• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A rock breaking device (10) having a striking cell (12) having at least one actuating chamber (14), a striking piston (16), and a hydraulic circuit including a hydraulic power source having a high pressure circuit (17) and a low pressure circuit (18), and an actuator (20) configured to connect the high pressure circuit (17) or the low pressure circuit (18) to the actuating chamber (14) so as to move the piston in translation in the striking cell (12) in a normal displacement zone whose limits are variable as a function of the pressure difference between the high pressure circuit (17) and the low pressure circuit (18) , the striking cell (12) comprising depressurization means configured to control a hydraulic communication of the High Pressure circuit (17) with the low pressure circuit (18) when the striking piston (16) leaves a zone of pre displacement determined.
    公开号:FR3044572A1
    申请号:FR1561749
    申请日:2015-12-02
    公开日:2017-06-09
    发明作者:Bernard Piras
    申请人:Montabert SAS；
    IPC主号:
    专利说明:

    ROCK BRISE DEVICE
    Technical area
    The present invention relates to the field of public works machinery. It relates to a percussion hydraulic apparatus type "breaker" or the like.
    PRIOR ART
    As described in Figures 1 and 2 illustrating the state of the art, hydraulic percussion apparatus 100 called "breakers" generally consist of a body containing a striking cell 120 protected from the outside environment by a mechanically welded structure which also makes it possible to secure the striking cell 120 to a carrier 11.
    The striking cell 120 comprises a greased mechanical front portion which carries a tool 250 intended to come into contact with a rock to be broken. The tool 250 is guided by wear rings, retained in translation in one direction by a system of keys and in the other direction by a fitting abutment 300 which allows to transmit the support of the carrier 11. A part the center of the striking cell 120 comprises a striking piston 160 movable in translation in a cylinder so as to strike the tool 250. A third part of the striking cell 120 may be located laterally or above the cylinder and comprises a hydraulic circuit providing a clockwise reciprocating movement of the striking piston 160.
    The movements of the striking piston 160 are controlled by two annular chambers 140, 150 antagonists fed alternately with fluid under pressure. The striking cell 120 also comprises a compression chamber 290, containing a compressible gas, disposed above the striking piston 160. When the device 100 is actuated, a first phase consists of moving the striking piston 160 in the chamber of compression 290 by application of a pressure in the lower annular chamber 150, thereby compressing the gas in the compression chamber 290. A second phase is to cancel the effect of the pressure in the lower annular chamber 150, by feeding substantially the same pressure the upper annular chamber 140. The force complementary to that created by the compressible gas then applied to the striking piston 160 depends on the surface difference between the annular chambers 140, 150 and this surface difference is generally low. In a third phase, the compressible gas relaxes and violently moves the striking piston 160 downwardly impacting the tool 250 with sufficient force to break a rock.
    The annular chambers 140, 150 are fed by a high pressure circuit 170 and a low pressure circuit 180. Preferably, the high pressure circuit 170 is connected to a hydraulic pump and the low pressure circuit 180 is connected to an open reservoir of the The upper annular chamber 140 is connected either to the high pressure circuit 170 or to the low pressure circuit 180 via an actuator 200, for example a distributor. The position of the actuator 200 is controlled by the position of the striking piston 160. For this purpose, the striking piston 160 comprises an actuating chamber 280 which can be connected on the one hand to the low-pressure circuit 180 and on the other hand. part of the control circuit 210 of the actuator 200. The control circuit 210 of the actuator 200 comprises a channel opening into the lower annular chamber 150 during the rise of the striking piston 160. The lower annular chamber 150 being connected with the high pressure circuit 170 of the hydraulic circuit, the control circuit 210 is thus connected to the high pressure circuit 170 which causes a control of the actuator 200 so as to connect the upper annular chamber 140 with the high pressure circuit 170 of the hydraulic circuit . During the descent of the striking piston 160, the actuating chamber 280 connects the control circuit 210 with the low pressure circuit 180. The control circuit 210 is thus connected to the low pressure circuit 180 which causes a displacement of the control slide. the actuator 200 so as to connect the upper annular chamber 140 with the low pressure circuit 180. The control of the actuator 200 is thus performed hydraulically according to the position of the striking piston 160.
    However, when the pressure of the high pressure circuit 170 exceeds a threshold value, for example during improper handling of an operator acting on the carrier 11, the speed of the striking piston 160 increases. The control of the actuator 200 being performed according to the position of the striking piston 160, the duration of the control cycles of the actuator 200 also decreases when the speed of the striking piston 160 increases causing a runaway piston speed In addition, the stroke of the striking piston 160 also increases in the compression chamber 290. Thus, an overflow of the high pressure circuit 170 can generate an overspeed of the striking piston 160 with respect to a limit speed for resistance to fatigue and wear of the device 100. In addition, damage may also occur due to this overspeed.
    To solve this problem, it is known from US Patent Application No. US 2008/0296035, as shown in Figure 2, to use a hydraulic fuse 110 positioned between the high pressure circuit 170 and the low pressure circuit 180 of so as to return a portion of the flow of the high pressure circuit 170 to the low pressure circuit 180 when the pressure of the high pressure circuit 170 exceeds a threshold value. However, this solution is complex to integrate into the body of the device.
    International Patent Application No. WO 2008/149030 proposes an alternative solution of diverting the excess flow directly to the tank of the carrier. However, this solution requires modifying the carrier.
    The French patent application No. FR 2916377 of the present Applicant proposes a solution consisting in measuring the flow rate at the high pressure circuit 170 and diverting the excess flow to the low pressure circuit 180 when the flow rate of the high pressure circuit 170 exceeds a predetermined value. The flow deflection is effected by a flow control device disposed in the impact cell 120 at an upper end of the striking piston 160. However, this solution increases the radial space requirement of the upper part of the pressure cell. Strikes 120. Increasing the size of the impact cell 120 also increases the complexity of assembly and design of the breakwater device. In addition, this solution is not implemented for low power devices because the size of the overflow protection solution would be too large compared to the volume of the impact cell 120.
    The technical problem of the invention is therefore to provide a rock break device provided with a protection against overflow whose size is reduced.
    Expose the invention
    The present invention proposes to solve this problem by means of a rock break device provided with a protection against overflow which is controlled according to the stroke of the piston. To this end, the invention relates to a rock break device comprising a striking cell having at least one actuating chamber, a striking piston movable in translation in the impact cell, and a hydraulic circuit comprising a hydraulic power source. having a high pressure circuit and a low pressure circuit, and an actuator configured to connect the high pressure circuit or the low pressure circuit to the operating chamber so as to move the piston in translation in the impact cell in a displacement zone normal whose limits are variable depending on the pressure difference between the high pressure circuit and the low pressure circuit. The striking cell also comprises depressurization means configured to control a hydraulic communication of the High Pressure circuit with the low pressure circuit when the striking piston leaves a predetermined displacement zone. The invention thus makes it possible to use the increase of the normal stroke of the striking piston when there are overflow to control a transfer of flow from the high pressure circuit to the low pressure circuit thus making it possible to limit the bulk. of the device breaks rocks. In addition, integration and mounting of the overflow protection with existing elements is facilitated.
    According to one embodiment, the depressurization means comprise: - a groove disposed on the striking piston, and - a regulating portion connected on the one hand to the high pressure circuit and on the other hand to the low pressure circuit, the portion of control being closed by the striking piston when the striking piston is movable in the predetermined displacement zone, - said groove being intended to penetrate into the regulating portion when the striking piston leaves the predetermined displacement zone so as to put in hydraulic communication the high pressure circuit with the low pressure circuit through the regulation portion.
    This embodiment is particularly simple to achieve because the realization of a groove in the striking piston is a conventional process.
    According to one embodiment, the depressurization means comprise: a depressurization valve connected on the one hand to the high pressure circuit and on the other hand to the low pressure circuit, the depressurization valve being able to adopt two positions: a holding position in which the high pressure circuit is disconnected from the low pressure circuit, and a depressurization position in which the high pressure circuit is connected to the low pressure circuit, - the position of said depressurization valve being controlled by a hydraulic circuit, - a regulating portion connected on the one hand to the high pressure circuit and on the other hand to the hydraulic circuit, the regulation portion being closed by the striking piston when the striking piston is movable in the predetermined displacement zone so that the hydraulic circuit controls the depressurizing valve in the holding position, and - a groove disposed on the striking piston; - said groove being intended to penetrate into the regulating portion when the striking piston exits the predetermined displacement zone so that the hydraulic circuit controls the depressurization valve in the depressurization position.
    This embodiment makes it possible to limit the flow rate in the groove because the fluid that passes through the groove serves only to control the depressurization valve.
    According to one embodiment, the depressurization means comprise: a groove and an annular protuberance disposed consecutively on the striking piston, and a regulating portion connected on the one hand to the low pressure circuit and on the other hand to the chamber. actuating, the annular protrusion closing a hydraulic communication channel between the regulating portion and the actuating chamber when the striking piston is movable in the predetermined displacement zone, - said groove being intended to penetrate into the chamber d actuation when the striking piston exits the predetermined displacement zone so as to hydraulically communicate the actuating chamber with the regulating portion through a channel passing through the groove.
    This embodiment makes it possible to limit the size of the device by arranging the actuating chamber in hydraulic communication with the regulation portion.
    According to one embodiment, the device comprising two actuating chambers, an upper actuating chamber and a lower actuating chamber, the regulating portion is positioned above the upper actuating chamber.
    According to one embodiment, the device comprising two actuating chambers, an upper actuating chamber and a lower actuating chamber, the regulating portion is positioned below the upper actuating chamber.
    According to one embodiment, the device comprising two actuating chambers, an upper actuating chamber and a lower actuating chamber, the regulating portion is positioned between the two actuating chambers.
    According to one embodiment, the device comprises hydraulic braking means of the striking piston configured to slow down the stroke of the striking piston when the striking piston leaves the predetermined displacement zone. This embodiment makes it possible to calibrate the quantity of fluid transmitted between the high pressure circuit and the low pressure circuit when the striking piston leaves the predetermined displacement zone.
    According to one embodiment, the hydraulic braking means comprise a nozzle connected to the low pressure circuit and configured to extract a portion of a hydraulic fluid contained in the hydraulic braking means. This embodiment also makes it possible to calibrate the quantity of fluid transmitted between the high pressure circuit and the low pressure circuit when the striking piston leaves the predetermined displacement zone.
    According to one embodiment, the hydraulic braking means comprise: - a channel connecting the actuating chamber with the low pressure circuit, - an annular protrusion disposed on the striking piston, and - a movable ring in the actuating chamber. the ring being positioned to close the channel when the striking piston is movable in the predetermined displacement zone, the annular protrusion being intended to penetrate into the ring when the striking piston leaves the predetermined displacement zone so that creating a drain compartment whose pressure is sufficient to move the ring and establish a hydraulic communication between the emptying compartment and the channel, - the annular protrusion being extracted from the ring and the ring being repositioned to close the channel when the pressure difference between the actuating chamber and the drain compartment is greater than a value threshold.
    This embodiment provides braking of the striking piston so as to calibrate the amount of fluid transmitted between the high pressure circuit and the low pressure circuit when the striking piston out of the predetermined displacement zone. In addition, this embodiment limits the size of the braking system since it is integrated with the actuating chamber.
    According to one embodiment, the hydraulic braking means (35) comprise: - an annular protuberance disposed on the striking piston, and - a ring movable in the actuating chamber, - the annular protrusion being intended to penetrate into the ring when the striking piston leaves the predetermined displacement zone so as to create a drain compartment whose pressure is sufficient to move the ring around the annular protrusion, - the fluid contained in the drain compartment being able to join the operating chamber by a peripheral channel formed around the ring when the ring is moved on the annular protrusion so as to reduce the pressure difference between the emptying compartment and the actuating chamber and extract the annular protrusion of the ring.
    This embodiment also provides braking of the striking piston so as to calibrate the amount of fluid transmitted between the high pressure circuit and the low pressure circuit when the striking piston out of the predetermined displacement zone. In addition, this embodiment limits the size of the braking system since it is integrated with the actuating chamber and has no channel connecting the actuating chamber with the low pressure circuit.
    Brief description of the figures
    The manner of carrying out the invention as well as the advantages which derive from it will emerge clearly from the following embodiment, given by way of indication but without limitation, in support of the appended figures in which FIGS. 1 to 11 represent: FIG. 1, state of the art: a perspective view of a carrier equipped with a broken rocks device; - Figure 2, state of the art: a schematic sectional representation of the rock break device of Figure 1; - Figure 3: a schematic sectional representation of a rock break device according to a first embodiment of the invention; - Figure 4: a schematic sectional representation of a rock break device according to a second embodiment of the invention; - Figure 5: a schematic sectional representation of a rock break device according to a third embodiment of the invention; - Figure 6: a schematic sectional representation of a rock break device according to a fourth embodiment of the invention; - Figure 7: a schematic sectional representation of a rock break device according to a fifth embodiment of the invention; - Figure 8: a schematic sectional representation of a rock break device according to a sixth embodiment of the invention; - Figures 9-11: a schematic sectional representation of a rock break device according to a seventh embodiment of the invention; and - Figure 12: a schematic sectional representation of a rock break device according to an eighth embodiment of the invention.
    Detailed Description of the Invention
    In the description, the percussion hydraulic apparatus 10a-10f is described assuming that it is positioned in its most common configuration, namely vertically, i.e., with the tool 25 vertically oriented in contact with each other. a surface to be destroyed as shown in Figure 1.
    Figure 3 illustrates a hydraulic percussion apparatus 10a referred to as "breaker devices" for mounting on a carrier 11 as illustrated in Figure 1. The breaker device 10a has a strike cell 12a protected from the external environment by a welded structure, not shown, which also ensures the attachment of the striking cell 12a to the carrier 11.
    The striking cell 12a has a greased mechanical front portion which carries a tool 25 intended to come into contact with a rock to be broken. The tool 25 is guided by wear rings, retained in translation in one direction by a system of keys and in the other direction by a fitting abutment 30 which allows to transmit the support of the carrier 11. A part The center of the striking cell 12a comprises a striking piston 16 movable in translation in the striking cell 12a so as to strike the tool 25. A third part of the striking cell 12a can be located laterally or above the piston 16 and comprises a hydraulic circuit providing a reciprocating clockwise movement of the striking piston 16.
    The movements of the striking piston 16 are controlled by two chambers 14, 15 antagonists fed alternately with fluid under pressure. For this purpose, the striking piston 16 has an upper shoulder 26 on which a fluid contained in the upper chamber 14 can bear to move the striking piston 16 downwards and a lower shoulder 27 on which a fluid contained in the chamber lower 15 can bear to move the striking piston 16 upwards. The striking cell 12a also comprises a compression chamber 29, containing a compressible gas, disposed above the striking piston 16. When the device 10a is actuated, a first phase consists of moving the striking piston 16 in the chamber of compression 29 by applying a pressure in the lower chamber 15, thereby compressing the gas in the compression chamber 29. A second phase is to cancel the effect of the pressure in the lower chamber 15, supplying substantially the same pressure the upper chamber 14. The force then applied to the striking piston 16 depends on the surface difference between the shoulders 26, 27. This surface difference is generally small. In a third phase, the compressible gas relaxes and violently moves the striking piston 16 downward, impacting the tool 25 with sufficient force to break a rock.
    The chambers 14, 15 are fed by a high pressure circuit 17 and a low pressure circuit 18. Preferably, the high pressure circuit 17 is connected to a hydraulic pump and the low pressure circuit 18 is connected to an open tank of the machine The upper chamber 14 is connected either to the high pressure circuit 17 or to the low pressure circuit 18 via an actuator 20, for example a distributor. The position of the actuator 20 is controlled by the position of the striking piston 16. For this purpose, the striking piston 16 comprises an actuating chamber 28 which can be connected on the one hand to the low-pressure circuit 18 and on the other hand part of the control circuit 21 of the actuator 20. The control circuit 21 of the actuator 20 has channel opening into the lower chamber 15 during the rise of the striking piston 16. The lower chamber 15 being connected with the circuit High pressure 17 of the hydraulic circuit, the control circuit 21 is thus connected to the high pressure circuit 17, which causes a control of the actuator 20 so as to connect the upper chamber 14 with the high pressure circuit 17 of the hydraulic circuit. During the descent of the striking piston 16, the actuating chamber 28 connects the control circuit 21 with the low pressure circuit 18. The control circuit 21 is thus connected to the low pressure circuit 18 which causes a displacement of the spool. the actuator 20 so as to connect the upper chamber 14 with the low pressure circuit 18. The control of the actuator 20 is thus performed hydraulically according to the position of the striking piston 16.
    However, when the pressure of the high pressure circuit 17 exceeds a threshold value, for example during improper handling of an operator acting on the carrier machine 11, the speed of the striking piston 16 increases. The control of the actuator 20 being performed according to the position of the striking piston 16, the duration of the control cycles of the actuator 20 also decreases when the speed of the striking piston 16 increases causing a runaway piston speed Moreover, the stroke of the striking piston 16 also increases in the compression chamber 29. Thus, an overflow of the high pressure circuit 17 can generate an overspeed of the striking piston 16 with respect to a limit speed for resistance to fatigue and wear of the device 10a. In addition, damage may also occur due to this overspeed.
    To solve this problem, the first embodiment, illustrated in Figure 3, proposes to have a groove 23 on the striking piston 16 so as to cooperate with a control portion 22 disposed in the body of the striking cell 12a. The control portion 22 is connected on the one hand to the high pressure circuit 17 and on the other hand to the low pressure circuit 18. The section of the striking piston 16 is adapted to the internal section of the striking cell 12a so that the control portion 22 is closed by the striking piston 16 when the striking piston 16 is movable in a predetermined displacement zone.
    The predetermined displacement zone corresponds to a regulated use of the device 10a in which the flow rate of the high pressure circuit 17 is lower than a threshold value. The combination of the groove 23 and the regulating portion 22 forms depressurization means making it possible to put the high-pressure circuit 17 in hydraulic communication with the low-pressure circuit 18 as a function of the position of the striking piston 16 in the control cell. strike 12a.
    Preferably, the striking piston 16 has a form of revolution cooperating with chambers 14, 15 annular. The striking piston 16 may comprise seals disposed on either side of the groove 23.
    FIG. 4 illustrates a second embodiment of a striking cell 12b of a device 10b in which the regulation portion 22 is connected to the High Pressure circuit 17 so as to control a depressurization valve 32. The depressurization valve 32 is movable between two positions: a holding position in which the high pressure circuit 17 is disconnected from the low pressure circuit 18, and a depressurization position in which the high pressure circuit 17 is connected to the low pressure circuit 18. The position of said valve depressurization 32 is controlled by a hydraulic circuit 31 connected to the control portion 22. A return spring 33 is arranged to put the depressurization valve 32 in the holding position when the high pressure circuit 17 is not connected to the circuit hydraulic 31.
    In the same manner as for the first embodiment of Figure 3, the control portion 22 is closed by the striking piston 16 when the striking piston 16 is movable in the predetermined displacement zone. Thus, the hydraulic circuit 31 is not connected to the high pressure circuit 17 and the return spring 33 puts the depressurization valve 32 in the holding position. When the striking piston 16 leaves the predetermined displacement zone, the hydraulic circuit 31 is connected to the high-pressure circuit 17 and controls the depressurization valve 32 in the depressurization position by overcoming the return force of the return spring 33.
    These two embodiments, illustrated in FIGS. 3 and 4, make it possible to transmit a part of the fluid of the high pressure circuit 17 to the low pressure circuit 18. The quantity of fluid that is thus transmitted depends on the communication time between the circuits. Pressure 17 and Low Pressure 18. To calibrate the amount of fluid transmitted to each cycle in which the striking piston 16 leaves the predetermined displacement zone, it is possible to lengthen the stroke of the striking piston 16, for example a few millimeters
    For the same purpose, FIG. 5 illustrates a third embodiment of a striking cell 12c of a device 10c in which the striking cell 12c comprises braking means 35 of the striking piston 16. The braking means 35 are arranged above the upper chamber 14 and allow to slow the stroke of the striking piston 16 when the striking piston 16 leaves the predetermined displacement zone. The duration of transmission of the fluid between the High Pressure 17 and Low Pressure 18 circuits is then increased. Preferably, the braking means 35 are formed by a flange arranged on the striking piston 16 and intended to penetrate into a chamber of the striking cell 12c filled with compressible fluid. When the striking piston 16 leaves the predetermined displacement zone, a surface of the flange cooperates with the compressible fluid of the chamber of the striking cell 12c, which causes the striking piston 16 to slow down.
    FIG. 6 illustrates a fourth embodiment of a striking cell 12d of a device 10d in which the braking means 35 are connected to the Low Pressure circuit 18 by means of a nozzle 37. This embodiment makes it possible to the complete stop of the operating cycle when the striking piston 16 leaves the predetermined displacement zone the time that the nozzle empties the fluid contained in the braking means 35. For this purpose, the surface of the collar of the striking piston 16 and the surface of the impact cell 12d filled with compressible fluid are calculated so that the resultant of the forces applied to the striking piston 16 as a function of the pressures maintains the striking piston 16 with a total discharge of the compressible fluid under pressure to the circuit Low Pressure 18.
    The four embodiments of FIGS. 3-6 illustrate a regulating portion 22 positioned above the upper actuating chamber 14. Alternatively, FIG. 7 illustrates a fifth embodiment of a 12 th striking cell. a device 10e in which the control portion 22 is positioned between the two actuating chambers 14, 15. FIG. 8 illustrates a sixth embodiment of a striking cell 12f of a device 10f in which the control portion 22 is positioned below the lower actuating chamber 15.
    FIGS. 9 to 11 illustrate a seventh embodiment of a striking cell 12g of a device 10g in which the regulation portion 22 is in hydraulic communication with the upper actuating chamber 14. The regulating portion 22 is arranged immediately below the upper chamber 14 and has a diameter smaller than the diameter of the upper chamber 14. The striking piston 16 has a groove 22 arranged consecutively with an annular protrusion 41 so that the annular protrusion 41 can cooperate with the portion 22 and hydraulically isolate the control portion 22 from the upper chamber 14. Thus, when the striking piston 16 is movable in the predetermined displacement zone, as shown in Figure 10, the annular protrusion 41 blocks any hydraulic communication between the upper chamber 14 and the regulating portion 22.
    The control portion 22 is also connected with the low pressure circuit 18. When the striking piston 16 leaves the predetermined displacement zone, as illustrated in FIG. 9, the annular protrusion 41 of the striking piston 16 is positioned in the upper chamber 14 and the groove 23 of the striking piston 16 makes it possible to establish a hydraulic communication between the upper chamber 14 and the regulation portion 22. The fluid of the high pressure circuit 17 contained in the upper chamber 14 is then transmitted to the low pressure circuit 18 via the regulating portion 22.
    The braking system of the striking piston 16 differs from the previous embodiments because it comprises a movable ring 40 disposed in the upper chamber 14. The ring 40 is disposed in front of a channel 42 connecting the upper chamber 14 with the low pressure circuit 18. Thus, when the striking piston 16 is movable in the predetermined displacement zone, the pressure of the high pressure circuit contained in the upper chamber 14 plates the ring 40 against the channel 42 which blocks the hydraulic communication between the high pressure circuit 17 and the low pressure circuit 18 through the channel 42.
    As illustrated in Figures 10 and 11, the annular protrusion 41 of the striking piston 16 is configured to cooperate with the ring 40 when the striking piston 16 exits the predetermined displacement zone. When the striking piston 16 rises in the upper chamber 14, the annular protrusion 41 enters the ring 40, a drain compartment 43 is formed. This emptying compartment 43 can then be hydraulically isolated from the upper chamber 14 and thus from the high pressure circuit 17.
    The fluid of the high pressure circuit 17 remaining in this emptying compartment 43 then causes a displacement of the ring 40 downwardly around the striking piston 16 which opens the channel 42 connecting the emptying compartment 43 with the low pressure circuit 18. The fluid from the emptying compartment 43 is then transmitted to the low pressure circuit 18 and possibly the chamber 14, during this process, the striking piston 16 is held in the ring 40. When a sufficient quantity of fluid has been transmitted between the emptying compartment 43 and the low pressure circuit 18 and possibly the chamber 14, the striking piston 16 reverses its movement and begins its descent, the ring 40 is redirected upwards to close the channel 42 once more. Strike 16 is released slowly from the ring 40 and the striking piston 16 can resume normal activity. During this braking process, a large quantity of fluid could thus be transmitted between the high pressure circuit 17 and the low pressure circuit 18 via the regulation portion 22.
    This embodiment makes it possible to more easily manage the opening time of the hydraulic communication between the high pressure circuit 17 and the low pressure circuit 18 with respect to the uncertainties related to manufacturing tolerances. In a variant, the braking system and / or the depressurization system may be installed at the level of the lower chamber 15.
    Alternatively, the evacuation of the pressure of the emptying compartment 43 may be effected by a peripheral channel formed around the ring 40. In this embodiment, the annular protrusion 41 enters the ring 40 when the striking piston 16 out of the predetermined displacement zone so as to create a emptying compartment 43 whose pressure is sufficient to move the ring 40 around the annular protrusion 41. The pressure of the emptying compartment 43 is evacuated gradually in the chamber actuating the peripheral channel so as to allow the extraction of the annular protrusion 41 and the displacement of the ring 40. During this braking process, a large amount of fluid could be transmitted between the high circuit Pressure 17 and the low pressure circuit 18 via the regulating portion 22.
    FIG. 12 illustrates an eighth embodiment of a striking cell 12f of a device 10f close to that of FIG. 3 but in which there is no compression chamber above the striking piston 16. The upper end of the striking piston 16 is not under pressure and can be connected to the open air. The differences in sections between the upper and lower chambers 14 are more pronounced than for the embodiment of FIG. 3. Thus, the acceleration of the striking piston 16 is created by the high pressure applied to the difference of the sections between the upper chamber 14 and lower 15. A nitrogen accumulator comprises two chambers 50, 51 connected by a deformable membrane. The lower chamber 51 of the nitrogen accumulator is connected to the high-pressure circuit while the upper chamber 50 comprises nitrogen under pressure. The nitrogen accumulator makes it possible to store pressurized fluid during the raising of the striking piston 16 and returns this fluid during the accelerated descent. The invention thus makes it possible to use the increase in the normal stroke of the striking piston 16 when there are overflow to control a transfer of flow from the high pressure circuit 17 to the low pressure circuit 18.
    权利要求:
    Claims (11)
    [1" id="c-fr-0001]
    Rock breaking apparatus (10) comprising: - a striking cell (12) having at least one actuating chamber (14, 15), - a striking piston (16) movable in translation in the striking cell (12). ), and - a hydraulic circuit comprising: - a hydraulic supply source having a high pressure circuit (17) and a low pressure circuit (18), and - an actuator (20) configured to connect the high pressure circuit (17) or the low pressure circuit (18) to the actuating chamber (14, 15) so as to move the piston in translation in the striking cell (12) in a normal displacement zone whose limits are variable depending on the pressure difference between the high pressure circuit (17) and the low pressure circuit (18), characterized in that the striking cell (12) comprises depressurization means configured to control a hydraulic communication of the high pressure circuit (17). ) with the circuit Low P recession (18) when the striking piston (16) emerges from a predetermined displacement zone.
    [2" id="c-fr-0002]
    2. Device according to claim 1, characterized in that the depressurizing means comprise: - a groove (23) disposed on the striking piston (16), and - a regulating portion (22) connected on the one hand to the circuit High pressure (17) and secondly low pressure circuit (18), the control portion (22) being closed by the striking piston (16) when the striking piston (16) is movable in the displacement zone predetermined, - said groove (23) being intended to penetrate into the regulating portion (22) when the striking piston (16) leaves the predetermined displacement zone so as to put the high pressure circuit (17) in hydraulic communication with the low pressure circuit (18) through the regulating portion (22).
    [3" id="c-fr-0003]
    3. Device according to claim 1, characterized in that the depressurization means comprise: - a depressurization valve (32) connected on the one hand to the high pressure circuit (17) and on the other hand to the low pressure circuit (18) , the depressurization valve (32) being able to adopt two positions: a holding position in which the high pressure circuit (17) is disconnected from the low pressure circuit (18), and a depressurization position in which the high pressure circuit (17) is connected to the low pressure circuit (18), - the position of said depressurization valve (32) being controlled by a hydraulic circuit (31), - a regulation portion (22) connected on the one hand to the high pressure circuit (17). ) and on the other hand to the hydraulic circuit (31), the control portion (22) being closed by the striking piston (16) when the striking piston (16) is movable in the predetermined displacement zone so that the circuit hydraulic (31) controls the depressurizing valve (32) in the holding position, and - a groove (23) disposed on the striking piston (16), - said groove (23) being intended to penetrate the control portion (22) when the striking piston (16) exits the predetermined displacement zone so that the hydraulic circuit (31) controls the depressurization valve (32) in the depressurization position.
    [4" id="c-fr-0004]
    4. Device according to claim 1, characterized in that the depressurization means comprise: - a groove (23) and an annular protrusion (41) arranged consecutively on the striking piston (16), and - a regulating portion (22). ) connected on the one hand to the low pressure circuit (18) and on the other hand to the actuating chamber (14, 15), the annular protrusion (41) closing a hydraulic communication channel between the regulating portion (22). ) and the actuating chamber (14, 15) when the striking piston (16) is movable in the predetermined displacement zone, - said groove (23) being intended to penetrate into the actuating chamber (14, 15) when the striking piston (16) leaves the predetermined displacement zone so as to put the actuating chamber (14, 15) in hydraulic communication with the regulating portion (22) through a channel passing through the groove (23). ).
    [5" id="c-fr-0005]
    5. Device according to one of claims 2 to 4, characterized in that the device comprising two actuating chambers (14, 15), an upper actuating chamber (14) and a lower actuating chamber (15). ), the regulating portion (22) is positioned above the upper operating chamber (14).
    [6" id="c-fr-0006]
    6. Device according to one of claims 2 to 4, characterized in that the device comprising two actuating chambers (14, 15), an upper actuating chamber (14) and a lower actuating chamber (15). ), the regulating portion (22) is positioned below the upper operating chamber (14).
    [7" id="c-fr-0007]
    7. Device according to one of claims 2 to 4, characterized in that the device comprising two actuating chambers (14, 15), an upper actuating chamber (14) and a lower actuating chamber (15). ), the regulating portion (22) is positioned between the two actuating chambers (14, 15).
    [8" id="c-fr-0008]
    8. Device according to one of claims 1 to 7, characterized in that it comprises hydraulic braking means (35) of the striking piston (16) configured to slow the stroke of the striking piston (16) when the piston of striking (16) leaves the predetermined displacement zone.
    [9" id="c-fr-0009]
    9. Device according to claim 8, characterized in that the hydraulic braking means (35) comprises a nozzle (37) connected to the low pressure circuit (18) and configured to extract a portion of a hydraulic fluid contained in the means of hydraulic braking (35).
    [10" id="c-fr-0010]
    10. Device according to claim 8 or 9, characterized in that the hydraulic braking means (35) comprise: - a channel (42) connecting the actuating chamber (14, 15) with the low pressure circuit (18), - an annular protrusion (41) disposed on the striking piston (16), and - a ring (40) movable in the actuating chamber (14, 15), - the ring (40) being positioned to close the channel ( 42) when the striking piston (16) is movable in the predetermined displacement zone, - the annular protrusion (41) being intended to penetrate into the ring (40) when the striking piston (16) leaves the zone of predetermined displacement so as to create a drain compartment (43) whose pressure is sufficient to move the ring (40) and establish a hydraulic communication between the emptying compartment (43) and the channel (42), - the annular protrusion (41) being extracted from the ring (40) and the ring (40) being repositioned e to close the channel (42) when the pressure difference between the operating chamber (14, 15) and the emptying compartment (43) is greater than a threshold value.
    [11" id="c-fr-0011]
    11. Device according to claim 8 or 9, characterized in that the hydraulic braking means (35) comprise: - an annular protrusion (41) disposed on the striking piston (16), and - a ring (40) movable in the actuating chamber (14, 15), the annular protrusion (41) being intended to penetrate into the ring (40) when the striking piston (16) leaves the predetermined displacement zone so as to create a compartment emptying means (43) whose pressure is sufficient to move the ring (40) around the annular outgrowth (41), the fluid contained in the emptying compartment (43) being able to reach the actuating chamber (14). , 15) by a peripheral channel formed around the ring (40) when the ring (40) is displaced on the annular protrusion (41) so as to reduce the pressure difference between the emptying compartment (43) and the chamber for actuating (14, 15) and extracting the excrescence ann (41) of the ring (40).
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    同族专利:
    公开号 | 公开日
    CN108367418B|2021-01-08|
    US20180345470A1|2018-12-06|
    FR3044572B1|2017-12-29|
    CN108367418A|2018-08-03|
    EP3383587A1|2018-10-10|
    US10974379B2|2021-04-13|
    WO2017093361A1|2017-06-08|
    KR20180090844A|2018-08-13|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US1846804A|1929-09-06|1932-02-23|Ingersoll Rand Co|Fluid actuated percussive tool|
    US4109734A|1975-11-04|1978-08-29|Roger Montabert|Percussion machine|
    FR2369908A1|1976-11-08|1978-06-02|Montabert Roger|HYDRAULIC PERCUSSION DEVICE|
    GB2074925A|1979-03-16|1981-11-11|Hydroacoustic Inc|Variable Frequency Hydraulically Reciprocated Impact Tool|
    EP2032316A2|2006-06-27|2009-03-11|Montabert S.A.|Percussion equipment driven by a pressurized incompressible fluid|
    WO2011059217A2|2009-11-11|2011-05-19|주식회사 수산중공업|System for preventing idle blow and adjusting hitting power of breaker|
    FR1431835A|1965-01-28|1966-03-18|Montabert Ets|Percussion device|
    SE508064C2|1993-10-15|1998-08-17|Atlas Copco Rock Drills Ab|Rock drilling device with reflex damper|
    JPH08281571A|1995-04-14|1996-10-29|Komatsu Ltd|Vibration generating device|
    DE102004035306A1|2004-07-21|2006-03-16|Atlas Copco Construction Tools Gmbh|Pressure medium operated impact device, in particular hydraulic hammer|
    FR2916377B1|2007-05-25|2009-07-24|Montabert Soc Par Actions Simp|METHOD OF PROTECTING AGAINST FLOW SUPPLY OF A DEVICE WITH MUTE PERCUSSIONS BY AN INCOMPRESSIBLE FLUID UNDER PRESSURE AND APPARATUS FOR CARRYING OUT SAID METHOD|
    SE536711C2|2012-10-29|2014-06-10|Atlas Copco Rock Drills Ab|Damping device for percussion, percussion, rock drill and method of damping at a rock drill|
    CN203500175U|2013-09-30|2014-03-26|湖北江山液压科技有限公司|Constant throttling buffering device of hydraulic cylinder|EP3508308A4|2016-08-31|2019-09-04|Furukawa Rock Drill Co., Ltd.|Hydraulic striking device|
    KR102159191B1|2019-06-04|2020-09-23|성철환경개발|The improved grinder to peel the mortar attached to recycled aggregates|
    KR102223600B1|2019-11-14|2021-03-04|재단법인 한국화학융합시험연구원|The improved multi directional grinder structure|
    法律状态:
    2016-12-23| PLFP| Fee payment|Year of fee payment: 2 |
    2017-06-09| PLSC| Publication of the preliminary search report|Effective date: 20170609 |
    2017-12-23| PLFP| Fee payment|Year of fee payment: 3 |
    2019-12-27| PLFP| Fee payment|Year of fee payment: 5 |
    2020-12-29| PLFP| Fee payment|Year of fee payment: 6 |
    2021-12-28| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1561749A|FR3044572B1|2015-12-02|2015-12-02|ROCK BRISE DEVICE|FR1561749A| FR3044572B1|2015-12-02|2015-12-02|ROCK BRISE DEVICE|
    KR1020187018663A| KR20180090844A|2015-12-02|2016-11-30|Crusher|
    US15/778,884| US10974379B2|2015-12-02|2016-11-30|Rock breaking device|
    PCT/EP2016/079349| WO2017093361A1|2015-12-02|2016-11-30|Rock breaking device|
    CN201680069514.XA| CN108367418B|2015-12-02|2016-11-30|Rock breaking apparatus|
    EP16805096.1A| EP3383587A1|2015-12-02|2016-11-30|Rock breaking device|
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