EP3383587A1 - Rock breaking device - Google Patents
Rock breaking deviceInfo
- Publication number
- EP3383587A1 EP3383587A1 EP16805096.1A EP16805096A EP3383587A1 EP 3383587 A1 EP3383587 A1 EP 3383587A1 EP 16805096 A EP16805096 A EP 16805096A EP 3383587 A1 EP3383587 A1 EP 3383587A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure circuit
- striking piston
- striking
- circuit
- low pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
- 239000011435 rock Substances 0.000 title claims abstract description 23
- 238000004891 communication Methods 0.000 claims abstract description 18
- 238000013519 translation Methods 0.000 claims abstract description 9
- 238000006073 displacement reaction Methods 0.000 claims description 46
- 239000012530 fluid Substances 0.000 claims description 30
- 230000001105 regulatory effect Effects 0.000 claims description 25
- 230000033228 biological regulation Effects 0.000 claims description 15
- 230000002093 peripheral effect Effects 0.000 claims description 4
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 8
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 239000007789 gas Substances 0.000 description 7
- 238000000034 method Methods 0.000 description 4
- 229910052757 nitrogen Inorganic materials 0.000 description 4
- 238000009527 percussion Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000005557 antagonist Substances 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000003116 impacting effect Effects 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
- E02F3/966—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements of hammer-type tools
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D17/00—Details of, or accessories for, portable power-driven percussive tools
- B25D17/24—Damping the reaction force
- B25D17/245—Damping the reaction force using a fluid
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/06—Means for driving the impulse member
- B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/14—Control devices for the reciprocating piston
- B25D9/16—Valve arrangements therefor
- B25D9/18—Valve arrangements therefor involving a piston-type slide valve
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/14—Control devices for the reciprocating piston
- B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2271—Actuators and supports therefor and protection therefor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
- B25D2217/0011—Details of anvils, guide-sleeves or pistons
- B25D2217/0023—Pistons
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/195—Regulation means
Definitions
- the present invention relates to the field of public works machinery. It relates to a percussion hydraulic apparatus type "breaker" or the like.
- hydraulic percussion apparatuses 100 called “breakers” generally consist of a body containing a striking cell 120 protected from the external environment by a welded structure which also ensures the attachment of 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.
- a first phase consists of moving the striking piston 160 in the chamber of compressing 290 by applying pressure in the lower annular chamber 150, thereby compressing the gas in the compression chamber 290.
- a second phase consists in canceling the effect of the pressure in the lower annular chamber 150, supplying the upper annular chamber 140 with substantially the same pressure.
- 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 small.
- 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.
- 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.
- 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.
- 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 .
- 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.
- 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
- the stroke of the striking piston 160 also increases in the compression chamber 290.
- 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.
- 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.
- this solution increases the radial space requirement of the upper part of the pressure cell. hit 120.
- the increase in the size of the impact cell 120 also increases the complexity of assembly and design of the broken rock device.
- 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.
- 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.
- 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 depressurization means comprise:
- a regulation portion connected on the one hand to the high pressure circuit and on the other hand to the low pressure circuit, the regulation portion 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 regulation portion when the striking piston leaves the predetermined displacement zone so as to put the high pressure circuit into hydraulic communication with the low pressure circuit through the regulation portion.
- 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,
- a regulation 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 depressurization valve in the holding position, and
- the depressurization means comprise:
- a regulating portion connected on the one hand to the low pressure circuit and on the other hand to the operating chamber, the annular protrusion closing a hydraulic communication channel between the regulating portion and the actuating chamber when the piston striking is movable in the predetermined displacement zone,
- said groove being intended to penetrate into the actuating chamber when the striking piston leaves the predetermined displacement zone so as to put the actuating chamber into hydraulic communication with the regulating portion through a channel passing through the throat; .
- 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.
- 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.
- 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.
- 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.
- 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.
- the hydraulic braking means comprise:
- the ring being positioned to close the channel when the striking piston is movable in the predetermined displacement zone
- the annular protuberance being intended to penetrate into the ring when the striking piston leaves the predetermined displacement zone so as to create a discharge compartment whose pressure is sufficient to move the ring and to establish a hydraulic communication between the compartment of emptying and the channel,
- 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.
- this embodiment limits the size of the braking system since it is integrated with the actuating chamber.
- the hydraulic braking means (35) comprise:
- the annular protuberance being intended to penetrate into the ring when the striking piston leaves the predetermined displacement zone so as to create a discharge compartment whose pressure is sufficient to move the ring around the annular protuberance
- the fluid contained in the emptying compartment being able to reach the actuating chamber via 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.
- 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.
- FIGS. 1 to 11 represent:
- FIG. 4 a schematic sectional representation of a rock break device according to a second embodiment of the invention.
- FIG. 5 a schematic sectional representation of a rock break device according to a third embodiment of the invention.
- FIG. 6 a schematic sectional representation of a rock break device according to a fourth embodiment of the invention.
- FIG. 7 a schematic sectional representation of a rock break device according to a fifth embodiment of the invention.
- FIG. 8 a schematic sectional representation of a rock break device according to a sixth embodiment of the invention.
- FIG. 9-11 a schematic sectional representation of a rock break device according to a seventh embodiment of the invention.
- FIG. 12 a schematic sectional representation of a rock break device according to an eighth embodiment of the invention.
- FIG. 3 illustrates a hydraulic percussion apparatus 10a called "breaker devices" to be mounted on a carrier 11 as illustrated on FIG. Figure 1.
- the breaker device 10a comprises a striking 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 machine 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.
- 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.
- 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.
- 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.
- 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.
- 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 to the control circuit 21 of the actuator 20.
- the control circuit 21 of FIG. the actuator 20 includes a channel opening into the lower chamber 15 during the rise of the striking piston 16.
- the lower chamber 15 is connected with the high pressure circuit 17 of the hydraulic circuit
- the control circuit 21 is thus connected to the high circuit Pressure 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.
- 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.
- 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.
- 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.
- the first embodiment 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 predetermined displacement zone also corresponds to an operation of the device in which the device cooperates with a tool.
- the invention does not relate to devices to prevent a lack of tools.
- 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.
- 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.
- the control portion 22 is closed by the striking piston 16 when the striking piston 16 is movable in the predetermined displacement zone.
- 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.
- 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 restoring force of the return spring 33.
- two embodiments, illustrated in FIGS. 3 and 4 make it possible to transmit a portion 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 high pressure circuits. 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 extend the stroke of the striking piston 16, for example a few millimeters .
- 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.
- 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 via a nozzle 37.
- This embodiment allows complete stopping 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.
- the surface of the flange 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 according to the pressures maintains the striking piston 16 with a total discharge of the compressible fluid under pressure to the low pressure circuit 18.
- the four embodiments of Figures 3 to 6 illustrate a regulating portion 22 positioned above the upper actuating chamber 14.
- Figure 7 illustrates a fifth embodiment. a striking cell 12e of a device 10e in which the control portion 22 is positioned between the two actuating chambers 14, 15.
- the Figure 8 illustrates a sixth embodiment of a striking cell 12f of a device 10f in which the regulating 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 disposed 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 disposed consecutively with an annular protrusion 41 so that the annular protrusion 41 can cooperate with the regulating portion 22 and hydraulically isolating the regulating portion 22 from the upper chamber 14.
- the annular protrusion 41 blocks any hydraulic communication between the upper chamber 14 and the regulation portion 22.
- the control portion 22 is also connected with the low pressure circuit 18.
- 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 through the control 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 a channel 42 connecting the upper chamber 14 with the low pressure circuit 18.
- 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.
- 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 of 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.
- the striking piston 16 reverses its movement and begins its descent, the ring 40 is redirected upwards to close off again the channel 42.
- the striking piston 16 is released slowly from the ring 40 and the striking piston 16 can resume normal activity.
- the braking system and / or the depressurization system may be installed at the level of the lower chamber 15.
- the evacuation of the pressure of the emptying compartment 43 may be effected by a peripheral channel formed around the ring 40.
- 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 sectional differences between the upper and lower chambers 14 are more pronounced than for the embodiment of FIG. 3.
- 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Automation & Control Theory (AREA)
- Percussive Tools And Related Accessories (AREA)
- Fluid-Pressure Circuits (AREA)
- Crushing And Grinding (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1561749A FR3044572B1 (en) | 2015-12-02 | 2015-12-02 | ROCK BRISE DEVICE |
PCT/EP2016/079349 WO2017093361A1 (en) | 2015-12-02 | 2016-11-30 | Rock breaking device |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3383587A1 true EP3383587A1 (en) | 2018-10-10 |
Family
ID=55236715
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16805096.1A Withdrawn EP3383587A1 (en) | 2015-12-02 | 2016-11-30 | Rock breaking device |
Country Status (6)
Country | Link |
---|---|
US (1) | US10974379B2 (en) |
EP (1) | EP3383587A1 (en) |
KR (1) | KR20180090844A (en) |
CN (1) | CN108367418B (en) |
FR (1) | FR3044572B1 (en) |
WO (1) | WO2017093361A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11084155B2 (en) * | 2016-08-31 | 2021-08-10 | Furukawa Rock Drill Co., Ltd. | Hydraulic striking device |
WO2019022021A1 (en) * | 2017-07-24 | 2019-01-31 | 古河ロックドリル株式会社 | Hydraulic hammering device |
KR102159191B1 (en) | 2019-06-04 | 2020-09-23 | (주)성철환경개발 | The improved grinder to peel the mortar attached to recycled aggregates |
KR102223600B1 (en) | 2019-11-14 | 2021-03-04 | 재단법인 한국화학융합시험연구원 | The improved multi directional grinder structure |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1846804A (en) * | 1929-09-06 | 1932-02-23 | Ingersoll Rand Co | Fluid actuated percussive tool |
FR1431835A (en) * | 1965-01-28 | 1966-03-18 | Montabert Ets | Percussion device |
FR2330507A1 (en) * | 1975-11-04 | 1977-06-03 | Montabert Roger | PERCUSSION MACHINE |
FR2369908A1 (en) * | 1976-11-08 | 1978-06-02 | Montabert Roger | HYDRAULIC PERCUSSION DEVICE |
GB2074925B (en) * | 1979-03-16 | 1983-03-16 | Hydroacoustic Inc | Variable frequency hydraulically reciprocated impact tool |
SE508064C2 (en) * | 1993-10-15 | 1998-08-17 | Atlas Copco Rock Drills Ab | Rock drilling device with reflex damper |
JPH08281571A (en) * | 1995-04-14 | 1996-10-29 | Komatsu Ltd | Vibration generating device |
DE102004035306A1 (en) * | 2004-07-21 | 2006-03-16 | Atlas Copco Construction Tools Gmbh | Pressure medium operated impact device, in particular hydraulic hammer |
FR2902684B1 (en) * | 2006-06-27 | 2010-02-26 | Montabert Roger | METHOD FOR SWITCHING THE STROKE STROKE OF A MU-PERCUSSION APPARATUS BY AN INCOMPRESSIBLE FLUID UNDER PRESSURE, AND APPARATUS FOR CARRYING OUT SAID METHOD |
FR2916377B1 (en) | 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 |
KR101072069B1 (en) * | 2009-11-11 | 2011-10-10 | 주식회사수산중공업 | A System for batting Control and no batting of Constrbattinguction Machine |
SE536711C2 (en) * | 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 (en) * | 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 |
-
2015
- 2015-12-02 FR FR1561749A patent/FR3044572B1/en not_active Expired - Fee Related
-
2016
- 2016-11-30 EP EP16805096.1A patent/EP3383587A1/en not_active Withdrawn
- 2016-11-30 KR KR1020187018663A patent/KR20180090844A/en active IP Right Grant
- 2016-11-30 CN CN201680069514.XA patent/CN108367418B/en not_active Expired - Fee Related
- 2016-11-30 US US15/778,884 patent/US10974379B2/en active Active
- 2016-11-30 WO PCT/EP2016/079349 patent/WO2017093361A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
KR20180090844A (en) | 2018-08-13 |
CN108367418B (en) | 2021-01-08 |
US10974379B2 (en) | 2021-04-13 |
US20180345470A1 (en) | 2018-12-06 |
CN108367418A (en) | 2018-08-03 |
FR3044572A1 (en) | 2017-06-09 |
WO2017093361A1 (en) | 2017-06-08 |
FR3044572B1 (en) | 2017-12-29 |
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