03-28 2019-10-03 Epiroc Rock Drills Aktiebolag Dispositif de percussion et procédé de commande de mécanisme de percussion d'un dispositif de percussion

Also Published As

Publication number Publication date
DE68928143T2 (de) 1997-12-11
EP0426928B1 (fr) 1997-06-25
ES2103711T3 (es) 1997-10-01
ATE154774T1 (de) 1997-07-15
DE68928143D1 (de) 1997-07-31

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