EP0516561B1 - Hydraulischer Schlagapparat - Google Patents

Hydraulischer Schlagapparat 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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Expired - Lifetime
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EP92420165A
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English (en)
French (fr)
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EP0516561A1 (de
Inventor
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)

Claims (11)

  1. Schlagapparat mit einem Schlagkolben (1), der hydraulisch mittels eines inkompressiblen Fluids im Innern eines Zylinders hin und her angetrieben wird und auf ein Werkzeug (60) aufschlägt, wobei der Kolben in einem Zylinder gleitet und zwei konzentrische Kolbenauflageflächen mit unterschiedlichen Querschnitten aufweist, von denen diejenige auf der Seite des Werkzeugs einen kleineren Querschnitt gegenüber der von dem Werkzeug weiter entfernten hat, wobei der Kolben und der Zylinder zwei gegenwirkende Kammern, eine kreisringförmige untere Kammer (7) und eine obere Kammer mit größerem Querschnitt begrenzen, dadurch gekennzeichnet, daß er Einrichtungen zur Regelung des Drucks aufweist, um ständig einen geregelten Druck mit einem Zwischenwert zwischen dem Einlaßdruck oder Hochdruck und dem Auslaßdruck oder Niederdruck zu erzeugen, und zwar im Innern der oberen Kammer (3) und der unteren kreisringförmigen Kammer (7) während des beschleunigten Abwärtshubs des Kolbens und im Innern der oberen Kammer (3) während des Aufwärtshubs des Kolbens, wenn die kreisringförmige Kammer (7) dem Zufuhrdruck oder Hochdruck ausgesetzt wird, wobei ein Verteiler (6) die Herstellung der Verbindung der kreisringförmigen Kammer (7) wechselweise mit dem Hochdruck-Zufuhrkreis während der Aufwärtsphase des Kolbens und mit der oberen Kammer (3) während der beschleunigten Abwärtsphase des Kolbens (1) sichert.
  2. Schlagapparat nach Anspruch 1, dadurch gekennzeichnet, daß die Einrichtungen zur Regelung des Zwischendrucks einerseits aus einem Energieakkumulator und andererseits aus einem Druckregler bestehen, der einen Zylinder aufweist, in dessem Innern ein einen Schieber bildender Kolben (9) eingebaut ist, bei dem ein Ende eine Kammer (18) begrenzt, die kontinuierlich oder diskontinuierlich mit dem Hochdruck verbunden ist, und bei dem sich das andere Ende in einer Kammer (19) befindet, die kontinuierlich oder diskontinuierlich mit dem Zwischendruck verbunden ist und eine Feder enthält, die den Schieber zu seinem anderen Ende hin verschieben kann, wobei die mit dem Zwischendruck verbundene Kammer (19) über eine Einschnürung, die sich an dem Fluidkreislauf befindet, mit einer mittleren Kammer (21) in Verbindung steht, die, verbunden mit dem Niederdruck-Rücklaufkreis (8), durch eine Querschnittsverringerung des Schiebers erzielt wird.
  3. Schlagapparat nach Anspruch 2, dadurch gekennzeichnet, daß die Kammer (18) des mit dem Hochdruck verbundenen Druckreglers mit einer kreisringförmigen Kammer (26) in Verbindung steht, die in den Zylinder eingearbeitet ist, in welchem sich der Schlagkolben (1) bewegt, und die ständig mit der Hochdruck-Fluidquelle verbunden ist.
  4. Schlagapparat nach Anspruch 2, dadurch gekennzeichnet, daß die Kammer (18) des mit dem Hochdruck verbindbaren Druckreglers mit der unteren kreisringförmigen Kammer (7) in Verbindung steht, die ihrerseits während der Aufwärtsphase des Kolbens mit dem Hochdruck verbunden ist.
  5. Schlagapparat nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Bewegung des Schlagkolbens durch einen hydraulischen Verteiler (6) gesteuert wird, der gleitend in einem Zylinder eingebaut ist, mit dem er vier gesonderte Kammern begrenzt, und zwar zwei sich an den beiden Enden des Verteilers befindende Kammern (3, 12), die über einen breiten Kanal (15) verbunden sind und ständig mit dem Zwischendruckkreis in Verbindung stehen, einer ersten kreisringförmigen Kammer (13), die ständig mit dem Hochdruckkreis verbunden ist, und einer zweiten, der vorhergehenden entgegenwirkenden kreisringförmigen Kammer (14), deren aktiver Querschnitt größer ist, welche wechselweise mit dem Hochdruckkreis und dem Zwischendruckkreis in Abhängigkeit von der Stellung des Schlagkolbens verbunden ist.
  6. Schlagapparat nach Anspruch 5, dadurch gekennzeichnet, daß der Verteiler (6) kreisringförmig ist und einen breiten mittigen Kanal (15) aufweist, der die an seinen Enden angeordneten gegenwirkenden Kammern (3, 12) in Verbindung bringt.
  7. Schlagapparat nach Anspruch 6, dadurch gekennzeichnet, daß der Verteiler (6) koaxial zu dem Schlagkolben (1) und in dem gleichen Zylinder wie dieser und oberhalb von ihm angeordnet ist.
  8. Schlagapparat nach Anspruch 7, dadurch gekennzeichnet, daß der Verteiler (6) eine kreisringförmige Nut (25) aufweist, die bei einer Stellung des Verteilers Nuten in Verbindung bringt, die in den Körper des Apparats eingearbeitet sind und jeweils mit der Hochdruck-Fluidquelle (4) und der unteren kreisringförmigen Kammer (7) verbunden sind.
  9. Schlagapparat nach einem der Ansprüche 6 und 7, dadurch gekennzeichnet, daß der Zylinder, in den der Schlagkolben (1) und der Verteiler (6) eingebaut sind, über eine kreisringförmige Wand (39) in zwei Abteile unterteilt ist.
  10. Schlagapparat nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß der Hochdruck-Fluidzufuhrkreis mit einem hydropneumatischen Akkumulator (10) geringen Volumens ausgerüstet ist, der die Druckschwankungen am Einlaß des Apparats dämpft.
  11. Schlagapparat nach Anspruch 2, dadurch gekennzeichnet, daß die obere Kammer (12) mit dem Druckregler über einen Kanal (5) verbunden ist, der in eine Nut (61) mündet, die in den Körper des Apparats in einen Bereich eingearbeitet ist, der von dem Verteiler (6) in der Abwärtsperiode des Schlagkolbens (1) bedeckt ist und während der Aufwärtsperiode des Schlagkolbens nicht bedeckt ist.
EP92420165A 1991-05-30 1992-05-20 Hydraulischer Schlagapparat Expired - Lifetime EP0516561B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9106693A FR2676953B1 (fr) 1991-05-30 1991-05-30 Appareil hydraulique a percussions.
FR9106693 1991-05-30

Publications (2)

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

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ID=9413413

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Application Number Title Priority Date Filing Date
EP92420165A Expired - Lifetime EP0516561B1 (de) 1991-05-30 1992-05-20 Hydraulischer Schlagapparat

Country Status (12)

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

Families Citing this family (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995016548A1 (en) * 1993-12-17 1995-06-22 Jarmo Uolevi Leppanen Accumulator charging system
DE59409798D1 (de) * 1994-02-19 2001-08-16 Klemm Guenter Hydraulischer Schlaghammer
FI104959B (fi) * 1994-06-23 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
JPH11508187A (ja) * 1995-06-21 1999-07-21 ヒドロプルソール アーベー 衝撃装置
WO1997002386A1 (fr) * 1995-07-06 1997-01-23 Komatsu Ltd. Rouleau-compacteur hydraulique
FI104960B (fi) * 1995-07-06 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
DE19652079C2 (de) * 1996-12-14 1999-02-25 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk
AU3862797A (en) * 1997-07-23 1999-02-16 Idromeccanica Italiana S.R.L. Hydraulic percussion device
US6764644B2 (en) * 1998-02-18 2004-07-20 Hydropulsor Ab Method of using an impact machine
FI107891B (fi) * 1998-03-30 2001-10-31 Sandvik Tamrock Oy Painenestekäyttöinen iskulaite
FI106618B (fi) * 1998-03-30 2001-03-15 Sandvik Tamrock Oy Sovitelma painenestekäyttöisen iskulaitteen, kuten esimerkiksi rikotuslaitteen yhteydessä
DE19923680B4 (de) * 1999-05-22 2004-02-26 Atlas Copco Construction Tools Gmbh Verfahren zur Ermittlung der Betriebsdauer und des Einsatz-Zustands eines hydraulischen Schlagaggregats, insbesondere Hydraulikhammer, sowie Vorrichtung zur Durchführung des Verfahrens
US6510904B1 (en) 2000-05-26 2003-01-28 Nippon Pneumatic Mfg. Co., Ltd. Protected tool bushing for an impact hammer
FR2811601B1 (fr) * 2000-07-13 2002-10-11 Montabert Ets Appareil hydraulique a percussions
NZ516798A (en) * 2002-07-24 2004-07-30 Bantry Ltd Sonic drilling
WO2004015357A2 (en) * 2002-08-09 2004-02-19 Fats, Inc. Gas operating system for firearm simulators
FI114290B (fi) * 2003-02-21 2004-09-30 Sandvik Tamrock Oy Ohjausventtiili ja järjestely iskulaitteessa
FI115451B (fi) * 2003-07-07 2005-05-13 Sandvik Tamrock Oy Iskulaite ja menetelmä jännityspulssin muodostamiseksi iskulaitteessa
EP1697089B1 (de) * 2003-12-19 2007-11-14 Clark Equipment Company Schlagwerkzeug
JP4200918B2 (ja) * 2004-02-09 2008-12-24 日立工機株式会社 穿孔機
SE527762C2 (sv) * 2004-10-14 2006-05-30 Atlas Copco Rock Drills Ab Slagverk
SE527921C2 (sv) * 2004-10-20 2006-07-11 Atlas Copco Rock Drills Ab Slagverk
SE529615C2 (sv) * 2006-02-20 2007-10-09 Atlas Copco Rock Drills Ab Slagverk och bergborrmaskin samt förfarande för att styra slagkolvens slaglängd
US7607491B2 (en) * 2006-03-15 2009-10-27 Integrated Tool Solutions Llc Jackhammer lift assist
FR2916377B1 (fr) * 2007-05-25 2009-07-24 Montabert Soc Par Actions Simp Procede de protection contre les suralimentations en debit d'un appareil a percussions mu par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procede.
DE102011002058A1 (de) * 2011-04-14 2012-10-18 Böllhoff Verbindungstechnik GmbH Hydraulisch betriebenes Setzgerät mit einem Hydraulikaggregat und ein Fügeverfahren zum Verbinden von mindestens zwei Bauteilen
AT511810B1 (de) * 2011-09-27 2013-03-15 Tmt Bbg Res And Dev Gmbh Schlagwerk für eine hammereinrichtung und verfahren zum offenstellen einer abstichöffnung
DE102012208913A1 (de) * 2012-05-25 2013-11-28 Robert Bosch Gmbh Schlagwerkeinheit
US9151386B2 (en) * 2013-03-15 2015-10-06 Caterpillar Inc. Accumulator membrane for a hydraulic hammer
CN105916634B (zh) * 2014-01-30 2017-08-25 古河凿岩机械有限公司 液压式冲击装置
CN106164300B (zh) * 2014-04-11 2019-10-08 考麦兹股份公司 用于切割兽皮和类似物的机器用的切割装置
FR3027543B1 (fr) * 2014-10-28 2016-12-23 Montabert Roger Appareil a percussions
US20160340849A1 (en) 2015-05-18 2016-11-24 M-B-W, Inc. Vibration isolator for a pneumatic pole or backfill tamper
US20170157759A1 (en) * 2015-12-08 2017-06-08 Caterpillar Inc. Dust Clearing Tool
US10377028B2 (en) * 2016-03-14 2019-08-13 Caterpillar Inc. Hammer protection system and method
EP3569362B1 (de) * 2017-01-12 2023-01-11 Furukawa Rock Drill Co., Ltd. Hydraulische hammervorrichtung
JP6757682B2 (ja) * 2017-02-24 2020-09-23 古河ロックドリル株式会社 液圧式打撃装置
US11590642B2 (en) * 2017-07-24 2023-02-28 Furukawa Rock Drill Co., Ltd. Hydraulic hammering device
FR3094658B1 (fr) * 2019-04-03 2021-03-19 Montabert Roger Appareil à percussions avec régulation automatique de la pression d’alimentation de l’appareil à percussions
KR102317232B1 (ko) * 2020-01-08 2021-10-22 주식회사 현대에버다임 유압 브레이커

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1431835A (fr) * 1965-01-28 1966-03-18 Montabert Ets Appareil à percussions
US3830463A (en) * 1970-11-09 1974-08-20 Worthington Cei Venturi back pressure controls
US3887019A (en) * 1971-05-11 1975-06-03 Af Hydraulics Hydraulic percussive implement
FI50390C (fi) * 1973-09-14 1976-03-10 Murskauskone Oy Hydraulisesti käytetty iskulaite
GB2100364B (en) * 1981-04-23 1985-01-09 Musso Mario A hydraulic percussive drill
DE3271910D1 (en) * 1982-01-22 1986-08-14 Mauro Vitulano Directional control valve to obtain in a hydraulic appliance the alternative motion of a piston operating to charge and fire a tool, specially suitable for hydraulic hammers
GB2141657A (en) * 1983-05-10 1985-01-03 Panther Equip Ltd Improvements in hydraulically operated hammers
DE3400302A1 (de) * 1984-01-03 1985-08-29 Mannesmann AG, 4000 Düsseldorf Hydraulisch betaetigte schlagvorrichtung
FR2602448B1 (fr) * 1986-08-07 1988-10-21 Montabert Ets Procede de regulation des parametres de percussion du piston de frappe d'un appareil mu par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procede

Also Published As

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

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