EP0516561B1 - Hydraulic impact apparatus - Google Patents

Hydraulic impact apparatus Download PDF

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Publication number
EP0516561B1
EP0516561B1 EP92420165A EP92420165A EP0516561B1 EP 0516561 B1 EP0516561 B1 EP 0516561B1 EP 92420165 A EP92420165 A EP 92420165A EP 92420165 A EP92420165 A EP 92420165A EP 0516561 B1 EP0516561 B1 EP 0516561B1
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EP
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Prior art keywords
piston
chamber
pressure
high pressure
circuit
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EP92420165A
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German (de)
French (fr)
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EP0516561A1 (en
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Bernard Piras
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Montabert SAS
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Montabert SAS
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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
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator

Definitions

  • the present invention relates to a hydraulic percussion device, and more specifically a hydraulic hammer of simple design intended to be easily adapted to various load-bearing vehicles, having energy sources of different powers.
  • this device must generate a low recoil force during the strike stroke of the piston in order to limit the vibrations transmitted to the carrier equipment, while providing constant energy and a high strike frequency to ensure good production.
  • the choice of the striking frequency as a function of the input flow rate determines the quantity of pressurized oil available for an operating cycle
  • the admissible recoil effort determines the maximum pressure that can be applied to the section driving force of the impact piston
  • the energy per stroke equal to the kinetic energy stored by the piston at the time of impact determines the stroke of the piston.
  • the stress in the steel of the impact piston and of the tool is proportional to the impact speed of the piston.
  • the admissible fatigue stress being known, the force applied to the driving section and the kinetic energy being defined, it is easy to calculate the necessary strike stroke, it being specified that this stroke must be sufficient to ensure the various switching operations necessary for operation of the distribution.
  • the quantity of oil under pressure available for a cycle must be used not only for the accelerated stroke of the striking piston but also for the return stroke of the latter, the distribution of this quantity of oil appreciably influencing the overall yield of the 'apparatus.
  • a simple solution consists in producing a striking piston mounted to slide in a cylinder with two spans and defining with the latter only two distinct chambers, an upper chamber of large section and an annular opposing chamber of small section.
  • a known hydraulic operating system consists in constantly supplying the annular chamber with pressurized fluid and alternately connecting the upper chamber to the source of pressurized fluid and then to a low pressure, so that the result of the forces applied to the piston is oriented alternately one way then another.
  • the document EP-A-0 085 279 which constitutes a state of the art corresponding to the preamble of claim 1 appended, relates to a percussion device comprising a striking piston hydraulically driven alternately by an incompressible fluid inside the cylinder, and striking a tool, the piston having at least three cylindrical and successive ranges of different sections, of which that situated on the side of the tool is less than that furthest from the tool, the piston and the cylinder delimiting the minus two opposing chambers: a lower annular chamber and an upper chamber of larger section.
  • the annular lower chamber is alternately connected by a distributor to the high pressure supply circuit during the piston raising phase and to the low pressure return circuit during the accelerated piston lowering phase, according to an alternative embodiment, or is constantly connected to the high pressure supply circuit, while the upper chamber of larger section is alternately connected by a distributor to the high pressure supply circuit during the accelerated descent phase of the piston and to the low pressure return circuit during the ascent phase of the piston according to another variant.
  • the calculated necessary input flow is more than twice the available flow.
  • the energy required for the return stroke of the piston is greater than that supplied during the accelerated stroke, which leads to an overall efficiency much less than 0.5.
  • the present invention aims to remedy these drawbacks.
  • the percussion device which it concerns, comprising a striking piston hydraulically driven alternately by an incompressible fluid inside a cylinder, and coming into contact with a tool, of the type in which the piston slides in a cylinder and has two concentric piston seats of different sections, one of which, located on the side of the tool, is of smaller section than that furthest from the tool, the piston and the cylinder delimiting two opposing chambers, one chamber lower annular and an upper chamber of larger section, is characterized in that it comprises pressure regulating means for permanently establishing a regulated pressure of intermediate value between the inlet or high pressure and outlet or low pressures pressure, inside the upper chamber (3) and the annular lower chamber during the accelerated lowering stroke of the piston, and inside of the upper chamber during the upward stroke of the piston when the annular chamber is subjected to supply pressure or high pressure, a distributor ensuring the communication of the annular chamber alternately with the high pressure supply circuit, during the piston raising phase, and with the upper chamber, during the accelerated piston lowering phase.
  • the means for regulating the intermediate pressure consist, on the one hand, of an energy accumulator and, on the other hand, of a pressure regulator comprising a cylinder with l inside of which is mounted a piston forming a drawer, one end of which delimits a chamber connected continuously or discontinuously to high pressure and the other end of which is situated in a chamber connected continuously or discontinuously to intermediate pressure and containing a spring tending to move the drawer towards its other end, the chamber connected to the intermediate pressure communicating by a throttle located on the circulation of the fluid with a throttle located on the circulation of the fluid with a median chamber which, connected to the low pressure return circuit, is obtained by a reduction in section of the drawer.
  • the chamber of the pressure regulator connected to the high pressure is in communication with an annular chamber formed in the cylinder in which the striking piston moves and which is permanently connected to the source of high-pressure fluid.
  • the pressure regulator chamber connectable to the high pressure is in communication with the lower annular chamber which is itself connected to the high pressure during the piston raising phase.
  • the movement of the striking piston is controlled by a hydraulic distributor slidingly mounted in a cylinder, with which it delimits four separate chambers, that is to say two chambers situated at the two ends of the distributor, connected by a wide channel and in permanent communication with the intermediate pressure circuit, a first annular chamber constantly connected to the high pressure circuit and a second annular chamber, antagonistic to the previous one and whose active section is greater than that of the above, connected alternately to the high pressure circuit and the intermediate pressure circuit, depending on the position of the impact piston.
  • the dispenser is annular and has a large central channel connecting the opposing chambers arranged at its ends, and the dispenser is arranged coaxially with the striking piston, in the same cylinder as the latter, and above it.
  • Figures 1 to 12 show, several embodiments of a percussion device operating according to the same principle, comprising a piston 1 sliding in a body 2.
  • the piston 1 defines with its cylinder a driving chamber 3, located above piston 1, and an annular chamber 7 antagonistic to chamber 3, the cross-sectional area of which is small.
  • the reciprocating movement of the piston is obtained by communication of the chamber 7, alternately with a high pressure supply circuit 4 and the driving chamber 3, so that the result of the hydraulic forces is exerted successively in one direction and in the 'other.
  • This communication of the chamber 7, alternately with the high and the medium pressure or intermediate pressure is carried out by a distributor 6, according to hydraulic means described below.
  • the striking piston 1 is driven in a downward movement when the chamber 7 is connected to the motor chamber 3, and in an upward movement when the chamber 7 is connected to the high pressure circuit.
  • the choice of the surfaces of the sections of the chambers 3 and 7 is such that during the ascent phase of the piston 1, the medium pressure created in the chamber 3 is at least slightly greater than the maximum pressure of the return line 8.
  • the medium pressure is an internal pressure, created by the circulation of the quantity of oil to be evacuated per cycle coming from the chamber 7, through a medium pressure regulator 9.
  • the quantity of high pressure oil used to fill the chamber 7 during the ascent of the piston is then evacuated towards the motor chamber 3 at medium pressure during the descent of the latter, then finally evacuated to the return circuit 8 by l 'Intermediate pressure regulator 9.
  • the latter maintains the average pressure at the predetermined value.
  • a hydropneumatic accumulator 11 of volume related to the quantity of oil under medium pressure necessary for the descent of the piston 1, is constantly connected to the medium pressure circuit 3, 5, 12. Its role is to accumulate energy during the ascent of the striking piston 1, and return it to carry out the accelerated descent of piston 1.
  • the function of the distributor 6 is shown schematically; depending on its position, either the chamber 7 is connected to the medium pressure circuit 3, 5, and the high pressure circuit 4 is isolated, the result of the forces applied to the impact piston is such that the latter descends, or the chamber 7 is connected to the high pressure circuit 4 and isolated from the medium pressure circuit 3, 5, the result of the forces applied to the impact piston is then such that the latter rises.
  • the distributor 6 is annular and arranged in the working cylinder, coaxial with the striking piston 1, and above the latter, delimits with the working cylinder four chambers 3, 12, 13, 14.
  • the chamber 3 and the chamber 12 are connected to each other by a wide channel 15, formed in the body of the distributor 6, and are constantly subjected to medium pressure.
  • the annular chamber 13 is constantly connected to the high pressure circuit 4 via a channel 16.
  • the chamber 14, the surface of the section 17 of which is greater than that of the chamber 13, is called the control chamber, and is antagonistic to rooms 12 and 13.
  • This control chamber 14 is alternately subjected to high pressure, then to medium pressure as a function of the position of the striking piston 1, so that the result of the forces applied to the distributor, is successively in one direction then in the other.
  • the distribution assembly is equipped with hydraulic means which make the distributor "bi-stable". This function is provided by known means such as calibrated orifices, provided in the bodies of the dispenser and of the device.
  • the choice of the surfaces of the sections of the chambers 3, 12, 13, 14 is such that, when the control chamber 14 is brought to the high supply pressure of the apparatus, the distributor 6 assumes the position of FIG. 4 and then puts the medium pressure circuit made up of the accumulator 11, the chambers 12 and 3 and the channels 5 and 15 into communication with the chamber 7, so as to accelerate the piston in its stroke. Conversely, when the control chamber 17 of the distributor is subjected at medium pressure, the distributor 6 occupies the position shown in FIG. 2, and connects the chamber 7 to the high pressure circuit, thereby allowing the striking piston 1 to rise.
  • the distributor 6 is driven in a downward movement when the control chamber 14 is connected to the medium pressure circuit, and in an upward movement when the latter communicates with the supply circuit 4.
  • the medium pressure regulating drawer 9 delimits with its working cylinder two opposing chambers 18 and 19, the first is constantly connected to the high pressure supply circuit by channel 20 or, according to a variant of the device, to the chamber 7.
  • the other chamber 19, which includes a spring, is continuously or discontinuously connected to the medium pressure circuit by the channel 5.
  • the regulating slide 9 furthermore comprises, in its central part, a groove 21, constantly connected to the return circuit 8 which, depending on the position of the slide, creates a constriction between the medium pressure circuit and the return circuit 8.
  • a hydropneumatic accumulator 10 of small volume is constantly connected to the high pressure circuit 4, in order to dampen the pressure fluctuations at the inlet of the device and thus save the pumps supply hydraulics.
  • the invention relates to a percussion device comprising a hydraulic device capable of sliding alternately and regularly, a striking piston stepped in a cylinder with two concentric spans.
  • the distribution assembly is also arranged, so as to make its operation independent of the pressure of the return circuit of the device.
  • FIG. 2 represents the position of the distributor 6 while the piston 1 rises.
  • the control chamber 14 is at this moment connected to the medium pressure circuit by a calibrated orifice 22, opening into a conduit 31, communicating with the motor chamber 3.
  • the upper edge 28 of the latter discovers the edge 29 of the groove 30 formed in the body of the device, and then puts in communication by a channel 31, the control chamber 14 and the medium pressure circuit via the chamber 3.
  • FIG. 5 represents a variant of the hydraulic device shown in FIGS. 2 to 4 in which the bore formed in the body of the device is separated by an annular wall 39 in two parts containing respectively the piston 1 and the distributor 6.
  • the end 37 of the distributor and the part 39 of the body of the apparatus delimit a chamber 40
  • the end 28 of the striking piston and the part 39 of the body of the apparatus delimit the driving chamber 3, the two chambers 3 and 40 being connected by a wide channel 41.
  • a groove 42 formed in the body of the device is constantly connected to the supply pressure by a channel 43.
  • a groove 44 is formed in the striking piston 1; its role is to allow a connection between the groove 30 and the groove 42.
  • FIG. 5 represents the position of the distributor 6 while the striking piston 1 rises.
  • the control chamber 14 is connected to the medium pressure circuit by the calibrated orifice 22.
  • the groove 25 of the distributor 6 connects the high pressure circuit 4 with the ascent chamber 7, by means of the circuit 27, 26, 25, 24 and 23 thus allowing the piston 1 to move up.
  • control chamber 14 is then connected to the high pressure circuit by a channel 31.
  • the quantity of oil under pressure, which can circulate through the calibrated orifice 22, is then insufficient to maintain the equilibrium pressure of the distributor. The result of the forces applied to the distributor reverses and the latter begins to rise.
  • the edge 45 of the groove 44 crosses the edge 46 of the groove 30 and thus closes the direct connection between the high pressure circuit 4, 43, 42, 44 and the control circuit 30, 31, 14.
  • the distributor 6 continues its climb stroke at reduced speed, as a function of the quantity of pressurized fluid which can circulate through the calibrated passage 34.
  • the upper edge 28 of the striking piston then discovers the edge 29 of the groove 30 (as shown in FIG. 6), and the operating cycle then becomes identical to that described in FIGS. 3 and 4.
  • FIG. 7 represents a variant of the hydraulic device described with reference to the preceding figures.
  • the chambers 40 and 3 are separate and connected by a wide channel 41.
  • a groove 51 formed in the body of the device and opening into the upper range of the striking piston, is constantly connected to a groove 47 formed in the body of the device, and opening into the lower reach of the distributor through a channel 48.
  • a groove 49 formed in the body of the distributor 6 makes it possible to relate the control chamber 14 and the groove 47 according to the position of the distributor.
  • channel 31 no longer opens directly into the control chamber 14, but into the intermediate range of the distributor 6.
  • a calibrated orifice 50 is formed in the body of the device, one of its ends is constantly in relation to the high pressure circuit 4; it has the same role as the calibrated passage 34 described in the previous figures.
  • FIG. 7 represents the position of the distributor 6 while the striking piston 1 rises.
  • the control chamber 14 is connected to the medium pressure circuit via the groove 49 and the calibrated orifice 22.
  • the groove 25 of the distributor 6 puts the high pressure circuit 4 into communication with the ascent chamber 7, by means of the circuit 27, 26, 25, 24 and 23, thus allowing the piston 1 to move up.
  • the control chamber 14 is then connected to the high pressure circuit 4 via the circuit 4, 27, 26, 25, 24, 23, 7, 51, 48, 47, 49.
  • the quantity of pressurized oil that can circulate through the calibrated orifice 22, is then insufficient to maintain distributor equilibrium pressure. The result of the forces applied to the distributor reverses and the latter begins to rise.
  • the upper edge 28 of the striking piston then discovers the edge 29 of the groove 30 (as shown in Figure 8).
  • the control chamber 14 is then connected to the medium pressure circuit by a wide channel 31.
  • the quantity of pressurized fluid, which can circulate through the calibrated orifice 50, is then insufficient to ensure the hydraulic balance of the distributor, the latter begins its downhill run.
  • the edge 54 of the groove 49 discovers the edge 55 of the groove 47, and simultaneously the other edge 56 of the groove 49 closes the calibrated orifice 50 and the channel 31, the channel 48 and the groove 51 being closed by the striking piston, the fluid contained in the control chamber 14 will then be discharged through the calibrated orifice 22, towards the medium pressure circuit.
  • the dispenser lowering speed is then regulated.
  • FIG. 9 represents a variant of the hydraulic device described in FIGS. 7 and 8.
  • the groove 26 formed in the body of the device and constantly connected to the high pressure circuit 4 no longer exists, as does the groove 25 formed in the body of the distributor 6.
  • All the other circuits remain identical to FIGS. 7 and 8 with the exception of channel 23 which is extended by a channel 57 which opens into the range of the distributor having the largest section.
  • the control chamber 14 is then connected to the medium pressure circuit by a channel 31.
  • the edge 54 of the groove 49 discovers the edge 55 of the groove 47, and simultaneously the other edge 56 of the groove 49 closes the calibrated orifice 50 and the channel 31, the channel 48 and the groove 51 being closed by the striking piston, the fluid contained in the control chamber 14 will then be discharged through the calibrated orifice 22, towards the medium pressure circuit.
  • the dispenser lowering speed is then regulated.
  • the edge 37 of the distributor 6 crosses the edge 38 of the groove 24 thus closing the connection between the ascent chamber 7 and the medium pressure circuit 3.
  • Figures 11 and 12 show a variant of the hydraulic device described in Figures 9 and 10.
  • the channel 5 is no longer constantly connected to the chamber 12 but to a groove 61 formed in the body of the device.
  • This groove 61 is positioned so that the edge 62 of the dispenser 6 which delimits one end of the chamber 12 discovers it during the downward movement of the dispenser and closes it during its upward movement.
  • the circulation of oil through the channel 5 towards the return circuit only takes place during the upward movement of the striking piston 1 (distributor 6 in the low position), during the descent of the piston 1 (distributor 6 in the high position), the quantity of pressurized oil returned by the accumulator 11 is entirely transferred to the driving chamber 3, the overall efficiency of the device is thus improved.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Fish Paste Products (AREA)
  • Consolidation Of Soil By Introduction Of Solidifying Substances Into Soil (AREA)
  • Earth Drilling (AREA)

Abstract

Apparatus comprising a striking piston (1) driven hydraulically in a reciprocating fashion by a non-compressible fluid inside a cylinder, and coming to strike a tool (60), of the type in which the piston slides in a cylinder comprising two concentric piston bearing surfaces of different cross-sections, of which the one situated on the tool side has a smaller cross-section than the one further away from the tool, the piston and the cylinder delimiting two opposing chambers, an annular lower chamber (7) and an upper chamber of larger cross-section. According to the invention, the inside of the upper chamber (3) is permanently at a regulated pressure, of intermediate value between the inlet or high pressure, and the outlet or low pressure, and the annular lower chamber (7) is alternately connected, via a directional control valve (6) to the high-pressure feed circuit during the phase in which the piston (1) rises, and to the upper chamber (3) during the accelerated descent phase of the piston (1). <IMAGE>

Description

La présente invention a pour objet un appareil hydraulique à percussions, et plus spécialement un marteau hydraulique de conception simple destiné à être facilement adapté à des engins porteurs divers, possèdant des sources d'énergie de différentes puissances.The present invention relates to a hydraulic percussion device, and more specifically a hydraulic hammer of simple design intended to be easily adapted to various load-bearing vehicles, having energy sources of different powers.

Compte tenu de son caractère polyvalent, un tel marteau doit pouvoir fonctionner sur une large plage de débits d'entrée tout en conservant un rendement supérieur à 0,5, le rendement étant le rapport entre la puissance fournie à l'outil et la puissance d'entrée. Cet appareil doit avoir un fonctionnement indépendant de la valeur de la pression de retour qui, selon les engins porteurs, peut varier dans de grandes proportions.Given its versatile nature, such a hammer must be able to operate over a wide range of input flow rates while maintaining a yield greater than 0.5, the yield being the ratio between the power supplied to the tool and the power d 'Entrance. This device must operate independently of the return pressure value, which, depending on the carrier, can vary widely.

Enfin, cet appareil doit générer une faible force de recul lors de la course de frappe du piston afin de limiter les vibrations transmises à l'équipement porteur, tout en fournissant une énergie constante et une fréquence de frappe élevée pour assurer une bonne production.Finally, this device must generate a low recoil force during the strike stroke of the piston in order to limit the vibrations transmitted to the carrier equipment, while providing constant energy and a high strike frequency to ensure good production.

A titre d'exemple, un marteau hydraulique, adaptable sur un engin de 0,8 à 3 tonnes doit pouvoir posséder les caractéristiques suivantes :

  • débit d'entrée de fluide hydraulique : de 20 à 45 litres/minute,
  • pression de la ligne retour : de 0 à 30 bars (1 bar = 10⁵ Pa),
  • effort de recul inférieur à 700 daN,
  • énergie par coup : 180 joules,
  • fréquence de frappe de 600 à 1 500 coups par minute,
  • diamètre de l'outil de l'ordre de 45 mm avec un diamètre minimum du piston de frappe de 40 mm.
For example, a hydraulic hammer, adaptable to a machine from 0.8 to 3 tonnes must be able to have the following characteristics:
  • hydraulic fluid inlet flow: from 20 to 45 liters / minute,
  • return line pressure: from 0 to 30 bars (1 bar = 10⁵ Pa),
  • recoil force less than 700 daN,
  • energy per stroke: 180 joules,
  • strike frequency from 600 to 1,500 strokes per minute,
  • diameter of the tool of the order of 45 mm with a minimum diameter of the impact piston of 40 mm.

Ces différents paramètres sont liés.These different parameters are linked.

En effet, le choix de la fréquence de frappe en fonction du débit d'entrée détermine la quantité d'huile sous pression disponible pour un cycle de fonctionnement, l'effort de recul admissible détermine la pression maximale qui peut s'appliquer sur la section motrice du piston de frappe, et l'énergie par coup égale à l'énergie cinétique emmagasinée par le piston au moment de l'impact détermine la course de frappe du piston.Indeed, the choice of the striking frequency as a function of the input flow rate determines the quantity of pressurized oil available for an operating cycle, the admissible recoil effort determines the maximum pressure that can be applied to the section driving force of the impact piston, and the energy per stroke equal to the kinetic energy stored by the piston at the time of impact determines the stroke of the piston.

En effet, la contrainte dans l'acier du piston de frappe et de l'outil est proportionnelle à la vitesse d'impact du piston. La contrainte de fatigue admissible étant connue, la force appliquée sur la section motrice et l'énergie cinétique étant définies, il est aisé de calculer la course de frappe nécessaire, étant précisé que cette course doit être suffisante pour assurer les différentes commutations nécessaires au fonctionnement de la distribution.Indeed, the stress in the steel of the impact piston and of the tool is proportional to the impact speed of the piston. The admissible fatigue stress being known, the force applied to the driving section and the kinetic energy being defined, it is easy to calculate the necessary strike stroke, it being specified that this stroke must be sufficient to ensure the various switching operations necessary for operation of the distribution.

Enfin, la quantité d'huile sous pression disponible pour un cycle doit servir non seulement à la course accélérée du piston de frappe mais aussi à la course retour de ce dernier, la répartition de cette quantité d'huile influençant sensiblement le rendement global de l'appareil.Finally, the quantity of oil under pressure available for a cycle must be used not only for the accelerated stroke of the striking piston but also for the return stroke of the latter, the distribution of this quantity of oil appreciably influencing the overall yield of the 'apparatus.

Une solution simple consiste à réaliser un piston de frappe monté coulissant dans un cylindre à deux portées et ne définissant avec ce dernier que deux chambres distinctes, une chambre supérieure de forte section et une chambre annulaire antagoniste de faible section. Un système de fonctionnement hydraulique connu consiste à alimenter constamment la chambre annulaire en fluide sous pression et à relier alternativement la chambre supérieure à la source de fluide sous pression puis à une basse pression, afin que la résultante des forces appliquées sur le piston soit orientée alternativement dans un sens puis dans un autre.A simple solution consists in producing a striking piston mounted to slide in a cylinder with two spans and defining with the latter only two distinct chambers, an upper chamber of large section and an annular opposing chamber of small section. A known hydraulic operating system consists in constantly supplying the annular chamber with pressurized fluid and alternately connecting the upper chamber to the source of pressurized fluid and then to a low pressure, so that the result of the forces applied to the piston is oriented alternately one way then another.

Le document EP-A-0 085 279, qui constitue un état de la technique correspondant au préambule de la revendication 1 annexée, concerne un appareil à percussions comportant un piston de frappe entraîné hydrauliquement de façon alternative par un fluide incompressible à l'intérieur du cylindre, et venant percuter un outil, le piston comportant au moins trois portées cylindriques et successives de sections différentes, dont celle située du côté de l'outil est inférieure à celle la plus éloignée de l'outil, le piston et le cylindre délimitant au moins deux chambres antagonistes : une chambre inférieure annulaire et une chambre supérieure de plus grande section. La chambre inférieure annulaire est reliée alternativement par un distributeur au circuit d'alimentation haute pression pendant la phase de montée du piston et au circuit retour basse pression pendant la phase de descente accélérée du piston, suivant une variante d'exécution, ou est reliée constamment au circuit d'alimentation haute pression, alors que la chambre supérieure de plus grande section est alternativement reliée par un distributeur au circuit d'alimentation haute pression pendant la phase de descente accélérée du piston et au circuit retour basse pression pendant la phase de montée du piston suivant une autre variante d'exécution.The document EP-A-0 085 279, which constitutes a state of the art corresponding to the preamble of claim 1 appended, relates to a percussion device comprising a striking piston hydraulically driven alternately by an incompressible fluid inside the cylinder, and striking a tool, the piston having at least three cylindrical and successive ranges of different sections, of which that situated on the side of the tool is less than that furthest from the tool, the piston and the cylinder delimiting the minus two opposing chambers: a lower annular chamber and an upper chamber of larger section. The annular lower chamber is alternately connected by a distributor to the high pressure supply circuit during the piston raising phase and to the low pressure return circuit during the accelerated piston lowering phase, according to an alternative embodiment, or is constantly connected to the high pressure supply circuit, while the upper chamber of larger section is alternately connected by a distributor to the high pressure supply circuit during the accelerated descent phase of the piston and to the low pressure return circuit during the ascent phase of the piston according to another variant.

Dans la mesure où l'on souhaite appliquer un tel système de fonctionnement hydraulique à un appareil comportant les caractéristiques définies précédemment, on obtient les valeurs suivantes :

  • pression motrice : 56 bars,
  • la pression d'entrée nécessaire étant de 56 bars et la pression maximale du circuit de retour étant de 30 bars, il est possible de calculer le diamètre minimum de la grande section du piston de frappe qui ressort à 59 mm,
  • l'énergie cinétique du piston de frappe étant égale à l'énergie hydraulique fournie lors de la course accélérée, il est possible de calculer la course du piston de frappe et la quantité d'huile nécessaire par coup, qui est de 70 cm³,
  • la fréquence de frappe prédéterminée permet de calculer le débit d'entrée nécessaire : 105 litres par minute.
Insofar as it is desired to apply such a hydraulic operating system to an apparatus comprising the characteristics defined above, the following values are obtained:
  • driving pressure: 56 bars,
  • the required inlet pressure being 56 bars and the maximum return circuit pressure being 30 bars, it is possible to calculate the minimum diameter of the large section of the striking piston which emerges at 59 mm,
  • the kinetic energy of the impact piston being equal to the hydraulic energy supplied during the accelerated stroke, it is possible to calculate the stroke of the impact piston and the quantity of oil required per stroke, which is 70 cm³,
  • the predetermined striking frequency allows the necessary input flow rate to be calculated: 105 liters per minute.

Or, le débit d'entrée nécessaire calculé est plus de deux fois supérieur au débit disponible. D'autre part, l'énergie nécessaire à la course retour du piston est supérieure à celle fournie lors de la course accélérée de frappe, ce qui conduit à un rendement global très inférieur à 0,5.However, the calculated necessary input flow is more than twice the available flow. On the other hand, the energy required for the return stroke of the piston is greater than that supplied during the accelerated stroke, which leads to an overall efficiency much less than 0.5.

Pour remédier à ces inconvénients, les constructeurs d'appareils à percussions ont cherché à utiliser des sections motrices de faible surface soumises à une pression motrice élevée. Il est ainsi possible de diminuer la quantité d'huile nécessaire pour un cycle tout en conservant l'énergie par coup sans affecter l'effort de recul et le rendement global. Toutefois, cette configuration impose de créer des pistons de frappe qui coulissent dans des cylindres à au moins trois portées afin de créer une section motrice annulaire. L'objectif de simplicité tant au plan de la structure qu'au plan de la commande hydraulique n'est alors plus rempli.To overcome these drawbacks, the manufacturers of percussion devices have sought to use drive sections of small area subjected to high drive pressure. It is thus possible to reduce the quantity of oil required for a cycle while conserving the energy per stroke without affecting the recoil effort and the overall yield. However, this configuration requires the creation of striking pistons which slide in cylinders with at least three spans in order to create an annular driving section. The objective of simplicity both in terms of structure and in terms of hydraulic control is no longer fulfilled.

La présente invention vise à remédier à ces inconvénients.The present invention aims to remedy these drawbacks.

A cet effet, l'appareil à percussions qu'elle concerne, comportant un piston de frappe entraîné hydrauliquement de façon alternative par un fluide incompressible à l'intérieur d'un cylindre, et venant percuter un outil, du type dans lequel le piston coulisse dans un cylindre et comporte deux portées de piston concentriques de sections différentes dont celle, située du côté de l'outil, est de section inférieure à celle le plus éloignée de l'outil, le piston et le cylindre délimitant deux chambres antagonistes, une chambre inférieure annulaire et une chambre supérieure de plus grande section, est caractérisé en ce qu'il comprend des moyens de régulation de pression pour établir en permanence, une pression régulée de valeur intermédiaire entre les pressions d'entrée ou haute pression et de sortie ou basse pression, à l'intérieur de la chambre supérieure (3) et de la chambre inférieure annulaire lors de la course de descente accélérée du piston, et à l'intérieur de la chambre supérieure lors de la course de montée du piston lorsque la chambre annulaire est soumise à la pression d'alimentation ou haute pression, un distributeur assurant la mise en communication de la chambre annulaire alternativement avec le circuit d'alimentation haute pression, pendant la phase de montée du piston, et avec la chambre supérieure, pendant la phase de descente accélérée du piston.To this end, the percussion device which it concerns, comprising a striking piston hydraulically driven alternately by an incompressible fluid inside a cylinder, and coming into contact with a tool, of the type in which the piston slides in a cylinder and has two concentric piston seats of different sections, one of which, located on the side of the tool, is of smaller section than that furthest from the tool, the piston and the cylinder delimiting two opposing chambers, one chamber lower annular and an upper chamber of larger section, is characterized in that it comprises pressure regulating means for permanently establishing a regulated pressure of intermediate value between the inlet or high pressure and outlet or low pressures pressure, inside the upper chamber (3) and the annular lower chamber during the accelerated lowering stroke of the piston, and inside of the upper chamber during the upward stroke of the piston when the annular chamber is subjected to supply pressure or high pressure, a distributor ensuring the communication of the annular chamber alternately with the high pressure supply circuit, during the piston raising phase, and with the upper chamber, during the accelerated piston lowering phase.

Il est ainsi possible d'avoir un effort de recul faible puisque la pression motrice est faible, d'accepter un débit d'entrée faible puisque la quantité d'huile sous pression d'entrée par cycle sert à alimenter une section annulaire de faible surface, d'avoir une course de frappe importante qui permet d'augmenter les longueurs d'étanchéité, d'obtenir un rendement global supérieur à 0,5, et d'avoir un fonctionnement indépendant de la pression du circuit de retour puisqu'aucune chambre n'est soumise a cette pression au cours du cycle.It is thus possible to have a low recoil effort since the driving pressure is low, to accept a low inlet flow rate since the quantity of oil under inlet pressure per cycle is used to feed an annular section of small area. , to have a large striking stroke which makes it possible to increase the sealing lengths, to obtain an overall efficiency greater than 0.5, and to have an operation independent of the pressure of the return circuit since no chamber is not subjected to this pressure during the cycle.

Selon une forme d'exécution avantageuse de cet appareil, les moyens de régulation de la pression intermédiaire sont constitués, d'une part, par un accumulateur d'énergie et, d'autre part, par un régulateur de pression comportant un cylindre à l'intérieur duquel est monté un piston formant tiroir dont une extrémité délimite une chambre reliée de manière continue ou discontinue à la haute pression et dont l'autre extrémité est située dans une chambre reliée de manière continue ou discontinue à la pression intermédiaire et contenant un ressort tendant à déplacer le tiroir vers son autre extrémité, la chambre reliée à la pression intermédiaire communiquant par un étranglement situé sur la circulation du fluide avec un étranglement situé sur la circulation de fluide avec une chambre médiane qui, reliée au circuit de retour basse pression, est obtenue par une diminution de section du tiroir.According to an advantageous embodiment of this device, the means for regulating the intermediate pressure consist, on the one hand, of an energy accumulator and, on the other hand, of a pressure regulator comprising a cylinder with l inside of which is mounted a piston forming a drawer, one end of which delimits a chamber connected continuously or discontinuously to high pressure and the other end of which is situated in a chamber connected continuously or discontinuously to intermediate pressure and containing a spring tending to move the drawer towards its other end, the chamber connected to the intermediate pressure communicating by a throttle located on the circulation of the fluid with a throttle located on the circulation of the fluid with a median chamber which, connected to the low pressure return circuit, is obtained by a reduction in section of the drawer.

Selon une possibilité, la chambre du régulateur de pression reliée à la haute pression est en communication avec une chambre annulaire ménagée dans le cylindre dans lequel se déplace le piston de frappe et qui est reliée en permanence à la source de fluide haute-pression.According to one possibility, the chamber of the pressure regulator connected to the high pressure is in communication with an annular chamber formed in the cylinder in which the striking piston moves and which is permanently connected to the source of high-pressure fluid.

Conformément à une autre possibilité, la chambre du régulateur de pression reliable à la haute pression est en communication avec la chambre annulaire inférieure qui est elle-même reliée à la haute pression pendant la phase de montée du piston.According to another possibility, the pressure regulator chamber connectable to the high pressure is in communication with the lower annular chamber which is itself connected to the high pressure during the piston raising phase.

Selon une autre caractéristique préférée de l'invention, le mouvement du piston de frappe est commandé par un distributeur hydraulique monté coulissant dans un cylindre, avec lequel il délimite quatre chambres distinctes, c'est-à-dire deux chambres situées aux deux extrémités du distributeur, reliées par un large canal et en communication permanente avec le circuit de pression intermédiaire, une première chambre annulaire reliée constamment au circuit à haute pression et une seconde chambre annulaire, antagoniste à la précédente et dont la section active est supérieure à celle de la précédente, reliée alternativement au circuit haute pression et au circuit de pression intermédiaire, en fonction de la position du piston de frappe.According to another preferred characteristic of the invention, the movement of the striking piston is controlled by a hydraulic distributor slidingly mounted in a cylinder, with which it delimits four separate chambers, that is to say two chambers situated at the two ends of the distributor, connected by a wide channel and in permanent communication with the intermediate pressure circuit, a first annular chamber constantly connected to the high pressure circuit and a second annular chamber, antagonistic to the previous one and whose active section is greater than that of the above, connected alternately to the high pressure circuit and the intermediate pressure circuit, depending on the position of the impact piston.

Avantageusement, le distributeur est annulaire et comporte un large canal central mettant en communication les chambres antagonistes disposées a ses extrémités, et le distributeur est disposé coaxialement au piston de frappe, dans le même cylindre que celui-ci, et au-dessus de lui.Advantageously, the dispenser is annular and has a large central channel connecting the opposing chambers arranged at its ends, and the dispenser is arranged coaxially with the striking piston, in the same cylinder as the latter, and above it.

De toute façon, l'invention sera bien comprise à l'aide de la description qui suit, en référence aux dessins schématiques annexés représentant, à titre d'exemples non limitatifs, plusieurs formes d'exécution de cet appareil :

  • Figure 1 est une vue très schématique de principe de l'appareil selon l'invention ;
  • Figures 2 à 4 sont trois vues en coupe longitudinale d'un appareil équipé d'un premier ensemble mobile piston de frappe, distributeur, tiroir de régulation de pression ;
  • Figures 5 à 6 sont deux vues en coupe longitudinale d'une variante de l'appareil de figure 1 à 3.
  • Figures 7 à 8 sont deux vues en coupe longitudinale d'une variante de l'appareil de figures 1 à 3 ;
  • Figures 9 et 10 sont deux vues en coupe longitudinale d'une variante de l'appareil de figures 7 et 8 ;
  • Figures 11 et 12 sont deux vues en coupe longitudinale d'une variante de l'appareil de figures 9 et 10.
In any case, the invention will be clearly understood with the aid of the description which follows, with reference to the appended schematic drawings showing, by way of nonlimiting examples, several embodiments of this device:
  • Figure 1 is a very schematic principle view of the apparatus according to the invention;
  • Figures 2 to 4 are three views in longitudinal section of an apparatus equipped with a first movable assembly striking piston, distributor, pressure regulation drawer;
  • Figures 5 to 6 are two views in longitudinal section of a variant of the device of figure 1 to 3.
  • Figures 7 to 8 are two views in longitudinal section of a variant of the apparatus of Figures 1 to 3;
  • Figures 9 and 10 are two views in longitudinal section of a variant of the apparatus of Figures 7 and 8;
  • Figures 11 and 12 are two views in longitudinal section of a variant of the apparatus of Figures 9 and 10.

Les figures 1 à 12 repésentent, plusieurs formes d'exécution d'un appareil à percussions fonctionnant suivant le même principe, comportant un piston 1 coulissant dans un corps 2. Le piston 1 délimite avec son cylindre une chambre motrice 3, située au-dessus du piston 1, et une chambre annulaire 7 antagoniste à la chambre 3 dont la surface de la section est faible. Le mouvement alternatif du piston est obtenu par communication de la chambre 7, alternativement avec un circuit d'alimentation en haute pression 4 et la chambre motrice 3, de telle sorte que la résultante des forces hydrauliques s'exerce successivement dans un sens et dans l'autre. Cette mise en communication de la chambre 7, alternativement avec la haute et la moyenne pression ou pression intermédiaire, est réalisée par un distributeur 6, selon des moyens hydrauliques décrits plus loin.Figures 1 to 12 show, several embodiments of a percussion device operating according to the same principle, comprising a piston 1 sliding in a body 2. The piston 1 defines with its cylinder a driving chamber 3, located above piston 1, and an annular chamber 7 antagonistic to chamber 3, the cross-sectional area of which is small. The reciprocating movement of the piston is obtained by communication of the chamber 7, alternately with a high pressure supply circuit 4 and the driving chamber 3, so that the result of the hydraulic forces is exerted successively in one direction and in the 'other. This communication of the chamber 7, alternately with the high and the medium pressure or intermediate pressure, is carried out by a distributor 6, according to hydraulic means described below.

Dans toutes les formes d'exécution, le piston de frappe 1 est animé d'un mouvement de descente lorsque la chambre 7 est reliée à la chambre motrice 3, et à un mouvement de montée lorsque la chambre 7 est reliée au circuit haute pression.In all embodiments, the striking piston 1 is driven in a downward movement when the chamber 7 is connected to the motor chamber 3, and in an upward movement when the chamber 7 is connected to the high pressure circuit.

Le choix des surfaces des sections des chambres 3 et 7 est tel qu'au cours de la phase de montée du piston 1, la moyenne pression créée dans la chambre 3 soit au moins légèrement supérieure à la pression maximale de la ligne retour 8.The choice of the surfaces of the sections of the chambers 3 and 7 is such that during the ascent phase of the piston 1, the medium pressure created in the chamber 3 is at least slightly greater than the maximum pressure of the return line 8.

La moyenne pression est une pression interne, créée par la circulation de la quantité d'huile à évacuer par cycle provenant de la chambre 7, à travers un régulateur de pression moyenne 9.The medium pressure is an internal pressure, created by the circulation of the quantity of oil to be evacuated per cycle coming from the chamber 7, through a medium pressure regulator 9.

En pratique, la quantité d'huile haute pression utilisée pour remplir la chambre 7 lors de la remontée du piston, est ensuite évacuée vers la chambre motrice 3 moyenne pression pendant la descente de ce dernier, puis enfin évacuée vers le circuit retour 8 par l'intermédiaire du régulateur de pression 9. Ce dernier maintient la moyenne pression à la valeur prédéterminée.In practice, the quantity of high pressure oil used to fill the chamber 7 during the ascent of the piston, is then evacuated towards the motor chamber 3 at medium pressure during the descent of the latter, then finally evacuated to the return circuit 8 by l 'Intermediate pressure regulator 9. The latter maintains the average pressure at the predetermined value.

Un accumulateur hydropneumatique 11 de volume en rapport avec la quantité d'huile sous moyenne pression nécessaire à la descente du piston 1, est constamment relié au circuit moyenne pression 3, 5, 12. Il a pour rôle d'accumuler l'énergie lors de la remontée du piston de frappe 1, et de la restituer pour réaliser la descente accélérée du piston 1.A hydropneumatic accumulator 11 of volume related to the quantity of oil under medium pressure necessary for the descent of the piston 1, is constantly connected to the medium pressure circuit 3, 5, 12. Its role is to accumulate energy during the ascent of the striking piston 1, and return it to carry out the accelerated descent of piston 1.

Dans la forme d'exécution représentée à la figure 1, la fonction du distributeur 6 est schématisée ; suivant sa position, soit la chambre 7 est reliée au circuit moyenne pression 3, 5, et le circuit haute pression 4 est isolé, la résultante des forces appliquées au piston de frappe est telle que ce dernier descend, soit la chambre 7 est reliée au circuit haute pression 4 et isolée du circuit moyenne pression 3, 5, la résultante des forces appliquées au piston de frappe est alors telle que ce dernier remonte.In the embodiment shown in Figure 1, the function of the distributor 6 is shown schematically; depending on its position, either the chamber 7 is connected to the medium pressure circuit 3, 5, and the high pressure circuit 4 is isolated, the result of the forces applied to the impact piston is such that the latter descends, or the chamber 7 is connected to the high pressure circuit 4 and isolated from the medium pressure circuit 3, 5, the result of the forces applied to the impact piston is then such that the latter rises.

Dans les formes d'exécution représentées aux figures 2 à 12, le distributeur 6 est annulaire et disposé dans le cylindre de travail, coaxialement au piston de frappe 1, et au-dessus de celui-ci, délimite avec le cylindre de travail quatre chambres 3, 12, 13, 14.In the embodiments shown in Figures 2 to 12, the distributor 6 is annular and arranged in the working cylinder, coaxial with the striking piston 1, and above the latter, delimits with the working cylinder four chambers 3, 12, 13, 14.

La chambre 3 et la chambre 12 sont reliées entre elles par un large canal 15, ménagé dans le corps du distributeur 6, et sont constamment soumises à la moyenne pression. La chambre 13 annulaire est constamment reliée au circuit haute pression 4 par l'intermédiaire d'un canal 16. Enfin, la chambre 14 dont la surface de la section 17 est supérieure à celle de la chambre 13, est appelée chambre de commande, et est antagoniste aux chambres 12 et 13.The chamber 3 and the chamber 12 are connected to each other by a wide channel 15, formed in the body of the distributor 6, and are constantly subjected to medium pressure. The annular chamber 13 is constantly connected to the high pressure circuit 4 via a channel 16. Finally, the chamber 14, the surface of the section 17 of which is greater than that of the chamber 13, is called the control chamber, and is antagonistic to rooms 12 and 13.

Cette chambre de commande 14 est alternativement soumise à la haute pression, puis à la moyenne pression en fonction de la position du piston de frappe 1, de telle sorte que la résultante des forces appliquées au distributeur, soit successivement dans un sens puis dans l'autre. Afin d'assurer la régularité des cycles, l'ensemble de distribution est équipé de moyens hydrauliques qui rendent le distributeur "bi-stable". Cette fonction est assurée par des moyens connus tels que des orifices calibrés, ménagés dans les corps du distributeur et de l'appareil.This control chamber 14 is alternately subjected to high pressure, then to medium pressure as a function of the position of the striking piston 1, so that the result of the forces applied to the distributor, is successively in one direction then in the other. In order to ensure the regularity of the cycles, the distribution assembly is equipped with hydraulic means which make the distributor "bi-stable". This function is provided by known means such as calibrated orifices, provided in the bodies of the dispenser and of the device.

Le choix des surfaces des sections des chambres 3, 12, 13, 14 est tel que, lorsque la chambre de commande 14 est mise à la haute pression d'alimentation de l'appareil, le distributeur 6 prend la position de la figure 4 et met alors en communication le circuit moyenne pression constitué de l'accumulateur 11, des chambres 12 et 3 et des canaux 5 et 15 avec la chambre 7, de façon à accélérer le piston dans sa course de frappe. Inversement, lorsque la chambre de commande 17 du distributeur est soumise a la moyenne pression, le distributeur 6 vient occuper la position représentée a la figure 2, et relie la chambre 7 au circuit haute pression en permettant ainsi la remontée du piston de frappe 1.The choice of the surfaces of the sections of the chambers 3, 12, 13, 14 is such that, when the control chamber 14 is brought to the high supply pressure of the apparatus, the distributor 6 assumes the position of FIG. 4 and then puts the medium pressure circuit made up of the accumulator 11, the chambers 12 and 3 and the channels 5 and 15 into communication with the chamber 7, so as to accelerate the piston in its stroke. Conversely, when the control chamber 17 of the distributor is subjected at medium pressure, the distributor 6 occupies the position shown in FIG. 2, and connects the chamber 7 to the high pressure circuit, thereby allowing the striking piston 1 to rise.

A titre d'exemple non limitatif et pour la suite de la description, il est admis que le distributeur 6 est animé d'un mouvement de descente lorsque la chambre de commande 14 est reliée au circuit moyenne pression, et d'un mouvement de montée lorsque cette dernière communique avec le circuit d'alimentation 4.By way of nonlimiting example and for the following description, it is accepted that the distributor 6 is driven in a downward movement when the control chamber 14 is connected to the medium pressure circuit, and in an upward movement when the latter communicates with the supply circuit 4.

Le tiroir de régulation de moyenne pression 9 délimite avec son cylindre de travail deux chambres antagonistes 18 et 19, la première est constamment reliée au circuit d'alimentation haute pression par le canal 20 ou, selon une variante de l'appareil, à la chambre de remontée 7. L'autre chambre 19, qui comprend un ressort, est de manière continue ou discontinue reliée au circuit moyenne pression par le canal 5. Le tiroir de régulation 9 comprend par ailleurs, dans sa partie centrale, une gorge 21, constamment reliée au circuit retour 8 qui permet, suivant la position du tiroir, de créer un étranglement entre le circuit moyenne pression et le circuit retour 8.The medium pressure regulating drawer 9 delimits with its working cylinder two opposing chambers 18 and 19, the first is constantly connected to the high pressure supply circuit by channel 20 or, according to a variant of the device, to the chamber 7. The other chamber 19, which includes a spring, is continuously or discontinuously connected to the medium pressure circuit by the channel 5. The regulating slide 9 furthermore comprises, in its central part, a groove 21, constantly connected to the return circuit 8 which, depending on the position of the slide, creates a constriction between the medium pressure circuit and the return circuit 8.

Dans les formes d'exécution représentées aux figures 2 à 10, un accumulateur hydropneumatique 10 de faible volume est constamment relié au circuit haute pression 4, afin d'amortir les fluctuations de pression à l'entrée de l'appareil et ainsi ménager les pompes hydrauliques d'alimentation.In the embodiments shown in FIGS. 2 to 10, a hydropneumatic accumulator 10 of small volume is constantly connected to the high pressure circuit 4, in order to dampen the pressure fluctuations at the inlet of the device and thus save the pumps supply hydraulics.

L'invention concerne un appareil à percussions comportant un dispositif hydraulique capable de faire coulisser alternativement et régulièrement, un piston de frappe étagé dans un cylindre à deux portées concentriques. L'ensemble de distribution est d'autre part agencé, de manière à rendre son fonctionnement indépendant de la pression du circuit retour de l'appareil.The invention relates to a percussion device comprising a hydraulic device capable of sliding alternately and regularly, a striking piston stepped in a cylinder with two concentric spans. The distribution assembly is also arranged, so as to make its operation independent of the pressure of the return circuit of the device.

Le fonctionnement de ce dispositif est le suivant :
   La figure 2 représente la position du distributeur 6 alors que le piston 1 monte.The operation of this device is as follows:
FIG. 2 represents the position of the distributor 6 while the piston 1 rises.

La chambre de commande 14 est à ce moment, reliée au circuit moyenne pression par un orifice calibré 22, débouchant dans un conduit 31, communiquant avec la chambre motrice 3.The control chamber 14 is at this moment connected to the medium pressure circuit by a calibrated orifice 22, opening into a conduit 31, communicating with the motor chamber 3.

Le distributeur 6, à cet instant, met en communication la chambre de remontée 7 avec le circuit haute pression 4, par l'intermédiaire du canal 23, de la gorge 24 ménagée dans le corps de l'appareil, de la gorge 25 ménagée dans le corps du distributeur, de la gorge 26 ménagée dans le corps de l'appareil et enfin, du canal 27 en permettant ainsi la course de montée du piston 1.The distributor 6, at this instant, puts the ascent chamber 7 into communication with the high pressure circuit 4, via the channel 23, the groove 24 formed in the body of the device, the groove 25 formed in the body of the distributor, of the groove 26 formed in the body of the device and finally, of the channel 27, thus allowing the upward stroke of the piston 1.

Au cours de sa montée, l'arête supérieure 28 du piston délimitant une extrémité de la chambre 3, croise l'arête supérieure 29 d'une gorge 30 ménagée dans le corps de l'appareil. Cette dernière gorge est constamment reliée à la chambre 14 par le canal 31.During its rise, the upper edge 28 of the piston delimiting one end of the chamber 3 crosses the upper edge 29 of a groove 30 formed in the body of the device. This last groove is constantly connected to the chamber 14 by the channel 31.

Lorsque le piston 1 rejoint le distributeur 6 au cours de sa montée, il entraîne ce dernier dans sa course, comme montré à la figure 3.When the piston 1 joins the distributor 6 during its rise, it drives the latter in its stroke, as shown in FIG. 3.

Au cours du mouvement du distributeur, successivement :

  • L'arête supérieure 32 de la chambre de commande 14 obture l'orifice calibré 22 du distributeur 6, et simultanément l'arête 33 de la chambre de commande 14 découvre le passage calibré 34, en permettant une alimentation contrôlée en fluide sous pression de la chambre 14 à partir de la gorge 26 reliée au canal 27.
  • L'arête supérieure 35 de la gorge 24, croise l'arête 36 de la gorge 25 du distributeur 6, la liaison entre circuit haute pression 4 et chambre de remontée 7 est alors obturée Le piston de frappe 1 ralentit sa course et se sépare du distributeur 6.
  • L'arête inférieure 37 du distributeur délimitant une extrémité de la chambre 3, croise l'arête inférieure 38 de la gorge 24. Dès cet instant la chambre de remontée 7 est mise en communication avec le circuit moyenne pression, par l'intermédiaire du canal 23, de la gorge 24 et de la chambre 3. La résultante des forces appliquées au piston de frappe s'inverse, et ce dernier commence sa course de frappe accélérée. Le distributeur 6 continue sa course de montée à vitesse réduite, en fonction de la quantité de fluide sous pression qui peut circuler à travers le passage calibré 34.
During the movement of the distributor, successively:
  • The upper edge 32 of the control chamber 14 closes the calibrated orifice 22 of the distributor 6, and simultaneously the edge 33 of the control chamber 14 discovers the calibrated passage 34, allowing controlled supply of fluid under pressure from the chamber 14 from the groove 26 connected to the channel 27.
  • The upper edge 35 of the groove 24 crosses the edge 36 of the groove 25 of the distributor 6, the connection between the high pressure circuit 4 and the ascent chamber 7 is then closed. The striking piston 1 slows down its stroke and separates from the distributor 6.
  • The lower edge 37 of the distributor delimiting one end of the chamber 3 crosses the lower edge 38 of the groove 24. From this moment the ascent chamber 7 is placed in communication with the medium pressure circuit, via the channel 23, the groove 24 and the chamber 3. The result of the forces applied to the striking piston reverses, and the latter begins its accelerated striking stroke. The distributor 6 continues its climb stroke at reduced speed, as a function of the quantity of pressurized fluid which can circulate through the calibrated passage 34.

Au cours de la descente du piston de frappe, comme représenté à la figure 4, l'arête supérieure 28 de ce dernier découvre l'arête 29 de la gorge 30 ménagée dans le corps de l'appareil, et met alors en communication par un canal 31, la chambre de commande 14 et le circuit moyenne pression par l'intermédiaire de la chambre 3.During the descent of the striking piston, as shown in Figure 4, the upper edge 28 of the latter discovers the edge 29 of the groove 30 formed in the body of the device, and then puts in communication by a channel 31, the control chamber 14 and the medium pressure circuit via the chamber 3.

La quantité de fluide sous pression pouvant circuler à travers le passage calibré 34, est alors insuffisante pour créer la pression nécessaire à l'équilibre du distributeur 6. La résultante des forces appliquées au distributeur 6 s'inverse et ce dernier amorce sa course de descente.The amount of pressurized fluid that can circulate through the calibrated passage 34 is then insufficient to create the pressure necessary for equilibrium of the distributor 6. The result of the forces applied to the distributor 6 is reversed and the latter begins its downward stroke .

Peu après le choc du piston 1 sur l'outil 60 et alors que le distributeur 6 descend, successivement :

  • L'arête 37 du distributeur 6 croise l'arête inférieure 38 de la gorge 24, et obture ainsi la liaison entre la chambre 7 et le circuit moyenne pression.
  • L'arête 36 de la gorge 25 du distributeur 6 découvre l'arête supérieure 35 de la gorge 24 : une liaison est alors établie entre circuit haute pression 4 et chambre de remontée 7, par l'intermédiaire du circuit 27, 26, 25, 24 et 23. La résultante des forces appliquées au piston de frappe 1 s'inverse et celui-ci amorce sa course de remontée.
  • L'arête 33 déterminant une des extrémités de la chambre 14, obture l'extrémité du passage calibré 34, et simultanément l'arête 32 délimitant l'autre extrémité de la gorge 14 découvre l'orifice calibré 22. Le distributeur 6 termine sa course de descente, le fluide déplacé dans la chambre 14 pouvant s'évacuer soit par le canal 31 et la gorge 30, soit par l'orifice calibré 22.
Shortly after the impact of the piston 1 on the tool 60 and while the distributor 6 descends, successively:
  • The edge 37 of the distributor 6 crosses the lower edge 38 of the groove 24, and thus closes the connection between the chamber 7 and the medium pressure circuit.
  • The edge 36 of the groove 25 of the distributor 6 discovers the upper edge 35 of the groove 24: a connection is then established between the high pressure circuit 4 and the ascent chamber 7, via the circuit 27, 26, 25, 24 and 23. The result of the forces applied to the striking piston 1 reverses and the latter begins its ascent stroke.
  • The edge 33 determining one of the ends of the chamber 14, closes the end of the calibrated passage 34, and simultaneously the edge 32 delimiting the other end of the groove 14 discovers the calibrated orifice 22. The distributor 6 ends its stroke lowering, the fluid displaced in the chamber 14 being able to be evacuated either by the channel 31 and the groove 30, or by the calibrated orifice 22.

Le cycle de fonctionnement continue comme décrit précédemment.The operating cycle continues as described above.

La figure 5 représente une variante du dispositif hydraulique représenté aux figures 2 à 4 dans laquelle l'alésage ménagé dans le corps de l'appareil est séparé par une paroi annulaire 39 en deux parties contenant respectivement le piston 1 et le distributeur 6. Dans ce cas, l'extrémité 37 du distributeur et la partie 39 du corps de l'appareil délimitent une chambre 40, l'extrémité 28 du piston de frappe et la partie 39 du corps de l'appareil délimitent la chambre motrice 3, les deux chambres 3 et 40 étant reliées par un large canal 41. Une gorge 42 ménagée dans le corps de l'appareil est constamment reliée à la pression d'alimentation par un canal 43. Une gorge 44 est ménagée dans le piston de frappe 1 ; elle a pour rôle de permettre une liaison entre la gorge 30 et la gorge 42.FIG. 5 represents a variant of the hydraulic device shown in FIGS. 2 to 4 in which the bore formed in the body of the device is separated by an annular wall 39 in two parts containing respectively the piston 1 and the distributor 6. In this In this case, the end 37 of the distributor and the part 39 of the body of the apparatus delimit a chamber 40, the end 28 of the striking piston and the part 39 of the body of the apparatus delimit the driving chamber 3, the two chambers 3 and 40 being connected by a wide channel 41. A groove 42 formed in the body of the device is constantly connected to the supply pressure by a channel 43. A groove 44 is formed in the striking piston 1; its role is to allow a connection between the groove 30 and the groove 42.

Le fonctionnement de l'appareil est le suivant :
   La figure 5 représente la position du distributeur 6 alors que le piston de frappe 1 remonte.The operation of the device is as follows:
FIG. 5 represents the position of the distributor 6 while the striking piston 1 rises.

La chambre de commande 14 est reliée au circuit moyenne pression par l'orifice calibré 22.The control chamber 14 is connected to the medium pressure circuit by the calibrated orifice 22.

La gorge 25 du distributeur 6 met en relation le circuit haute pression 4 avec la chambre de remontée 7, par l'intermédiaire du circuit 27, 26, 25, 24 et 23 permettant ainsi le mouvement de montée du piston 1.The groove 25 of the distributor 6 connects the high pressure circuit 4 with the ascent chamber 7, by means of the circuit 27, 26, 25, 24 and 23 thus allowing the piston 1 to move up.

Dès que l'arête 45 de la gorge 44 ménagée dans le corps du piston 1, découvre l'arête 46 délimitant l'extrémité inférieure de la gorge 30, la chambre de commande 14 est alors reliée au circuit haute pression par un canal 31. La quantité d'huile sous pression, pouvant circuler à travers l'orifice calibré 22, est alors insuffisante pour maintenir la pression d'équilibre du distributeur. La résultante des forces appliquées au distributeur s'inverse et ce dernier amorce sa montée.As soon as the edge 45 of the groove 44 formed in the body of the piston 1, uncovers the edge 46 delimiting the lower end of the groove 30, the control chamber 14 is then connected to the high pressure circuit by a channel 31. The quantity of oil under pressure, which can circulate through the calibrated orifice 22, is then insufficient to maintain the equilibrium pressure of the distributor. The result of the forces applied to the distributor reverses and the latter begins to rise.

Au cours de son mouvement, successivement :

  • L'arête 32 de la chambre de commande 14 obture l'orifice calibré 22, simultanément l'arête 33 de la même chambre 14 découvre le passage calibré 34.
  • L'arête 35 de la gorge 24 croise l'arête 36 de la gorge 25 du distributeur 6, la liaison entre circuit haute pression 4 et chambre de remontée 7 est alors obturée.
  • L'arête 37 à l'extrémité du distributeur 6 découvre l'arête 38 de la gorge 24. Dès cet instant, la chambre de remontée 7 est mise en communication avec le circuit moyenne pression 40, 41, 3, par l'intermédiaire de la gorge 24 et du canal 23. La résultante des forces appliquées au piston de frappe s'inverse et ce dernier commence sa course de frappe accélérée.
During its movement, successively:
  • The edge 32 of the control chamber 14 closes the calibrated orifice 22, simultaneously the edge 33 of the same chamber 14 discovers the calibrated passage 34.
  • The edge 35 of the groove 24 crosses the edge 36 of the groove 25 of the distributor 6, the connection between the high pressure circuit 4 and the ascent chamber 7 is then closed.
  • The edge 37 at the end of the distributor 6 discovers the edge 38 of the groove 24. From this instant, the ascent chamber 7 is placed in communication with the medium pressure circuit 40, 41, 3, by means of the groove 24 and the channel 23. The result of the forces applied to the striking piston reverses and the latter begins its accelerated striking stroke.

Au cours de sa descente, l'arête 45 de la gorge 44 croise l'arête 46 de la gorge 30 et obture ainsi la liaison directe entre circuit haute pression 4, 43, 42, 44 et circuit de commande 30, 31, 14. Le distributeur 6 continue sa course de montée à vitesse réduite, en fonction de la quantité de fluide sous pression qui peut circuler à travers le passage calibré 34.During its descent, the edge 45 of the groove 44 crosses the edge 46 of the groove 30 and thus closes the direct connection between the high pressure circuit 4, 43, 42, 44 and the control circuit 30, 31, 14. The distributor 6 continues its climb stroke at reduced speed, as a function of the quantity of pressurized fluid which can circulate through the calibrated passage 34.

L'arête supérieure 28 du piston de frappe découvre ensuite l'arête 29 de la gorge 30 (comme représenté figure 6), et le cycle de fonctionnement devient alors identique à celui décrit aux figures 3 et 4.The upper edge 28 of the striking piston then discovers the edge 29 of the groove 30 (as shown in FIG. 6), and the operating cycle then becomes identical to that described in FIGS. 3 and 4.

La figure 7 représente une variante du dispositif hydraulique décrit en référence aux figures précédentes. Comme dans le dispositif décrit aux figures 5 et 6, les chambres 40 et 3 sont distinctes et reliées par un large canal 41. Une gorge 51 ménagée dans le corps de l'appareil et débouchant dans la portée supérieure du piston de frappe, est constamment reliée à une gorge 47 ménagée dans le corps de l'appareil, et débouchant dans la portée inférieure du distributeur par un canal 48.FIG. 7 represents a variant of the hydraulic device described with reference to the preceding figures. As in the device described in Figures 5 and 6, the chambers 40 and 3 are separate and connected by a wide channel 41. A groove 51 formed in the body of the device and opening into the upper range of the striking piston, is constantly connected to a groove 47 formed in the body of the device, and opening into the lower reach of the distributor through a channel 48.

Une gorge 49 ménagée dans le corps du distributeur 6, permet de mettre en relation la chambre de commande 14 et la gorge 47 suivant la position du distributeur.A groove 49 formed in the body of the distributor 6 makes it possible to relate the control chamber 14 and the groove 47 according to the position of the distributor.

Enfin le canal 31 ne débouche plus directement dans la chambre de commande 14, mais dans la portée intermédiaire du distributeur 6.Finally, the channel 31 no longer opens directly into the control chamber 14, but into the intermediate range of the distributor 6.

Un orifice calibré 50 est ménagé dans le corps de l'appareil, une de ses extrémités est constamment en relation avec le circuit haute pression 4 ; il a le même rôle que le passage calibré 34 décrit aux figures précédentes.A calibrated orifice 50 is formed in the body of the device, one of its ends is constantly in relation to the high pressure circuit 4; it has the same role as the calibrated passage 34 described in the previous figures.

Le fonctionnement de l'appareil est le suivant :
   La figure 7 représente la position du distributeur 6 alors que le piston de frappe 1 remonte.The operation of the device is as follows:
FIG. 7 represents the position of the distributor 6 while the striking piston 1 rises.

La chambre de commande 14 est reliée au circuit moyenne pression par l'intermédiaire de la gorge 49 et de l'orifice calibré 22.The control chamber 14 is connected to the medium pressure circuit via the groove 49 and the calibrated orifice 22.

La gorge 25 du distributeur 6, met en communication le circuit haute pression 4 avec la chambre de remontée 7, par l'intermédiaire du circuit 27, 26, 25, 24 et 23 permettant ainsi le mouvement de montée du piston 1.The groove 25 of the distributor 6 puts the high pressure circuit 4 into communication with the ascent chamber 7, by means of the circuit 27, 26, 25, 24 and 23, thus allowing the piston 1 to move up.

Dès que l'arête 52 du piston de frappe 1, délimitant une extrémité de la chambre annulaire 7, découvre l'arête 53, délimitant l'extrémité inférieure de la gorge 51, la chambre de commande 14 est alors reliée au circuit haute pression 4 par l'intermédiaire du circuit 4, 27, 26, 25, 24, 23, 7, 51, 48, 47, 49. La quantité d'huile sous pression pouvant circuler à travers l'orifice calibré 22, est alors insuffisante pour maintenir la pression d'équilibre du distributeur. La résultante des forces appliquées au distributeur s'inverse et ce dernier amorce sa montée.As soon as the edge 52 of the striking piston 1, delimiting one end of the annular chamber 7, discovers the edge 53, delimiting the lower end of the groove 51, the control chamber 14 is then connected to the high pressure circuit 4 via the circuit 4, 27, 26, 25, 24, 23, 7, 51, 48, 47, 49. The quantity of pressurized oil that can circulate through the calibrated orifice 22, is then insufficient to maintain distributor equilibrium pressure. The result of the forces applied to the distributor reverses and the latter begins to rise.

Au cours de son mouvement, successivement :

  • L'arête inférieure 54 délimitant une extrémité de la gorge 49, croise l'arête 55 délimitant l'extrémité supérieure de la gorge 47, et simultanément l'autre extrémité 56 de la gorge 49 découvre le canal 31 et l'orifice calibré 50, permettant ainsi l'alimentation régulée en fluide sous pression de la chambre de commande 14. (La gorge 30 et le canal 31 sont à ce moment du cycle, obturés par le piston de frappe 1).
  • L'arête 35 de la gorge 24 croise l'arête 36 de la gorge 25 du distributeur 6, la liaison entre circuit haute pression 4 et chambre de remontée 7 est alors obturée.
  • L'arête 37 délimitant l'extrémité inférieure du distributeur 6, découvre l'arête 38 de la gorge 24. Dès cet instant, la chambre de remontée 7 est mise en communication avec le circuit moyenne pression 40, 41, 3, par l'intermédiaire de la gorge 24 et du canal 23. La résultante des forces appliquées au piston de frappe s'inverse et ce dernier débute sa course de frappe accélérée. Le distributeur 6 termine sa course de montée.
During its movement, successively:
  • The lower edge 54 delimiting one end of the groove 49 crosses the edge 55 delimiting the upper end of the groove 47, and simultaneously the other end 56 of the groove 49 discovers the channel 31 and the calibrated orifice 50, thus allowing the regulated supply of pressurized fluid to the control chamber 14. (The groove 30 and the channel 31 are at this point in the cycle, closed by the striking piston 1).
  • The edge 35 of the groove 24 crosses the edge 36 of the groove 25 of the distributor 6, the connection between the high pressure circuit 4 and the ascent chamber 7 is then closed.
  • The edge 37 delimiting the lower end of the distributor 6, uncovers the edge 38 of the groove 24. From this moment, the ascent chamber 7 is placed in communication with the medium pressure circuit 40, 41, 3, by the intermediate the groove 24 and the channel 23. The result of the forces applied to the striking piston reverses and the latter begins its accelerated striking stroke. The distributor 6 ends its climb stroke.

Au cours de sa descente, l'arête 52 du piston 1 croise l'arête 53 et obture ainsi la liaison entre la chambre de remontée 7 et la gorge 47.During its descent, the edge 52 of the piston 1 crosses the edge 53 and thus closes the connection between the ascent chamber 7 and the groove 47.

L'arête supérieure 28 du piston de frappe, découvre ensuite l'arête 29 de la gorge 30 (comme représenté figure 8). La chambre de commande 14 se trouve alors reliée au circuit moyenne pression par un large canal 31. La quantité de fluide sous pression, pouvant circuler à travers l'orifice calibré 50, est alors insuffisante pour assurer l'équilibre hydraulique du distributeur, ce dernier commence sa course de descente.The upper edge 28 of the striking piston, then discovers the edge 29 of the groove 30 (as shown in Figure 8). The control chamber 14 is then connected to the medium pressure circuit by a wide channel 31. The quantity of pressurized fluid, which can circulate through the calibrated orifice 50, is then insufficient to ensure the hydraulic balance of the distributor, the latter begins its downhill run.

Au cours du mouvement de descente du distributeur 6, l'arête 54 de la gorge 49 découvre l'arête 55 de la gorge 47, et simultanément l'autre arête 56 de la gorge 49 obture l'orifice calibré 50 et le canal 31, le canal 48 et la gorge 51 étant obturés par le piston de frappe, le fluide contenu dans la chambre de commande 14 va alors être évacué par l'orifice calibré 22, vers le circuit moyenne pression. La vitesse de descente du distributeur est alors régulée.During the downward movement of the distributor 6, the edge 54 of the groove 49 discovers the edge 55 of the groove 47, and simultaneously the other edge 56 of the groove 49 closes the calibrated orifice 50 and the channel 31, the channel 48 and the groove 51 being closed by the striking piston, the fluid contained in the control chamber 14 will then be discharged through the calibrated orifice 22, towards the medium pressure circuit. The dispenser lowering speed is then regulated.

A partir de cet instant, la fin du cycle de fonctionnement devient identique à celui décrit en référence aux figures 2 à 3.From this moment, the end of the operating cycle becomes identical to that described with reference to Figures 2 to 3.

La figure 9 représente une variante du dispositif hydraulique décrit aux figures 7 et 8. Dans cette configuration, la gorge 26 ménagée dans le corps de l'appareil et constamment reliée au circuit haute pression 4 n'existe plus, de même que la gorge 25 ménagée dans le corps du distributeur 6. Tous les autres circuits restent identiques aux figures 7 et 8 à l'exception du canal 23 qui est prolongé par un canal 57 qui débouche dans la portée du distributeur ayant la plus grande section.FIG. 9 represents a variant of the hydraulic device described in FIGS. 7 and 8. In this configuration, the groove 26 formed in the body of the device and constantly connected to the high pressure circuit 4 no longer exists, as does the groove 25 formed in the body of the distributor 6. All the other circuits remain identical to FIGS. 7 and 8 with the exception of channel 23 which is extended by a channel 57 which opens into the range of the distributor having the largest section.

Le fonctionnement de l'appareil est le suivant :

  • La figure 9 représente la position du distributeur 6 alors que le piston de frappe 1 remonte.
  • La chambre de commande 14 est reliée au circuit moyenne pression par l'intermédiaire de la gorge 49 et de l'orifice calibré 22.
  • L'arête 58 délimitant une extrémité de la chambre 13 découvre le canal 57 et met ainsi en communication le circuit haute pression 4 avec la chambre de remontée 7, par l'intermédiaire du circuit 16, 13, 57 et 23 permettant ainsi le mouvement de montée du piston 1.
  • Dès que l'arête 52 du piston de frappe 1, délimitant une extrémité de la chambre annulaire 7, découvre l'arête 53, délimitant l'extrémité inférieure de la gorge 51, la chambre de commande 14 est alors reliée au circuit haute pression 4 par l'intermédiaire du circuit 16, 13, 57, 23, 7, 51, 48, 47, 49. La quantité d'huile sous pression pouvant circuler à travers l'orifice calibré 22 est alors insuffisante pour maintenir la pression d'équilibre du distributeur. La résultante des forces appliquées au distributeur 6 s'inverse et ce dernier amorce sa montée.
The operation of the device is as follows:
  • FIG. 9 represents the position of the distributor 6 while the striking piston 1 rises.
  • The control chamber 14 is connected to the medium pressure circuit via the groove 49 and the calibrated orifice 22.
  • The edge 58 delimiting one end of the chamber 13 uncovers the channel 57 and thus puts the high pressure circuit 4 into communication with the ascent chamber 7, by means of the circuit 16, 13, 57 and 23 thus allowing the movement of piston rise 1.
  • As soon as the edge 52 of the striking piston 1, delimiting one end of the annular chamber 7, discovers the edge 53, delimiting the lower end of the groove 51, the control chamber 14 is then connected to the high pressure circuit 4 via the circuit 16, 13, 57, 23, 7, 51, 48, 47, 49. The quantity of pressurized oil which can circulate through the calibrated orifice 22 is then insufficient to maintain the pressure distributor balance. The result of the forces applied to the distributor 6 is reversed and the latter begins its rise.

Au cours de son mouvement, successivement :

  • L'arête inférieure 54 délimitant une extrémité de la gorge 49 croise l'arête 55 délimitant l'extrémité supérieure de la gorge 47, et simultanément l'autre extrémité 56 de la gorge 49 découvre le canal 31 et l'orifice calibré 50, permettant ainsi l'alimentation régulée en fluide sous pression de la chambre de commande 14. (la gorge 30 et le canal 31 sont à ce moment du cycle, obturés par le piston de frappe 1).
  • L'arête 58 obture le canal 57 interrompant ainsi la liaison entre circuit haute pression 4 et chambre de remontée 7.
  • L'arête 37 délimitant l'extrémité inférieure du distributeur 6, découvre l'arête 38 de la gorge 24. Dès cet instant, la chambre de remontée 7 est mise en communication avec le circuit moyenne pression 40, 41, 3, par l'intermédiaire de la gorge 24 et du canal 23. La résultante des forces appliquées au piston de frappe s'inverse et ce dernier débute sa course de frappe accélérée. Le distributeur 6 termine sa course de montée.
During its movement, successively:
  • The lower edge 54 delimiting one end of the groove 49 crosses the edge 55 delimiting the upper end of the groove 47, and simultaneously the other end 56 of the groove 49 discovers the channel 31 and the calibrated orifice 50, allowing thus the regulated supply of pressurized fluid to the control chamber 14. (the groove 30 and the channel 31 are at this point in the cycle, closed by the striking piston 1).
  • The edge 58 closes the channel 57 thus interrupting the connection between the high pressure circuit 4 and the ascent chamber 7.
  • The edge 37 delimiting the lower end of the distributor 6, uncovers the edge 38 of the groove 24. From this moment, the ascent chamber 7 is placed in communication with the medium pressure circuit 40, 41, 3, by the intermediate the groove 24 and the channel 23. The result of the forces applied to the striking piston reverses and the latter begins its accelerated striking stroke. The distributor 6 ends its climb stroke.

Au cours de sa descente, l'arête 52 du piston 1 croise l'arête 53 et obture ainsi la liaison entre la chambre de remontée 7 et la gorge 47.During its descent, the edge 52 of the piston 1 crosses the edge 53 and thus closes the connection between the ascent chamber 7 and the groove 47.

L'arête supérieure 28 du piston de frappe 1, découvre ensuite l'arête 29 de la gorge 30 (comme représenté figure 10). La chambre de commande 14 se trouve alors reliée au circuit moyenne pression par un canal 31.The upper edge 28 of the striking piston 1, then discovers the edge 29 of the groove 30 (as shown in Figure 10). The control chamber 14 is then connected to the medium pressure circuit by a channel 31.

La quantité de fluide sous pression, pouvant circuler à travers l'orifice calibré 50, est alors insuffisante pour assurer l'équilibre hydraulique du distributeur, ce dernier commence sa course de descente.The quantity of fluid under pressure, which can circulate through the calibrated orifice 50, is then insufficient to ensure the hydraulic balance of the distributor, the latter begins its downward stroke.

Au cours du mouvement de descente du distributeur 6, l'arête 54 de la gorge 49 découvre l'arête 55 de la gorge 47, et simultanément l'autre arête 56 de la gorge 49 obture l'orifice calibré 50 et le canal 31, le canal 48 et la gorge 51 étant obturés par le piston de frappe, le fluide contenu dans la chambre de commande 14 va alors être évacué par l'orifice calibré 22, vers le circuit moyenne pression. La vitesse de descente du distributeur est alors régulée.During the downward movement of the distributor 6, the edge 54 of the groove 49 discovers the edge 55 of the groove 47, and simultaneously the other edge 56 of the groove 49 closes the calibrated orifice 50 and the channel 31, the channel 48 and the groove 51 being closed by the striking piston, the fluid contained in the control chamber 14 will then be discharged through the calibrated orifice 22, towards the medium pressure circuit. The dispenser lowering speed is then regulated.

L'arête 37 du distributeur 6 croise l'arête 38 de la gorge 24 obturant ainsi la liaison entre chambre de remontée 7 et circuit moyenne pression 3.The edge 37 of the distributor 6 crosses the edge 38 of the groove 24 thus closing the connection between the ascent chamber 7 and the medium pressure circuit 3.

Peu après l'arête 58 déterminant une extrémité de la chambre 13 découvre le canal 57 et crée alors une liaison entre circuit haute pression 4 et chambre de remontée 7. La résultante des forces appliquées au piston de frappe 1 s'inverse et celui-ci amorce sa course de remontée.Shortly after the edge 58 determining one end of the chamber 13 discovers the channel 57 and then creates a connection between the high pressure circuit 4 and the ascent chamber 7. The result of the forces applied to the piston of hits 1 reverses and it starts its ascent stroke.

Le cycle de fonctionnement continue comme décrit précédemment.The operating cycle continues as described above.

Les figures 11 et 12 représentent une variante du dispositif hydraulique décrit aux figures 9 et 10. Dans cette configuration le canal 5 n'est plus constamment relié à la chambre 12 mais à une gorge 61 ménagée dans le corps de l'appareil. Cette gorge 61 est positionnée de manière à ce que l'arête 62 du distributeur 6 qui délimite une extrémité de la chambre 12 la découvre lors du mouvement de descente du distributeur et l'obture lors de son mouvement de montée. Ainsi, la circulation d'huile à travers le canal 5 vers le circuit retour ne s'effectue plus que lors du mouvement de montée du piston de frappe 1 (distributeur 6 en position basse), lors de la descente du piston 1 (distributeur 6 en position haute), la quantité d'huile sous pression restituée par l'accumulateur 11 est entièrement transférée vers la chambre motrice 3, le rendement global de l'appareil est ainsi amélioré.Figures 11 and 12 show a variant of the hydraulic device described in Figures 9 and 10. In this configuration the channel 5 is no longer constantly connected to the chamber 12 but to a groove 61 formed in the body of the device. This groove 61 is positioned so that the edge 62 of the dispenser 6 which delimits one end of the chamber 12 discovers it during the downward movement of the dispenser and closes it during its upward movement. Thus, the circulation of oil through the channel 5 towards the return circuit only takes place during the upward movement of the striking piston 1 (distributor 6 in the low position), during the descent of the piston 1 (distributor 6 in the high position), the quantity of pressurized oil returned by the accumulator 11 is entirely transferred to the driving chamber 3, the overall efficiency of the device is thus improved.

Claims (11)

  1. Impact apparatus comprising a striking piston (1) hydraulically driven in a reciprocating manner by an incompressible fluid inside a cylinder and striking a tool (60), of the type in which the piston slides in a cylinder and comprises two concentric piston bearing surfaces of different cross sections of which that which is situated at the tool end is of a smaller cross section than that which is more distant from the tool, the piston and the cylinder delimiting two opposing chambers, a lower annular chamber (7) and an upper chamber of larger cross section, is characterised in that it includes pressure regulating means for permanently establishing a regulated pressure of a value intermediate between the input pressure or high pressure and the output or low pressure, inside the upper chamber (3) and the lower annular chamber (7) during the accelerated descending stroke of the piston, and inside the upper chamber (3) during the ascending stroke of the piston when the annular chamber (7) is subject to the feed pressure or high pressure, a directional control valve (6) ensuring connection of the annular chamber (7) alternately to the high pressure feed circuit during the ascending phase of the piston, and to the upper chamber (3) during the accelerated descent phase of the piston (1).
  2. Impact apparatus according to Claim 1, characterised in that the means for regulating the intermediate pressure are constituted on the one hand by an energy accumulator and, on the other hand, by a pressure regulator comprising a cylinder inside which is mounted a piston (9) forming a slide valve of which one end delimits a chamber (18) linked in a continuous or non-continuous manner to the high pressure and whose other end is located in a chamber (19) linked in a continuous or non-continuous manner to the intermediate pressure and containing a spring which tends to displace the slide valve towards its other end, the chamber (19) linked to the intermediate pressure communicating through a constriction situated in the fluid circuit with a medial chamber (21) which, linked to the low pressure return circuit (8), is obtained by a reduction of the slide valve cross section.
  3. Impact apparatus according to Claim 2, characterised in that the pressure regulator chamber (18) which is linked to the high pressure is connected to an annular chamber (26) housed in the cylinder in which the striking piston (1) moves and which is linked permanently to the high pressure fluid source.
  4. Impact apparatus according to Claim 2, characterised in that the pressure regulator chamber (18) which may be linked to the high pressure is connected to the lower annular chamber (7) which is itself linked to the high pressure during the ascending phase of the piston.
  5. Impact apparatus according to one of the Claims 1 to 4, characterised in that the movement of the striking piston is controlled by a hydraulic directional control valve (6) slidably mounted in a cylinder, with which it delimits four distinct chambers, that is to say two chambers (3, 12) situated at the two ends of the directional control valve, linked by a wide channel (15) and in permanent communication with the intermediate pressure circuit, a first annular chamber (13) continuously linked to the high pressure circuit and a second annular chamber (14), opposing the previous chamber and whose active cross section is greater than that of the previous chamber, alternately linked to the high pressure circuit and to the intermediate pressure circuit according to the position of the striking piston.
  6. Impact apparatus according to Claim 5, characterised in that the directional control valve (6) is annular and comprises a wide central channel (15) which connects the opposing chambers (3,12) arranged at its ends to one another.
  7. Impact apparatus according to Claim 6, characterised in that the directional control valve (6) is arranged coaxial to the striking piston (1), in the same cylinder as it and above it.
  8. Impact apparatus according to Claim 7, characterised in that the directional control valve (6) comprises an annular groove (25) intended, in one position of the directional control valve, to connect grooves housed in the body of the apparatus and linked respectively to the source of high pressure fluid (4) and to the lower annular chamber (7).
  9. Impact apparatus according to one of the Claims 6 and 7, characterised in that the cylinder in which are mounted the striking piston (1) and the directional control valve (6) is separated into two compartments by an annular partition (39).
  10. Impact apparatus according to one of the Claims 1 to 9, characterised in that the feed circuit for the high pressure fluid is equipped with a hydropneumatic accumulator (10) of low volume intended for damping the pressure fluctuations in the apparatus input.
  11. Impact apparatus according to Claim 2, characterised in that the upper chamber (12) is linked to the pressure regulator by a channel (5) opening out into a groove (61) housed in the body of the apparatus in a zone covered up by the directional control valve (6) during the period of the descent of the striking piston (1) and uncovered during the period of the ascent of the striking piston.
EP92420165A 1991-05-30 1992-05-20 Hydraulic impact apparatus Expired - Lifetime EP0516561B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9106693 1991-05-30
FR9106693A FR2676953B1 (en) 1991-05-30 1991-05-30 HYDRAULIC PERCUSSION APPARATUS.

Publications (2)

Publication Number Publication Date
EP0516561A1 EP0516561A1 (en) 1992-12-02
EP0516561B1 true EP0516561B1 (en) 1995-09-13

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Family Applications (1)

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EP92420165A Expired - Lifetime EP0516561B1 (en) 1991-05-30 1992-05-20 Hydraulic impact apparatus

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US (1) US5392865A (en)
EP (1) EP0516561B1 (en)
JP (1) JP2515206B2 (en)
AT (1) ATE127717T1 (en)
AU (1) AU647623B2 (en)
CA (1) CA2069184C (en)
DE (1) DE69204747T2 (en)
DK (1) DK0516561T3 (en)
ES (1) ES2077379T3 (en)
FI (1) FI101688B1 (en)
FR (1) FR2676953B1 (en)
ZA (1) ZA923479B (en)

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FR2676953A1 (en) 1992-12-04
ZA923479B (en) 1993-01-27
ES2077379T3 (en) 1995-11-16
JP2515206B2 (en) 1996-07-10
AU1728792A (en) 1992-12-03
DE69204747T2 (en) 1996-02-22
FI101688B (en) 1998-08-14
FI101688B1 (en) 1998-08-14
FI922483A0 (en) 1992-05-29
JPH05146976A (en) 1993-06-15
FI922483A (en) 1992-12-01
EP0516561A1 (en) 1992-12-02
DE69204747D1 (en) 1995-10-19
DK0516561T3 (en) 1996-01-29
CA2069184C (en) 1996-02-27
FR2676953B1 (en) 1993-08-20
US5392865A (en) 1995-02-28
AU647623B2 (en) 1994-03-24
ATE127717T1 (en) 1995-09-15
CA2069184A1 (en) 1992-12-01

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