EP0070246B1 - Hydraulic percussion device - Google Patents

Hydraulic percussion device Download PDF

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Publication number
EP0070246B1
EP0070246B1 EP82420091A EP82420091A EP0070246B1 EP 0070246 B1 EP0070246 B1 EP 0070246B1 EP 82420091 A EP82420091 A EP 82420091A EP 82420091 A EP82420091 A EP 82420091A EP 0070246 B1 EP0070246 B1 EP 0070246B1
Authority
EP
European Patent Office
Prior art keywords
chamber
piston
distributor
high pressure
pressure circuit
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.)
Expired
Application number
EP82420091A
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German (de)
French (fr)
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EP0070246A1 (en
Inventor
Roger Montabert
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.)
Montabert SAS
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Montabert SAS
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Publication date
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Priority to AT82420091T priority Critical patent/ATE9071T1/en
Publication of EP0070246A1 publication Critical patent/EP0070246A1/en
Application granted granted Critical
Publication of EP0070246B1 publication Critical patent/EP0070246B1/en
Expired legal-status Critical Current

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    • 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
    • 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
    • B25D9/145—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
    • 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

  • the present invention relates to a percussion device driven by a pressurized fluid such as an incompressible hydraulic fluid.
  • This device provides, by means of a striking striking mass in the form of a piston, a succession of percussions on a tool.
  • the piston is slidably mounted in a cylinder which, formed in the body of the device and comprising lights, connected by channels, is also used for the sliding of a distributor putting the chamber located above the piston in alternative communication with the high pressure circuit to allow rapid descent of the piston and with a low pressure circuit to allow the return stroke of this piston.
  • the distributor is pushed by a spring in the direction of the tool, in accordance with the subject of French patent No 1431835.
  • the dispenser can for example be moved not by the spring, but by pushers driven by hydraulic pressure, in accordance with certificate of addition No 2045289 to French patent No 1431835, or be moved by a central plunger with two opposite rods in accordance with French patent FR-A No 2369908.
  • This return compression wave is usually dissipated either in the body of the device via the flange of the tool, or returned to the piston in the form of kinetic energy.
  • the piston rebounds and pushes the fluid towards the low pressure circuit in the form of a hydraulic pressure wave usually called water hammer in hydraulic installations.
  • the object of the invention is to allow the recovery of the energy contained in the compression wave back in the tool, in order to reuse it later.
  • the apparatus which it relates comprises, on the one hand, a non-return valve allowing the passage of fluid from the chamber located above the striking piston towards the high pressure circuit and, on the other hand, means ensuring a sequential movement of the distributor, so that, starting from a position in which the chamber located above the piston is in communication with the high pressure, the distributor moves very quickly to a position in which it cuts the communication between said chamber and the high pressure, then at reduced and controlled speed, so as to delay the communication of the chamber with the low pressure network, in order to allow, throughout the isolation time of the chamber located above the piston vis-à-vis the high pressure and low pressure networks, the maximum recovery of the energy of restitution, by compression of the fluid isolated in the chamber and passage of this latter in the high pressure network by the non-return valve.
  • the traveling time of the striker district between the closure of the communication between the chamber situated above the piston and the high pressure network and the communication of this same chamber with the low pressure network is equal to the time necessary for the most important restitution known according to the hardest rocks.
  • This feature allows maximum energy recovery, regardless of the nature of the material to be broken with this percussion device.
  • the distributor undergoes a new acceleration movement as soon as the chamber located above the piston is in communication with the low pressure network, so as to largely release this opening and to allow a free movement of the moving striking mass.
  • the distributor comprises two parts of different sections, namely a part located on the side of the piston, of section corresponding to the section of the cylinder in which the striking piston is slidably mounted, and a part of larger section located on the side opposite to the piston, this part of larger section being mounted in a cavity which, extending the cylinder, is of section greater than that of the part of large section of the distributor, this part of large section of dispenser can enter a chamber of the same section as it, disposed between the cylinder and the enlarged cavity, the beginning of penetration into this chamber being made when the dispenser arrives in a position in which it closes the communication between the chamber located at above the piston and the high pressure network, the annular volume delimited by the chamber of intermediate section and by the connection between the two sections of the distributor communicating with the chamber located above the piston by at least one calibrated leak orifice.
  • the calibrated orifice allowing the escape of fluid from the annular chamber is formed in the wall externally limiting the latter.
  • a channel is formed axially in the distributor, the end of which opens into the crown connecting the zones of different sections of the distributor forms the calibrated orifice ensuring the escape of fluid from the annular chamber.
  • the distributor 10 comprises two parts of different sections, namely a lower part 16 of diameter corresponding to that of the cylinder 4 in which the striking piston 2 moves, engaged in the upper end of this cylinder, and an upper part 17 of larger section.
  • This part 17 is housed in a cavity 18 of section substantially greater than its own.
  • the increase in section of the cavity 18 relative to that of the dispenser 17 is obtained by providing a lateral recess in the form of a half-moon, while in FIG. 7, the cavity 18 comprises two diametrically opposite recesses, each in the shape of a half-moon.
  • Part 17 of the dispenser can, however, enter a chamber 19 of section corresponding to its own, the chamber 19 extending the cylinder 4.
  • the dimensions of the chamber 19 and the enlarged part 17 or collar of the distributor are such that the distributor ensures the closure of the passage between the high pressure 12 and the chamber 11 situated above the piston when the collar 17 arrives at the level of chamber 19 and comes close it.
  • non-return valve 22 aims to allow the passage of pressurized fluid from the chamber 11 to the high pressure network 12.
  • This travel time during which the chamber 11 will be isolated from both the high pressure 12 and low pressure networks 13 will allow, as shown in FIG. 3, the maximum recovery of the energy of restitution by passage of the compressed fluid by the striking piston 2 from the chamber 11 towards the high pressure network, and more precisely towards the accumulator 24 thereof via the valve. non-return 22.
  • This phase corresponds to the displacement (d1, d2) of the distributor during the period (t1, t2) of the diagram in FIG. 13.
  • Fig. 8 shows a variant of the exhaust of the annular chamber 19.
  • a channel 25 is formed axially in the distributor which opens into the crown 23 connecting its zones of different sections.
  • the function of escaping the fluid through the channel 25 is exactly the same as through the calibrated orifice 20.
  • the non-return valve 22 is returned to its seat, thanks to a central chamber 26 located under the head of the valve, which is connected by a channel 29 to the low pressure network.
  • the non-return valve 22 is returned to its seat, thanks to an annular chamber 27 which, resulting from the difference between two diameters 28a and 28b, is connected by a channel 29 to the low pressure network.
  • valve 22 is held in the closed position by the vacuum existing between the high pressure network 12 and the chamber 11 as soon as the direction of circulation of the fluid tends to reverse, because the valve lift is limited by a stop 30 to a reduced game J.
  • valve 22 is returned to the closed position by a spring 32 bearing, on the one hand, on the valve and, on the other hand, on a stop 33 located on the side of the high pressure network.
  • FIG. 12 of the drawing shows an alternative embodiment of the apparatus of FIGS. 1 to 5, in which the distributor 10 is no longer subjected to the action of a spring 14, but to the action of a central plunger 34 with two opposite rods.
  • the valve return device shown in FIG. 8 any of those shown in FIGS. 9 to 11 can be considered.
  • the distributor 10 has a groove 35 formed between the cylindrical parts 16 and 17.
  • the body of the cylinder 4 is also formed at least one channel 36 which is broadly dimensioned and which, opening into the cavity in which the cylindrical part 16 slides , communicates with the cavity 18.
  • the channel 36 is also positioned so as to put the annular volume formed by the groove 35 into communication with the low pressure network, as soon as the position of the distributor 10 ensures the communication of the chamber 11 with the low pressure network. This allows a further acceleration of the movement of the dispenser.
  • the fluid escaping from the chamber 18 is produced by a channel 25, as in the case shown in FIG. 8.
  • a groove 37 is formed at the periphery of the chamber 19, and a channel 38 is formed in the distributor, capable of placing the chamber 19 in broad communication with the low pressure network, as soon as the position of the distributor 10 ensures the setting in communication of chamber 11 with the low pressure network.
  • the invention brings a great improvement to the existing technique by providing a percussion device whose structure is not more complex than that of traditional devices, and which has much higher performance and reliability. to those of the latter.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Valve Device For Special Equipments (AREA)
  • Emulsifying, Dispersing, Foam-Producing Or Wetting Agents (AREA)
  • Medicines Containing Antibodies Or Antigens For Use As Internal Diagnostic Agents (AREA)
  • Pens And Brushes (AREA)
  • Surgical Instruments (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
  • Ultra Sonic Daignosis Equipment (AREA)
  • Earth Drilling (AREA)
  • Lasers (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Catching Or Destruction (AREA)

Abstract

1. A percussion apparatus moved by a pressurised fluid, of the type comprising a mobile striking mass (2) in the form of a piston supplying a series of impacts on a tool (3), this piston being slidably mounted in a cylinder (4) which, provided in the body (5) of the apparatus and including ports (6, 7) connected by ducts (8, 9), serves additionally in the sliding of a distributor (10) connecting the chamber (11) situated above the piston alternately to a high pressure circuit (12), for enabling the piston to descend rapidly, and to a low pressure circuit (13) for effecting the return strocke of this piston, characterised in that it comprises, on the one hand, a non-return valve (22) enabling fluid to pass from the chamber (11) located above the strike piston towards the high pressure circuit (12) and, on the other hand, means ensuring that the distributor (10) is displaced sequentially in such a way that, starting from a position in which the chamber (11) located above the piston is connected to the high pressure (12), the distributor is displaced very rapidly as far as a position in which it interrupts the connection between the said chamber and the high pressure, then at a lower, controlled speed, so as to delay the connecting of the chamber (11) to the low pressure circuit (13), so as to enable the maximum amount of restorative energy to be recovered for the entire duration of the isolation of the chamber located above the piston with respect to the high pressure and low pressure circuits, by compressing the fluid isolated in the chamber for the passage of the latter into the high pressure circuit by means of the non-return valve.

Description

La présente invention a pour objet un appareil à percussion mû par un fluide sous pression tel qu'un fluide hydraulique incompressible.The present invention relates to a percussion device driven by a pressurized fluid such as an incompressible hydraulic fluid.

Cet appareil fournit, par l'intermédiaire d'une masse frappante mobile en forme de piston, une succession de percussions sur un outil. Le piston est monté coulissant dans un cylindre qui, ménagé dans le corps de l'appareil et comportant des lumières, reliées par des canaux sert, en outre, au coulissement d'un distributeur mettant la chambre située au-dessus du piston en communication alternative avec le circuit haute pression pour permettre la descente rapide du piston et avec un circuit basse pression pour permettre la course retour de ce piston.This device provides, by means of a striking striking mass in the form of a piston, a succession of percussions on a tool. The piston is slidably mounted in a cylinder which, formed in the body of the device and comprising lights, connected by channels, is also used for the sliding of a distributor putting the chamber located above the piston in alternative communication with the high pressure circuit to allow rapid descent of the piston and with a low pressure circuit to allow the return stroke of this piston.

Dans cette forme d'exécution, le distributeur est poussé par un ressort en direction de l'outil, conformément à l'objet du brevet français No 1431835.In this embodiment, the distributor is pushed by a spring in the direction of the tool, in accordance with the subject of French patent No 1431835.

Néanmoins, cet appareil pourrait se présenter sous différentes formes, le distributeur pouvant par exemple être déplacé non pas par le ressort, mais par des poussoirs mus par la pression hydraulique, conformément au certificat d'addition No 2045289 au brevet français No 1431835, ou encore être déplacé par un piston plongeur central à deux tiges opposées conformément au brevet français FR-A No 2369908.However, this device could come in different forms, the dispenser can for example be moved not by the spring, but by pushers driven by hydraulic pressure, in accordance with certificate of addition No 2045289 to French patent No 1431835, or be moved by a central plunger with two opposite rods in accordance with French patent FR-A No 2369908.

Le fonctionnement de ce type d'appareil, quel que soit le mode d'actionnement du distributeur, procède d'une technique de base permettant de mettre la chambre située au-dessus du piston alternativement en relation avec la haute et la basse pression, une section annulaire de faible surface et antagoniste étant maintenue constamment à la haute pression, de telle façon que la résultante de forces hydrauliques soit orientée alternativement dans un sens et dans l'autre.The operation of this type of device, whatever the actuation mode of the distributor, proceeds from a basic technique making it possible to put the chamber situated above the piston alternately in relation to the high and the low pressure, a annular section of small surface and antagonistic being constantly maintained at high pressure, so that the resultant of hydraulic forces is oriented alternately in one direction and in the other.

L'étude du fonctionnement de cet appareil montre que l'énergie cinétique, emmagasinée dans le piston de frappe lancé à grande vitesse, se transforme, au moment de l'impact sur l'outil, en une onde de compression, qui va parcourir l'outil à la vitesse du son dans le métal, puis se transformer au contact de la roche en une force susceptible de la fracturer. En fait, une fraction seulement de cette énergie est absorbée par la roche, le solde étant restitué à l'outil sous la forme d'une onde de compression qui revient vers l'appareil.The study of the operation of this device shows that the kinetic energy, stored in the striking piston launched at high speed, transforms, upon impact on the tool, into a compression wave, which will travel l tool at the speed of sound in metal, then transform on contact with the rock into a force likely to fracture it. In fact, only a fraction of this energy is absorbed by the rock, the balance being returned to the tool in the form of a compression wave which returns to the device.

Cette onde de compression en retour est habituellement dissipée soit dans le corps de l'appareil par l'intermédiaire de la collerette de l'outil, soit restituée au piston sous forme d'énergie cinétique. Dans ce cas, le piston rebondit et repousse le fluide vers le circuit basse pression sous la forme d'une onde de pression hydraulique habituellement dénommée coup de bélier dans les installations hydrauliques.This return compression wave is usually dissipated either in the body of the device via the flange of the tool, or returned to the piston in the form of kinetic energy. In this case, the piston rebounds and pushes the fluid towards the low pressure circuit in the form of a hydraulic pressure wave usually called water hammer in hydraulic installations.

Dans les eux cas, non seulement cette énergie en retour est irrémédiablement perdue, mais encore elle induit des sollicitations nuisibles à la bonne tenue du matériel, et notamment l'usure rapide des collerettes de contact entre l'outil et le corps de l'appareil, la fatigue du flexible basse pression ou encore l'échauffement dû à la dissipation de l'énergie de l'onde de retour.In these cases, not only is this return energy irretrievably lost, but it also induces stresses harmful to the good performance of the equipment, and in particular the rapid wear of the contact flanges between the tool and the body of the device. , the fatigue of the low pressure hose or the heating due to the dissipation of the energy of the return wave.

En outre, il faut noter que, dans la mesure où l'onde de compression en retour dans l'outil est restituée au piston sous forme d'énergie cinétique, le piston est aidé dans sa course de retour, et les paramètres de fonctionnement sont modifiés dans le sens d'une diminution de la haute pression proportionnellement à la dureté de la roche, cette diminution de pression étant préjudiciable à l'efficacité de l'appareil.In addition, it should be noted that, since the compression wave back in the tool is restored to the piston in the form of kinetic energy, the piston is assisted in its return stroke, and the operating parameters are modified in the direction of a decrease in high pressure in proportion to the hardness of the rock, this pressure decrease being detrimental to the efficiency of the device.

Le but de l'invention est de permettre la récupération de l'énergie contenue dans l'onde de compression en retour dans l'outil, afin de la réutiliser ultérieurement.The object of the invention is to allow the recovery of the energy contained in the compression wave back in the tool, in order to reuse it later.

A cet effet, l'appareil qu'elle concerne comprend, d'une part, un clapet antiretour permettant le passage de fluide de la chambre située au-dessus du piston de frappe vers le circuit haute pression et, d'autre part, des moyens assurant un déplacement séquentiel du distributeur, de telle sorte que, partant d'une position dans laquelle la chambre située au-dessus du piston est en communication avec la haute pression, le distributeur se déplace très rapidement jusqu'à une position dans laquelle il coupe la communication entre ladite chambre et la haute pression, puis à vitesse réduite et contrôlée, de manière à retarder la mise en communication de la chambre avec le réseau basse pression, afin de permettre, pendant toute la durée d'isolement de la chambre située au-dessus du piston vis-à-vis des réseaux haute pression et basse pression, la récupération maximale de l'énergie de restitution, par compression du fluide isolé dans la chambre et passage de celui-ci dans le réseau haute pression par le clapet antiretour.To this end, the apparatus which it relates comprises, on the one hand, a non-return valve allowing the passage of fluid from the chamber located above the striking piston towards the high pressure circuit and, on the other hand, means ensuring a sequential movement of the distributor, so that, starting from a position in which the chamber located above the piston is in communication with the high pressure, the distributor moves very quickly to a position in which it cuts the communication between said chamber and the high pressure, then at reduced and controlled speed, so as to delay the communication of the chamber with the low pressure network, in order to allow, throughout the isolation time of the chamber located above the piston vis-à-vis the high pressure and low pressure networks, the maximum recovery of the energy of restitution, by compression of the fluid isolated in the chamber and passage of this latter in the high pressure network by the non-return valve.

Cet agencement présente des avantages nombreux et importants, à savoir:

  • - une moindre usure de la collerette d'appui de l'outil;
  • - une meilleure tenue des flexibles basse pression puisque les coups de bélier à ce niveau sont supprimés;
  • - pour un débit donné, une augmentation de la fréquence des impacts puisque l'on peut disposer de tout le fluide récupéré en plus du fluide fourni à l'appareil; cette augmentation de fréquence équivaut au raccourcissement de la durée de chaque cycle, et entraîne une modification des paramètres de fonctionnement en sens inverse du sens précédent, c'est-à-dire dans le sens d'une augmentation de la haute pression, donc de l'efficacité de chaque impact proportionnellement à la dureté du rocher;
  • - une diminution de l'échauffement habituellement dû à la dissipation de l'énergie de l'onde de retour, ce qui est favorable à la bonne tenue dans le temps des organes de l'appareil;
  • - cette amélioration des conditions de fonctionnement permet également une diminution de l'amplitude de recul et des vibrations que doit encaisser le bras-support de l'appareil.
This arrangement has numerous and important advantages, namely:
  • - less wear of the tool support flange;
  • - better resistance of the low pressure hoses since water hammer at this level is eliminated;
  • - for a given flow, an increase in the frequency of impacts since it is possible to have all the recovered fluid in addition to the fluid supplied to the device; this increase in frequency is equivalent to shortening the duration of each cycle, and causes a modification of the operating parameters in the opposite direction to the previous direction, that is to say in the direction of an increase in the high pressure, therefore the effectiveness of each impact in proportion to the hardness of the rock;
  • - A reduction in heating usually due to the dissipation of the energy of the return wave, which is favorable to the good resistance over time of the organs of the apparatus;
  • - This improvement in operating conditions also allows a reduction in the amplitude of recoil and the vibrations that the support arm of the device must receive.

Avantageusement, le temps de déplacement du district buteur entre la fermture de la communication entre la chambre située au-dessus du piston et le réseau haute pression et la mise en communication de cette même chambre avec le réseau basse pression est égal au temps nécessaire pour la restitution la plus importante connue en fonction des roches les plus dures.Advantageously, the traveling time of the striker district between the closure of the communication between the chamber situated above the piston and the high pressure network and the communication of this same chamber with the low pressure network is equal to the time necessary for the most important restitution known according to the hardest rocks.

Cette caractéristique permet une récupération maximale d'énergie, quelle que soit la nature du matériau à briser avec cet appareil à percussions.This feature allows maximum energy recovery, regardless of the nature of the material to be broken with this percussion device.

Conformément à une autre caractéristique préférée de l'invention, le distributeur subit un nouveau mouvement d'accélération dès que la chambre située au-dessus du piston est en communication avec le réseau basse pression, de manière à dégager largement cette ouverture et à permettre un déplacement libre de la masse frappante mobile.In accordance with another preferred characteristic of the invention, the distributor undergoes a new acceleration movement as soon as the chamber located above the piston is in communication with the low pressure network, so as to largely release this opening and to allow a free movement of the moving striking mass.

Selon une forme d'exécution de l'invention, le distributeur comporte deux parties de sections différentes, à savoir une partie située du côté du piston, de section correspondant à la section du cylindre dans lequel est monté coulissant le piston de frappe, et une partie de section plus importante située du côté opposé au piston, cette partie de section plus importante étant montée dans une cavité qui, prolongeant le cylindre, est de section supérieure à celle de la partie de grande section du distributeur, cette partie de grande section du distributeur pouvant pénétrer dans une chambre de même section qu'elle, disposée entre le cylindre et la cavité élargie, le début de la pénétration dans cette chambre se faisant lorsque le distributeur arrive dans une position dans laquelle il ferme la communication entre la chambre située au-dessus du piston et le réseau haute pression, le volume annulaire délimité par la chambre de section intermédiaire et par le raccord entre les deux sections du distributeur communiquant avec la chambre située au-dessus du piston par au moins un orifice de fuite calibré.According to one embodiment of the invention, the distributor comprises two parts of different sections, namely a part located on the side of the piston, of section corresponding to the section of the cylinder in which the striking piston is slidably mounted, and a part of larger section located on the side opposite to the piston, this part of larger section being mounted in a cavity which, extending the cylinder, is of section greater than that of the part of large section of the distributor, this part of large section of dispenser can enter a chamber of the same section as it, disposed between the cylinder and the enlarged cavity, the beginning of penetration into this chamber being made when the dispenser arrives in a position in which it closes the communication between the chamber located at above the piston and the high pressure network, the annular volume delimited by the chamber of intermediate section and by the connection between the two sections of the distributor communicating with the chamber located above the piston by at least one calibrated leak orifice.

Quand la totalité de la partie de grande section ou collerette du distributeur se trouve dans la cavité située au-dessus du cylindre, le distributeur ne subit aucun freinage et se déplace rapidement en direction du piston.When the entire large section or flange of the distributor is in the cavity above the cylinder, the distributor is not braked and moves quickly towards the piston.

Lorsque la couronne correspondant au raccordement des deux sections du distributeur vient fermer la chambre annulaire, il se produit, à l'intérieur de cette dernière, une compression du fluide qu'elle contient, se traduisant par un freinage brutal du mouvement du distributeur. A partir de ce moment, le mouvement du distributeur ne peut se poursuivre que par échappement de fluide par l'orifice calibré. C'est donc de la section de ce dernier que dépend la vitesse de déplacement du distributeur entre la position dans laquelle il assure la séparation entre la chambre située au-dessus du piston et le réseau haute pression et celle où il met en communication cette dernière avec le réseau basse pression.When the crown corresponding to the connection of the two sections of the distributor closes the annular chamber, there occurs, inside the latter, a compression of the fluid which it contains, resulting in a brutal braking of the movement of the distributor. From this moment, the movement of the distributor can only continue by escaping fluid through the calibrated orifice. It is therefore on the section of the latter that the speed of movement of the distributor depends between the position in which it ensures the separation between the chamber located above the piston and the high pressure network and that where it puts the latter into communication. with the low pressure network.

Selon une première possibilité, l'orifice calibré permettant l'échappement de fluide hors de la chambre annulaire est ménagé dans la paroi limitant extérieurement cette dernière.According to a first possibility, the calibrated orifice allowing the escape of fluid from the annular chamber is formed in the wall externally limiting the latter.

Selon une autre possibilité, un canal est ménagé axialement dans le distributeur, dont l'extrémité débouchant dans la couronne raccordant les zones de différentes sections du distributeur forme l'orifice calibré assurant l'échappement de fluide hors de la chambre annulaire.According to another possibility, a channel is formed axially in the distributor, the end of which opens into the crown connecting the zones of different sections of the distributor forms the calibrated orifice ensuring the escape of fluid from the annular chamber.

De toute façon, l'invention sera bien comprise à l'aide de la description qui suit, en référence au dessin schématique annexé représentant, à titre d'exemples non limitatifs, plusieurs formes d'exécution d'un appareil selon l'invention.

  • Les fig. 1 à 5 sont cinq vues en coupe longitudinale d'une première forme d'exécution de cet appareil au cours de cinq phases de fonctionnement;
  • la fig. 6 est une vue partielle en coupe selon la ligne 6-6 de la fig. 1 de la cavité dans laquelle est montée la partie supérieure du distributeur;
  • la fig. 7 est une vue en coupe d'une variante de la cavité de la fig. 6;
  • la fig. 8 est une vue partielle de cet appareil représentant, en coupe, une variante du dispositif d'échappement du fluide hors de la chambre annulaire;
  • les fig. 9, 10 et 11 sont des vues partielles de cet appareil représentant, en coupe, trois formes d'exécution du clapet antiretour situé entre la chambre haute du piston de frappe et le réseau haute pression;
  • la fig. 12 est une vue en coupe longitudinale d'une variante d'exécution de l'appareil des fig. 1 à 5;
  • la fig. 1 3 est une vue représentant un diagramme de déplacement du distributeur en fonction du temps;
  • les fig. 14 et 15 sont deux vues en coupe longitudinale et à échelle agrandie de la partie contenant le distributeur de l'appareil des fig. 1 à 5, au cours de deux phases de fonctionnement;
  • les fig. 16 et 17 sont deux vues en coupe longitudinale et à échelle agrandie de la partie contenant le distributeur de l'appareil de la fig. 8 au cours de deux phases de fonctionnement.
In any case, the invention will be clearly understood with the aid of the description which follows, with reference to the appended schematic drawing representing, by way of nonlimiting examples, several embodiments of an apparatus according to the invention.
  • Figs. 1 to 5 are five views in longitudinal section of a first embodiment of this device during five operating phases;
  • fig. 6 is a partial sectional view along line 6-6 of FIG. 1 of the cavity in which the upper part of the distributor is mounted;
  • fig. 7 is a sectional view of a variant of the cavity of FIG. 6;
  • fig. 8 is a partial view of this device representing, in section, a variant of the fluid exhaust device outside the annular chamber;
  • fig. 9, 10 and 11 are partial views of this device representing, in section, three embodiments of the non-return valve located between the upper chamber of the striking piston and the high pressure network;
  • fig. 12 is a view in longitudinal section of an alternative embodiment of the apparatus of FIGS. 1 to 5;
  • fig. 1 3 is a view showing a movement diagram of the dispenser as a function of time;
  • fig. 14 and 15 are two views in longitudinal section and on an enlarged scale of the part containing the distributor of the apparatus of FIGS. 1 to 5, during two operating phases;
  • fig. 16 and 17 are two views in longitudinal section and on an enlarged scale of the part containing the distributor of the apparatus of FIG. 8 during two operating phases.

Le distributeur 10 comprend deux parties de sections différentes, à savoir une partie inférieure 16 de diamètre correspondant à celui du cylindre 4 dans lequel se déplace le piston de frappe 2, engagé dans l'extrémité supérieure de ce cylindre, et une partie supérieure 17 de section plus importante. Cette partie 17 est logée dans une cavité 18 de section sensiblement supérieure à la sienne.The distributor 10 comprises two parts of different sections, namely a lower part 16 of diameter corresponding to that of the cylinder 4 in which the striking piston 2 moves, engaged in the upper end of this cylinder, and an upper part 17 of larger section. This part 17 is housed in a cavity 18 of section substantially greater than its own.

Dans la forme d'exécution représentée à la fig. 6, l'augmentation de section de la cavité 18 par rapport à celle 17 du distributeur est obtenue par ménagement d'un évidement latéral en forme de demi-lune, tandis que, à la fig. 7, la cavité 18 comprend deux évidements diamétralement opposés, chacun en forme de demi-lune.In the embodiment shown in FIG. 6, the increase in section of the cavity 18 relative to that of the dispenser 17 is obtained by providing a lateral recess in the form of a half-moon, while in FIG. 7, the cavity 18 comprises two diametrically opposite recesses, each in the shape of a half-moon.

La partie 17 du distributeur peut, néanmoins, pénétrer dans une chambre 19 de section correspondant à la sienne, la chambre 19 prolongeant le cylindre 4. Les dimensionnements de la chambre 19 et de la partie élargie 17 ou collerette du distributeur sont tels que le distributeur assure la fermeture du passage entre la haute pression 12 et la chambre 11 située au-dessus du piston lorsque la collerette 17 arrive au niveau de la chambre 19 et vient obturer celle-ci.Part 17 of the dispenser can, however, enter a chamber 19 of section corresponding to its own, the chamber 19 extending the cylinder 4. The dimensions of the chamber 19 and the enlarged part 17 or collar of the distributor are such that the distributor ensures the closure of the passage between the high pressure 12 and the chamber 11 situated above the piston when the collar 17 arrives at the level of chamber 19 and comes close it.

La communication entre la chambre annulaire 19 et la cavité 18 n'est plus assurée que par un orifice calibré 20.Communication between the annular chamber 19 and the cavity 18 is no longer ensured except through a calibrated orifice 20.

Entre la cavité 18 mise en communication avec la chambre 11 par le déplacement du distributeur et le réseau haute pression 12 est prévu un clapet antiretour désigné par la référence générale 22, dont la description sera donnée plus loin. Le clapet antiretour 22 vise à permettre le passage de fluide sous pression de la chambre 11 vers le réseau haute pression 12.Between the cavity 18 placed in communication with the chamber 11 by the movement of the distributor and the high pressure network 12 is provided a non-return valve designated by the general reference 22, the description of which will be given below. The non-return valve 22 aims to allow the passage of pressurized fluid from the chamber 11 to the high pressure network 12.

Le fonctionnement de cet appareil est le su ivant:

  • Dans un premier temps, comme montré à la fig. 1, le distributeur 10 se déplace très rapidement de la position dans laquelle l'admission haute pression se produit, vers une position de fermeture de la haute pression correspondant à la fig. 2. Cette phase correspond au déplacement (d0, d1) pendant la période (t0, t1 ) du diagramme de la fig. 13. Ce déplacement rapide est rendu possible du fait que les deux faces de la collerette 17 du distributeur sont maintenues en relation hydraulique par de larges canaux au niveau de la cavité 18. Lorsque la couronne 23 de raccordement des zones de sections différentes du distributeur arrive au niveau de la chambre 19 et vient obturer celle-ci, un certain volume de fluide est comprimé dans ladite chambre, la poursuite du mouvement de déplacement du distributeur ne pouvant être obtenue que par échappement du fluide par l'orifice calibré 20. Par l'ajustement de la section de l'orifice 20, il est possible de contrôler le temps de déplacement du distributeur entre la position qu'il occupe à la fig. 2 et la position qu'il occupe à la fig.4, ces deux positions correspondant, respectivement, à la fermeture de la haute pression et à l'ouverture du réseau basse pression 13.
The operation of this device is as follows:
  • At first, as shown in fig. 1, the distributor 10 moves very quickly from the position in which the high pressure intake occurs, to a closed position of the high pressure corresponding to FIG. 2. This phase corresponds to the displacement (d0, d1) during the period (t0, t1) of the diagram in fig. 13. This rapid movement is made possible by the fact that the two faces of the collar 17 of the distributor are maintained in hydraulic relation by wide channels at the level of the cavity 18. When the ring 23 for connecting zones of different sections of the distributor arrives at the level of the chamber 19 and comes to close off the latter, a certain volume of fluid is compressed in the said chamber, the continuation of the movement of movement of the distributor can only be obtained by escaping the fluid through the calibrated orifice 20. By l 'adjustment of the section of the orifice 20, it is possible to control the time of movement of the distributor between the position it occupies in fig. 2 and the position which it occupies in FIG. 4, these two positions corresponding, respectively, to the closing of the high pressure and to the opening of the low pressure network 13.

Ce temps de déplacement pendant lequel la chambre 11 sera isolée à la fois des réseaux haute pression 12 et basse pression 13 va permettre, comme montré à la fig. 3, la récupération maximale de l'énergie de restitution par passage du fluide comprimé par le piston de frappe 2 de la chambre 11 vers le réseau haute pression, et plus précisément vers l'accumulateur 24 de celui-ci par l'intermédiaire du clapet antiretour 22. Cette phase correspond au déplacement (d1, d2) du distributeur pendant la période (t1, t2) du diagramme de la fig. 13.This travel time during which the chamber 11 will be isolated from both the high pressure 12 and low pressure networks 13 will allow, as shown in FIG. 3, the maximum recovery of the energy of restitution by passage of the compressed fluid by the striking piston 2 from the chamber 11 towards the high pressure network, and more precisely towards the accumulator 24 thereof via the valve. non-return 22. This phase corresponds to the displacement (d1, d2) of the distributor during the period (t1, t2) of the diagram in FIG. 13.

La récupération d'énergie de restitution étant achevée, le distributeur poursuit sa course vers le bas jusqu'à la position représentée à la fig. 5. La chambre 11, située au-dessus du piston, est progressivement mise en relation avec le circuit basse pression par les canaux 7, 9, autorisant la course de retour du piston de frappe 2, en assurant la vidange du fluide contenu dans cette chambre. Cette phase se traduit par le déplacement (d2, d3) du distributeur, représenté au diagramme de la fig. 13.The recovery of restoring energy having been completed, the distributor continues its downward movement to the position shown in FIG. 5. The chamber 11, located above the piston, is gradually brought into contact with the low pressure circuit by the channels 7, 9, allowing the return stroke of the striking piston 2, ensuring the emptying of the fluid contained in this bedroom. This phase results in the displacement (d2, d3) of the distributor, shown in the diagram in FIG. 13.

La fig. 8 représente une variante de la mise à l'échappement de la chambre annulaire 19. Dans ce cas, un canal 25 est ménagé axialement dans le distributeur qui débouche dans la couronne 23 reliant ses zones de sections différentes. La fonction d'échappement du fluide par le canal 25 est exactement la même que par l'orifice calibré 20.Fig. 8 shows a variant of the exhaust of the annular chamber 19. In this case, a channel 25 is formed axially in the distributor which opens into the crown 23 connecting its zones of different sections. The function of escaping the fluid through the channel 25 is exactly the same as through the calibrated orifice 20.

Selon une première possibilité représentée aux fig. 1 à 5 et 8, le clapet antiretour 22 est rappelé sur son siège, grâce à une chambre centrale 26 située sous la tête du clapet, qui est reliée par un canal 29 au réseau basse pression.According to a first possibility shown in FIGS. 1 to 5 and 8, the non-return valve 22 is returned to its seat, thanks to a central chamber 26 located under the head of the valve, which is connected by a channel 29 to the low pressure network.

Dans la forme d'exécution représentée à la fig. 9, le clapet antiretour 22 est rappelé sur son siège, grâce à une chambre annulaire 27 qui, résultant de la différence entre deux diamètres 28a et 28b, est reliée par un canal 29 au réseau basse pression.In the embodiment shown in FIG. 9, the non-return valve 22 is returned to its seat, thanks to an annular chamber 27 which, resulting from the difference between two diameters 28a and 28b, is connected by a channel 29 to the low pressure network.

Dans la forme d'exécution représentée à la fig. 10, le clapet 22 est maintenu en position fermée par la dépression existant entre le réseau haute pression 12 et la chambre 11 dès que le sens de circulation du fluide tend à s'inverser, du fait que la levée du clapet est limitée par une butée 30 à un jeu réduit J.In the embodiment shown in FIG. 10, the valve 22 is held in the closed position by the vacuum existing between the high pressure network 12 and the chamber 11 as soon as the direction of circulation of the fluid tends to reverse, because the valve lift is limited by a stop 30 to a reduced game J.

Dans la forme d'exécution représentée à la fig. 11, le clapet 22 est rappelé en position de fermeture par un ressort 32 prenant appui, d'une part, sur le clapet et, d'autre part, sur une butée 33 située du côté du réseau haute pression.In the embodiment shown in FIG. 11, the valve 22 is returned to the closed position by a spring 32 bearing, on the one hand, on the valve and, on the other hand, on a stop 33 located on the side of the high pressure network.

La fig. 12 du dessin représente une variante de réalisation de l'appareil des fig. 1 à 5, dans lequel le distributeur 10 n'est plus soumis à l'action d'un ressort 14, mais à l'action d'un piston plongeur central 34 à deux tiges opposées. Dans ce cas, il n'est pas possible de prévoir le dispositif de rappel de clapet représenté à la fig. 8, l'un quelconque de ceux représentés aux fig. 9 à 11 pouvant être envisagé.Fig. 12 of the drawing shows an alternative embodiment of the apparatus of FIGS. 1 to 5, in which the distributor 10 is no longer subjected to the action of a spring 14, but to the action of a central plunger 34 with two opposite rods. In this case, it is not possible to provide the valve return device shown in FIG. 8, any of those shown in FIGS. 9 to 11 can be considered.

Dans la forme d'exécution représentée aux fig. 14 et 15, le distributeur 10 présente une gorge 35 ménagée entre les parties cylindriques 16 et 17. Dans le corps du cylindre 4 est en outre ménagé au moins un canal 36 largement dimensionné qui, débouchant dans la cavité dans laquelle coulisse la partie cylindrique 16, communique avec la cavité 18. Le canal 36 est en outre positionné de manière à mettre en communication le volume annulaire ménagé par la gorge 35 avec le réseau basse pression, dès que la position du distributeur 10 assure la mise en communication de la chambre 11 avec le réseau basse pression. Cela permet une nouvelle accélération du mouvement du distributeur.In the embodiment shown in Figs. 14 and 15, the distributor 10 has a groove 35 formed between the cylindrical parts 16 and 17. In the body of the cylinder 4 is also formed at least one channel 36 which is broadly dimensioned and which, opening into the cavity in which the cylindrical part 16 slides , communicates with the cavity 18. The channel 36 is also positioned so as to put the annular volume formed by the groove 35 into communication with the low pressure network, as soon as the position of the distributor 10 ensures the communication of the chamber 11 with the low pressure network. This allows a further acceleration of the movement of the dispenser.

Dans la forme d'exécution représentée aux fig. 16 et 17, l'échappement de fluide hors de la chambre 18 est réalisé par un canal 25, comme dans le cas représenté à la fig. 8. Une gorge 37 est ménagée à la périphérie de la chambre 19, et un canal 38 est ménagé dans le distributeur, susceptible de mettre largement la chambre 19 en communication avec le réseau basse pression, dès que la position du distributeur 10 assure la mise en communication de la chambre 11 avec le réseau basse pression.In the embodiment shown in Figs. 16 and 17, the fluid escaping from the chamber 18 is produced by a channel 25, as in the case shown in FIG. 8. A groove 37 is formed at the periphery of the chamber 19, and a channel 38 is formed in the distributor, capable of placing the chamber 19 in broad communication with the low pressure network, as soon as the position of the distributor 10 ensures the setting in communication of chamber 11 with the low pressure network.

Comme il ressort de ce qui précède, l'invention apporte une grande amélioration à la technique existante en fournissant un appareil à percussions dont la structure n'est pas plus complexe que celle des appareils traditionnels, et qui possède des performances et une fiabilité bien supérieures à celles de ces derniers.As is apparent from the above, the invention brings a great improvement to the existing technique by providing a percussion device whose structure is not more complex than that of traditional devices, and which has much higher performance and reliability. to those of the latter.

Claims (8)

1. A percussion apparatus moved by a pressurised fluid, of the type comprising a mobile striking mass (2) in the form of a piston supplying a series of impacts on a tool (3), this piston being slidably mounted in a cylinder (4) which, provided in the body (5) of the apparatus and including ports (6, 7) connected by ducts (8, 9), serves additionally in the sliding of a distributor (10) connecting the chamber (11) situated above the piston alternately to a high pressure circuit (12), for enabling the piston to descend rapidly, and to a low pressure circuit (13) for effecting the return strocke of this piston, characterised in that it comprises, on the one hand, a non-return valve (22) enabling fluid to pass from the chamber (11) located above the strike piston towards the high pressure circuit (12) and, on the other hand, means ensuring that the distributor (10) is displaced sequentially in such a way that, starting from a position in which the chamber (11) located above the piston is connected to the high pressure (12), the distributor is displaced very rapidly as far as a position in which it interrupts the connection between the said chamber and the high pressure, then at a lower, controlled speed, so as to delay the connecting of the chamber (11) to the low pressure circuit (13), so as to enable the maximum amount of restorative energy to be recovered for the entire duration of the isolation of the chamber located above the piston with respect to the high pressure and low pressure circuits, by compressing the fluid isolated in the chamber for the passage of the latter into the high pressure circuit by means of the non-return valve.
2. A percussion apparatus as claimed in Claim 1, characterised in that the time for displacing the distributor (10) between the closure of the connection between the chamber (11) located above the piston and the high pressure circuit (12), and the connecting of this chamber (11) to the low pressure circuit (13), equals the time necessary for the greatest known rebound as a function of the hardest rocks.
3. A percussion apparatus as claimed in any one of Claims 1 or 2, characterised in that the distributor (10) undergoes a further acceleration movement as soon as the chamber (11) located above the piston is connected to the low pressure circuit (13) so as to disengage this aperture to a large extent and to enable mobile striking mass (2) to move freely.
4. A percussion apparatus as claimed in any one of Claims 1 to 3, characterised in that the distributor (10) comprises two parts having different sections, i.e. a part (16) located on the piston side, having a section corresponding to the section of the cylinder (4) in which the strike piston (2) is slidably mounted, and a part (17) of larger section located on the side opposite the piston, this part of larger section being mounted in a cavity (18) which, extending the cylinder, has a larger section than that of the large section part (17) of the distributor, this large section part of the distributor being able to penetrate into a chamber (19) having the same section as itself, arranged between the cylinder (4) and the enlarged cavity (19), penetration into this chamber (19) beginning when the distributor (10) arrives in a position in which it closes the connection between the chamber (11) located above the piston and the high pressure circuit (12), the annular volume delimited by the chamber (19) having an intermediate section and by the connection between the two sections of the distributor, being connected by at least one passage (20) to the chamber (11) located above the piston.
5. A percussion apparatus as claimed in Claim 4, characterised in that the passage (20) enabling fluid to escape from the annular chamber (19) is provided in the wall limiting the latter externally.
6. A percussion apparatus as claimed in all of Claims 3 to 5, characterised in that the distributor (10) has a groove (35) provided between the two cylindrical parts (16) and (17) having different sections, and in that at least one duct (36) opens into the cylinder (4), capable of connecting the annular volume delimited by the groove (35) to the low pressure circuit, as soon as the position of the distributor (10) ensures that the chamber (11) located above the piston is connected to the low pressure circuit.
7. A percussion apparatus as claimed in Claim 4, characterised in that a duct (25) is provided axially in the distributor (10), the end of which, opening into the collar (23) connecting the areas of the distributor with different sections, forms the calibrated aperture ensuring that fluid escapes from the annular chamber.
8. A percussion apparatus as claimed in all of Claims 3, 4 and 7, characterised in that the chamber (19), in which the fluid is compressed during the movement of the distributor, has a peripheral groove (37) which can be connected to the low pressure circuit by a duct (38) provided in the distributor, as soon as the position of the latter ensures that the chamber (11) located above the piston is connected to the low pressure circuit.
EP82420091A 1981-07-10 1982-07-06 Hydraulic percussion device Expired EP0070246B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82420091T ATE9071T1 (en) 1981-07-10 1982-07-06 HYDRAULIC IMPACT DEVICE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8114043A FR2509217A1 (en) 1981-07-10 1981-07-10 MU-PERCUSSION APPARATUS USING PRESSURIZED FLUID
FR8114043 1981-07-10

Publications (2)

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EP0070246A1 EP0070246A1 (en) 1983-01-19
EP0070246B1 true EP0070246B1 (en) 1984-08-22

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EP (1) EP0070246B1 (en)
JP (1) JPS5912428B2 (en)
AT (1) ATE9071T1 (en)
AU (1) AU540338B2 (en)
BR (1) BR8203985A (en)
CA (1) CA1205353A (en)
DE (2) DE3260607D1 (en)
ES (1) ES8304466A1 (en)
FI (1) FI78857C (en)
FR (1) FR2509217A1 (en)
NO (1) NO151109C (en)
ZA (1) ZA824781B (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2141657A (en) * 1983-05-10 1985-01-03 Panther Equip Ltd Improvements in hydraulically operated hammers
FR2550983A1 (en) * 1983-08-25 1985-03-01 Montabert Ets HYDRAULIC PERCUSSION APPARATUS
DE3443542A1 (en) * 1984-11-29 1986-06-05 Fried. Krupp Gmbh, 4300 Essen HYDRAULIC BEATER
FR2595972B2 (en) * 1985-07-16 1989-10-20 Montabert Ets PERCUSSION APPARATUS
FR2602448B1 (en) * 1986-08-07 1988-10-21 Montabert Ets METHOD FOR REGULATING THE PERCUSSION PARAMETERS OF THE STRIKE PISTON OF AN APPARATUS MOVED BY AN INCOMPRESSIBLE PRESSURE FLUID, AND APPARATUS FOR CARRYING OUT SAID METHOD
FR2618092B1 (en) * 1987-07-17 1989-11-10 Montabert Ets HYDRAULIC DISTRIBUTOR FOR A PERCUSSION APPARATUS MOUSED BY AN INCOMPRESSIBLE PRESSURE FLUID
DE68928143T2 (en) * 1989-10-18 1997-12-11 Mauro Vitulano Process for the automatic adjustment of the functional parameters of an impact device
SG43961A1 (en) * 1992-01-21 1997-11-14 Bsp Int Foundation Valve mechanism
IT1312140B1 (en) * 1999-06-22 2002-04-09 Priver Ind Srl PERCUSSION HYDRAULIC MACHINE OF INNOVATIVE CONCEPTION WORKING WITH CONSTANT HYDRAULIC PRESSURE.
CN110107220B (en) * 2019-05-05 2020-12-04 三峡大学 Percussion device and rock drilling equipment

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
FR1431835A (en) * 1965-01-28 1966-03-18 Montabert Ets Percussion device
CA941264A (en) * 1970-04-03 1974-02-05 Etablissements Montabert Dispositif de commande du distributeur d'un appareil a percussions mu par un liquide sous pression
US3991655A (en) * 1974-11-11 1976-11-16 Hydroacoustics Inc. Hydroacoustic apparatus and valving mechanisms for use therein
FI751895A (en) * 1975-06-26 1976-12-27 Xandor Ag
FI56430C (en) * 1975-10-20 1982-08-09 Tampella Oy Ab SLAGANORDNING DRIVEN AV EN TRYCKVAETSKA
FR2369908A1 (en) * 1976-11-08 1978-06-02 Montabert Roger HYDRAULIC PERCUSSION DEVICE
SU945412A2 (en) * 1978-12-27 1982-07-23 Ордена Трудового Красного Знамени институт гидродинамики СО АН СССР Percussive device

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Publication number Publication date
FI78857C (en) 1989-10-10
FR2509217B1 (en) 1984-08-10
NO151109C (en) 1985-02-13
FI78857B (en) 1989-06-30
DE70246T1 (en) 1983-05-11
ES513330A0 (en) 1983-03-16
JPS5871081A (en) 1983-04-27
FR2509217A1 (en) 1983-01-14
BR8203985A (en) 1983-07-05
CA1205353A (en) 1986-06-03
ATE9071T1 (en) 1984-09-15
FI822439L (en) 1983-01-11
DE3260607D1 (en) 1984-09-27
EP0070246A1 (en) 1983-01-19
ZA824781B (en) 1983-04-27
AU540338B2 (en) 1984-11-15
JPS5912428B2 (en) 1984-03-23
NO151109B (en) 1984-11-05
ES8304466A1 (en) 1983-03-16
NO822392L (en) 1983-01-11
FI822439A0 (en) 1982-07-08
AU8577882A (en) 1983-01-13

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