WO2006097816A1 - Machine a percussion oleodynamique a vanne d'arret a tiroir et piston pilote - Google Patents

Machine a percussion oleodynamique a vanne d'arret a tiroir et piston pilote Download PDF

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Publication number
WO2006097816A1
WO2006097816A1 PCT/IB2006/000555 IB2006000555W WO2006097816A1 WO 2006097816 A1 WO2006097816 A1 WO 2006097816A1 IB 2006000555 W IB2006000555 W IB 2006000555W WO 2006097816 A1 WO2006097816 A1 WO 2006097816A1
Authority
WO
WIPO (PCT)
Prior art keywords
volume
throttle
pushing
pilot piston
pilot
Prior art date
Application number
PCT/IB2006/000555
Other languages
English (en)
Inventor
Giammichele CALÒ
Original Assignee
Eutecna S.R.L.
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 Eutecna S.R.L. filed Critical Eutecna S.R.L.
Priority to EP06710541A priority Critical patent/EP1863616A1/fr
Publication of WO2006097816A1 publication Critical patent/WO2006097816A1/fr

Links

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
    • 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
    • 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
    • B25D2209/005—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

  • the present invention relates to a new percussion oleodynamic machine comprising an on-off hydraulic or slide valve, a pilot piston and a primary hitting tool, that transforms mechanical energy into impact energy.
  • Conventional percussion oleodynamic machines comprise a housing with a cylinder therein, in which a reciprocating hitting piston repeatedly impact on a demolisher tool.
  • the demolisher tool transfers the impact energy to the material to be crashed.
  • the piston motion is given by a hydraulic circuit, connected to the high- and low-pressure circuits, which sequentially feed the drive chambers of the hitting tool, giving to said piston a uniformly accelerating motion up to the impact on the tool.
  • the impacting piston transmits a compression wave that propagates from the impact area to the material at sound speed. After the impact, reflected wave combines with the compression wave reducing its speed and as a consequence its impact content.
  • This energy transmission model implies a poor impact efficiency and the dissipated mechanical energy reduces the reliability of the percussion oleodynamic machine and its performances.
  • the invention solves these technical problems being a new oleodynamic percussive machine characterized by a telescopic pilot piston, which interacts with a small on-off slide valve and controls the distribution timing of the machine hydraulic charge and discharge.
  • Said pilot piston is telescopically inserted in the primary hitting tool, from which it receives the consent signal for the oleodynamic positioning.
  • Said signal acts as a set-point for the opening/closing time of the inlet and outlet ports of the hydraulic circuits of the slide valve.
  • the pilot piston telescopic motion is obtained by injecting a certain amount of the pressurized oil coming from the braking chamber.
  • the amount of the pressurized oil depends on the tool penetration in the material; therefore, controlling the rising stroke of the two hitting tooles, the timing and, consequently, the active displacement.
  • Both pilot piston and primary hitting tool have different mass and inertia, different speed (during both rising and descending) and are never in contact, being separated by a pressurized oil control volume.
  • This second impact interacts with the return impact wave, thus preventing the expansion phase of the primary mass (having opposite verse) and instantaneously smoothing the cyclic oscillation.
  • the result is the optimization of the impact energy transfer on the tool, due to the absence of oscillatory phenomena and the control of pilot piston axial position.
  • the oleodynamic percussion machine comprises a high pressure oil-nytrogen source (2), a casing (1) accommodating a primary hitting tool (3) with its pushing chambers (12, 5), a pilot piston (4) with its pushing chambers (5, 23) and a demolisher tool (10).
  • the machine comprises an on-off slide valve (7), with inlet (9) and outlet (8) chambers, a service circuit (14) and the high pressure feeding circuits (11, 26) of the two hitting tools (3, 4).
  • the machine also comprises low pressure discharge circuits (25, 27), connected to the chambers (8, 13) and to the exit collector (18), by means of a low-pressure control throttle (100).
  • the machine includes the control volume (15) of the primary hitting tool, the volume (19), the circuits (20, 21) and the volume (22), with different pushing areas: they provide the supplementary translation of the pilot piston (4), controlled by the pilot throttle (16) of the differential stroke (28).
  • the opening and closing of the on-off slide valve (7) is given by the service circuit (14), the volume (32) and the low pressure control throttle (100).
  • the pressurization of the pushing volume (23) and the feeding circuit (29) is provided by the chamber (6) and the start throttle (24). Referring to the same Fig. 1, the working procedure of the percussion oleodynamic machine will be described.
  • the high-pressure oil from the start throttle 24 immediately pressurizes the pushing chamber (23), allowing the pilot piston (4) to move, and feeds the pushing chamber 5 of the primary hitting tool through the feeding circuit (29) and the pilot throttle (16). Being different the high pressure exposed areas, both the pilot piston (4) and the primary hitting tool (3) are pushed downward.
  • the pilot piston (4) acceleration is proportional to the feeding pressure and inversely proportional to its mass, while its initial speed is kept lower than the speed of the primary hitting tool (3). Such speed difference is controlled by the pilot throttle (16) of the differential stroke (28).
  • Shape, diameter and length of the pilot throttle influence the separation of the two hitting tooles, the pressure difference between the two pushing chambers (5, 23) and the optimal value of the differential stroke (28) between the primary hitting tool (3) and the pilot piston (4).
  • the high pressure, acting on the pushing chambers (5, 12, 19) of the primary hitting tool (3) creates the net force, proportional to the difference between pushing chamber (5) area and pushing chambers (12, 19) areas.
  • the circuit (20) is closed and can not be connected with the circuit (21), which feeds the pushing chamber (22) of the pilot piston (4).
  • the speed of the pilot piston depends on its stroke, from the start up to the impact against the demolisher tool (10).
  • the primary hitting tool (3) and the pilot piston (4) start at the same timo with different speed, separate themselves, the primary hitting tool (3) preceding the pilot piston (4); at the fixed time, they achieve a position defined by the differential stroke (28), and reach the same speed, keeping it constant up the rapid sequential impacts.
  • the oil- gas source provides the oil to keep the pressure in the pushing chambers (23, 5) almost constant.
  • the pilot piston (4) closes the start throttle (24) and pressurizes the chamber (32), which feeds the service circuit (14), and the pushing chamber (9) of the slide valve (7).
  • one important feature of the invention is the control of the differential stroke (28) of the primary hitting tool (3), which determines the telescopic motion of the pilot piston, during the rising stroke.
  • the piston (4) modulates the intervention timing of the vale itself, thus obtaining the variation of the machine active displacement.
  • the pilot piston (4) is inserted into the primary hitting tool (3) and can translate with respect of the hitting tool (3) position, by receiving a hydraulic set point signal. The latter is obtained by injecting a controlled quantity of high-pressure oil (22). This quantity comes from the hydraulic braking chamber (15), which is proportional to the tool penetration and consequently to the material hardness, by means of the hydraulic circuits (20, 21) and the volume (19).
  • a second embodiment of the invention is shown.
  • the hydraulic set point signal, controlling the piston (4) translation can be more precisely obtained by controlling the primary hitting tool (3) motion, when penetrating the material in neutral pressure area.
  • an oil control volume (35) between the body (1) and the hitting tool (3) is created.
  • the mass (3) defines the set point signal, by feeding the volume (36).
  • the latter is constituted by different pressure exposed sections, on the pilot piston (4) connecting channels (34).
  • the pilot piston (4) displacement, inside the hitting tool (3) can be everyway amplified, by suitable dimensioning the pressure exposed sections of the volume (36) sections; the set point signal of the pressure in the volume (15) can become independent.
  • the machine active displacement can be varied in real time and more precisely, by defining the differential stroke translation in a shot to shot modality, even when the impact mechanical conditions change, because of tool (10) rebounce, material non-homogeneity or real working conditions.
  • the impact speed of the hitting tool must be kept inside a defined range, to obtain both an impact optimal efficiency and a high reliability or mechanical resistance of the parts during the impact; moreover, especially for low- medium size machines with lower performances, the invention can be semplified, to reduce the machine production costs.
  • the oleodynamic percussion machine can show some design modifications, though mantaining the same working principle.
  • the modifications are mostly related to the primary hitting tool (3) and pilot piston geometry, the service circuit (14), without the low pressure control throttle (100), and the higher speed of the slide valve (7).
  • the embodiment in Fig. 7 comprises only one knocking and pilot mass (3), having the two functions.
  • the start throttle is inside the slide valve, such solution being suitable for low- medium oleodynamic machines.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

L'invention concerne une machine à percussion oléodynamique comprenant un corps (1) ; au moins un accumulateur huile-azote haute pression (2) ; au moins une vanne du type vanne-tiroir (7), à étranglement de réglage basse pression (100) ; une pluralité de volumes de poussée des éléments mobiles, une pluralité de circuits d'alimentation et de décharge, avec orifices d'entrée et de sortie correspondants, au moins un outil démolisseur (10), caractérisée en ce que ladite vanne-tiroir (7) est une vanne d'arrêt à tiroir, en ce qu'il est prévu deux outils de frappe différents (3, 4), de sorte que par déplacement vers le bas, lesdites masses, d'une inertie différente, sont séparées par un volume d'huile haute pression, du fait d'un étranglement pilote (16) ; et en ce qu'il est prévu un clapet de réglage au démarrage (24) lequel exerce une pression sur le volume de poussée.
PCT/IB2006/000555 2005-03-16 2006-03-03 Machine a percussion oleodynamique a vanne d'arret a tiroir et piston pilote WO2006097816A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06710541A EP1863616A1 (fr) 2005-03-16 2006-03-03 Machine a percussion oleodynamique a vanne d'arret a tiroir et piston pilote

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBA2005A000012 2005-03-16
ITBA20050012 ITBA20050012A1 (it) 2005-03-16 2005-03-16 Macchina oleodinamica a percussione con un cassetto di distribuzione di tipo on-off e pistone pilota

Publications (1)

Publication Number Publication Date
WO2006097816A1 true WO2006097816A1 (fr) 2006-09-21

Family

ID=36572031

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2006/000555 WO2006097816A1 (fr) 2005-03-16 2006-03-03 Machine a percussion oleodynamique a vanne d'arret a tiroir et piston pilote

Country Status (3)

Country Link
EP (1) EP1863616A1 (fr)
IT (1) ITBA20050012A1 (fr)
WO (1) WO2006097816A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4165788A (en) * 1976-11-08 1979-08-28 Roger Montabert Hydraulic percussion apparatus
US4474248A (en) * 1981-04-23 1984-10-02 Giovanni Donadio Hydraulic demolishing rock drill
GB2141657A (en) * 1983-05-10 1985-01-03 Panther Equip Ltd Improvements in hydraulically operated hammers
US4819542A (en) * 1985-12-23 1989-04-11 Spetsialnoe Konstruktorskoe Bjuro Gidroimpulsnoi Tekhniki Sibirskogo Otdelenia Akademii Nauk Sssr Percussive tool
US5960893A (en) * 1996-12-14 1999-10-05 Krupp Bautechnik Gmbh Fluid-powered percussion tool
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

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4165788A (en) * 1976-11-08 1979-08-28 Roger Montabert Hydraulic percussion apparatus
US4474248A (en) * 1981-04-23 1984-10-02 Giovanni Donadio Hydraulic demolishing rock drill
GB2141657A (en) * 1983-05-10 1985-01-03 Panther Equip Ltd Improvements in hydraulically operated hammers
US4819542A (en) * 1985-12-23 1989-04-11 Spetsialnoe Konstruktorskoe Bjuro Gidroimpulsnoi Tekhniki Sibirskogo Otdelenia Akademii Nauk Sssr Percussive tool
US5960893A (en) * 1996-12-14 1999-10-05 Krupp Bautechnik Gmbh Fluid-powered percussion tool
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

Also Published As

Publication number Publication date
EP1863616A1 (fr) 2007-12-12
ITBA20050012A1 (it) 2006-09-17

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