WO2017010400A1 - 液圧式打撃装置 - Google Patents
液圧式打撃装置 Download PDFInfo
- Publication number
- WO2017010400A1 WO2017010400A1 PCT/JP2016/070155 JP2016070155W WO2017010400A1 WO 2017010400 A1 WO2017010400 A1 WO 2017010400A1 JP 2016070155 W JP2016070155 W JP 2016070155W WO 2017010400 A1 WO2017010400 A1 WO 2017010400A1
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- WIPO (PCT)
- Prior art keywords
- piston
- chamber
- striking device
- hydraulic striking
- pressure
- Prior art date
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Classifications
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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
- B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/14—Control devices for the reciprocating piston
- B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D2209/002—Pressure accumulators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/005—Adjustable tool components; Adjustable parameters
- B25D2250/021—Stroke length
Definitions
- the present invention relates to a hydraulic hitting device such as a rock drill or a breaker.
- Patent Document 1 a technique described in Patent Document 1 is disclosed as this type of hydraulic striking device.
- the hydraulic striking device described in this document includes, for example, a cylinder 100P, a front head 300, and a back head 400P, and a piston 200 is slidably fitted in the cylinder 100P as illustrated in FIG.
- the front head 300 is disposed on the front side of the cylinder 100, and the rod 310 is slidably fitted so as to be capable of moving forward and backward.
- a striking chamber 301 is formed inside the front head 300, and the tip of the piston 200 strikes the rear end of the rod 310 in the striking chamber 301.
- the back head 400P is disposed on the rear side of the cylinder 100, and the rear end of the piston 200 moves back and forth in a retreat chamber 401P formed inside the back head 400P.
- the piston 200 is a solid cylindrical body, and has large-diameter portions 201 and 202 at substantially the center thereof.
- a medium diameter portion 203 is provided on the front side of the large diameter portion 201, and a small diameter portion 204 is provided on the rear side of the large diameter portion 202.
- An annular valve switching groove 205 is formed in the approximate center of the large diameter portions 201 and 202.
- the outer diameter of the piston middle diameter portion 203 is set larger than the outer diameter of the piston small diameter portion 204.
- the pressure receiving area of the piston 200 in the piston front chamber 110 and the piston rear chamber 111 described later that is, the diameter difference between the large diameter portion 201 and the medium diameter portion 203 and the diameter difference between the large diameter portion 202 and the small diameter portion 204 are
- the rear chamber 111 side is larger (hereinafter referred to as a pressure receiving area difference).
- the piston 200 is slidably fitted into the cylinder 100, so that a piston front chamber 110 and a piston rear chamber 111 are defined in the cylinder 100, respectively.
- the piston front chamber 110 is always connected to the high-pressure circuit 101 via the piston front chamber passage 120.
- the piston rear chamber 111 can be alternately communicated with the high pressure circuit 101 and the low pressure circuit 102 via the piston rear chamber passage 121 by switching a switching valve mechanism 130 described later.
- the high pressure circuit 101 is connected to the pump P, and a high pressure accumulator 140 is provided in the middle of the high pressure circuit 101.
- the low pressure circuit 102 is connected to the tank T, and a low pressure accumulator 141 is provided in the middle of the low pressure circuit 102.
- the switching valve mechanism 130 is a known switching valve that is disposed at appropriate positions inside and outside the cylinder 100P, and is operated by pressure oil supplied and discharged from a valve control passage 122 described later, and makes the piston rear chamber 111 high and low pressure. Switch alternately.
- a piston forward control port 112 Between the piston front chamber 110 and the piston rear chamber 111, a piston forward control port 112, a piston reverse control port 113, and an oil discharge port 114 are provided at predetermined intervals from the front to the rear. .
- a passage branched from the valve control passage 122 is connected to the piston forward control port 112 and the piston backward control port 113, respectively.
- the oil drain port 114 is connected to the tank T via the oil drain passage 123.
- the piston forward control port 112 has a front short stroke port 112a and a rear long stroke port 112b.
- a short stroke is achieved by operating a variable throttle 112c provided between the short stroke port 112a and the valve control passage 122. It is possible to switch between a long stroke and a long stroke. When the variable aperture 112c is fully opened, a short stroke is obtained, and when the variable throttle 112c is fully closed, a long stroke is obtained.
- the switching valve mechanism 130 When the piston advance control port 112 communicates with the piston front chamber 110 and pressure oil is supplied to the valve control passage 122, the switching valve mechanism 130 is switched to a position where the piston rear chamber passage 121 communicates with the high pressure circuit 101. Further, the switching valve mechanism 130 communicates the piston rear chamber passage 121 to the low pressure circuit 102 when the piston reverse control port 113 communicates with the oil discharge port 114 and the pressure oil is discharged from the valve control passage 122 to the tank T. It is switched to the position to do.
- the piston advance control port 112 is provided with the long stroke port 112b and the short stroke port 112a.
- the number of hits can be increased more than the long stroke setting.
- FIG. 10 shows a piston stroke-speed diagram of a long stroke and a short stroke in a conventional hydraulic striking device.
- the dotted line is a long stroke setting diagram
- L1 is the full stroke
- L2 is the piston retraction acceleration section (the piston advance control port communicates with the piston front chamber after the piston starts retreating)
- the valve is L3 is the piston reverse deceleration zone (until the piston rear chamber is switched to high pressure and the piston reaches the rear stroke end)
- Vlong is the piston speed at the striking point.
- the solid line is a diagram for setting a short stroke, and similarly, L1 ′ is a full stroke, L2 ′ is a piston reverse acceleration section, L3 ′ is a piston reverse deceleration section, and Vshort is a piston speed at an impact point.
- the present invention has been made paying attention to such problems, and provides a hydraulic striking device capable of increasing the striking output by shortening the piston stroke while maintaining the striking energy. Is an issue.
- a hydraulic striking device includes a cylinder, a piston slidably fitted in the cylinder, an outer peripheral surface of the piston, and an inner peripheral surface of the cylinder.
- the piston front chamber and the piston rear chamber which are defined between and separated from each other in the axial direction, and at least one of the piston front chamber and the piston rear chamber is switched to at least one of a high pressure circuit and a low pressure circuit.
- a switching valve mechanism for driving the piston, and abutting the piston during the retreating process of the piston, and the piston is moved forward in cooperation with a braking force by pressure oil acting on the piston.
- biasing means for biasing is provided for biasing.
- the urging unit abuts on the piston at a timing when a braking force by pressure oil acts on the piston during the retreating process of the piston.
- the urging means is a speed increasing piston that generates thrust by pressure oil supplied from the high pressure circuit.
- the urging means is a speed increasing piston that generates a thrust by a gas pressure filled in a closed space.
- the urging means is provided at the rear of the piston, and the urging means abuts on the piston during the retreating process of the piston, and the braking force by the pressure oil acting on the piston. Since the piston is urged forward in cooperation with the above, the backward stroke of the piston is shortened and the forward movement of the piston is accelerated. As a result, the piston speed does not decrease, and high output is possible. Therefore, according to the hydraulic striking device according to the present invention, the striking output can be increased by shortening the piston stroke while maintaining the striking energy.
- the hydraulic striking device it is preferable to include an operation selection unit that retracts the urging unit to a position where it does not contact the piston when the urging unit is not operated.
- the switching valve mechanism is configured to drive at least the piston rear chamber alternately between the high pressure circuit and the low pressure circuit to drive the piston, and the pressure oil supply passage to the speed increasing piston includes It is preferable to be branched from a passage for supplying pressure oil to the piston rear chamber.
- a biasing accumulator is provided at a position close to the biasing means in a pressure oil supply passage from the high-pressure circuit to the biasing means. Further, in the hydraulic striking device according to one aspect of the present invention, the pressure oil supply passage is provided at a position closer to the pressure oil supply source than the biasing accumulator and close to the biasing accumulator. It is preferable to provide a direction regulating means that allows only the supply of pressure oil to the biasing means.
- FIG. 3 is a schematic diagram ((a) to (d)) showing an operating state of the first embodiment. It is a piston stroke-speed diagram of a first embodiment. It is a schematic diagram of 2nd embodiment of the hydraulic striking device which concerns on 1 aspect of this invention. It is a schematic diagram of 3rd embodiment of the hydraulic striking device which concerns on 1 aspect of this invention. It is a schematic diagram of 4th embodiment of the hydraulic striking device which concerns on 1 aspect of this invention. It is a schematic diagram of 5th embodiment of the hydraulic striking device which concerns on 1 aspect of this invention. It is a schematic diagram of 6th embodiment of the hydraulic striking device which concerns on 1 aspect of this invention. It is a schematic diagram of the conventional hydraulic striking device. It is a piston stroke-speed diagram of the conventional hydraulic striking device.
- the hydraulic striking device includes a cylinder 100, a front head 300, and a back head 400, and a piston 200 is slidably fitted in the cylinder 100.
- the piston 200 is a solid cylindrical body, and has large-diameter portions 201 and 202 at substantially the center thereof.
- a medium diameter portion 203 is provided on the front side of the large diameter portion 201, and a small diameter portion 204 is provided on the rear side of the large diameter portion 202.
- An annular valve switching groove 205 is formed in the approximate center of the large diameter portions 201 and 202.
- the outer diameter of the piston middle diameter portion 203 is set larger than the outer diameter of the piston small diameter portion 204.
- the pressure receiving area of the piston 200 in the piston front chamber 110 and the piston rear chamber 111 described later that is, the diameter difference between the large diameter portion 201 and the medium diameter portion 203 and the diameter difference between the large diameter portion 202 and the small diameter portion 204 are The chamber 111 side is larger.
- the piston 200 is slidably fitted into the cylinder 100, whereby a piston front chamber 110 and a piston rear chamber 111 are defined in the cylinder 100, respectively.
- the piston front chamber 110 is always connected to the high-pressure circuit 101 via the piston front chamber passage 120.
- the piston rear chamber 111 can be alternately communicated with the high pressure circuit 101 and the low pressure circuit 102 via the piston rear chamber passage 121 by switching a switching valve 1300 described later.
- the high pressure circuit 101 is connected to the pump P, and a high pressure accumulator 140 is provided in the middle of the high pressure circuit 101.
- the low pressure circuit 102 is connected to the tank T, and a low pressure accumulator 141 is provided in the middle of the low pressure circuit 102.
- the switching valve mechanism 130 is a known switching valve that is disposed at appropriate positions inside and outside the cylinder 100, and is operated by pressure oil supplied and discharged from a valve control passage 122 described later, and causes the piston rear chamber 111 to have a high pressure and a low pressure. Switch alternately.
- a piston forward control port 112 Between the piston front chamber 110 and the piston rear chamber 111, a piston forward control port 112, a piston reverse control port 113, and an oil discharge port 114 are provided at predetermined intervals from the front to the rear. .
- a passage branched from the valve control passage 122 is connected to the piston forward control port 112 and the piston backward control port 113, respectively.
- the oil drain port 114 is connected to the tank T via the oil drain passage 123.
- the piston advance control port 112 has a front short stroke port 112a and a rear long stroke port 112b.
- the piston advance control port 112 can be switched between a short stroke and a long stroke without a step by operating a variable throttle 112b provided between the short stroke port 112a and the valve control passage 122.
- a variable aperture 112c When the variable aperture 112c is fully opened, a short stroke is obtained, and when the variable throttle 112c is fully closed, a long stroke is obtained.
- the front head 300 is disposed on the front side of the cylinder 100, and the rod 310 is slidably fitted so as to be able to advance and retreat.
- the tip of the piston 200 strikes the rear end of the rod 310 in the striking chamber 301 formed inside the front head 300.
- the back head 400 is disposed on the rear side of the cylinder 100. Inside the back head 400, a retracting chamber 401 and a pressurizing chamber 402 are formed behind the retracting chamber 401.
- the inner diameter of the retracting chamber 401 is set so that there is no influence when the piston small-diameter portion 204 moves back and forth, and the inner diameter of the pressurizing chamber 402 is set larger than the inner diameter of the retracting chamber 401.
- An end face 403 is formed at the boundary between the retreat chamber 401 and the pressurizing chamber 402.
- the pressurizing chamber 402 is fitted with a speed increasing piston 410 as an urging means.
- the speed increasing piston 410 has a front small diameter portion 411 and a rear large diameter portion 412.
- a stepped surface 413 is formed at the boundary between the small diameter portion 411 and the large diameter portion 412.
- the large-diameter portion 412 is in sliding contact with the inner diameter of the pressurizing chamber 402, and the end surface 403 and the stepped surface 413 are in contact with each other, thereby defining a hydraulic chamber on the rear side of the large-diameter portion 412 in the pressurizing chamber 402.
- the hydraulic chamber is always connected to the high-pressure circuit 101 by a pressurizing passage 404.
- the striking interface between the piston 200 and the rod 310 that is, the outer diameter of the piston inner diameter portion 203 and the rear end portion of the rod 310 is set to the same size.
- the reason is to increase the transmission efficiency of the stress wave generated when the piston 200 strikes the rod 310.
- the outer diameter of the small diameter portion 411 of the speed increasing piston 410 is smaller than the piston small diameter.
- the outer diameter of the portion 204 is set to be substantially the same.
- FIG. 2 a portion where the circuit is connected to a high voltage is indicated by a thick solid line and shaded area.
- the piston 200 since the piston front chamber 110 is always connected to high pressure, the piston 200 is always urged backward, and the piston rear chamber 111 is connected to high pressure by the operation of the switching valve mechanism 130.
- the piston 200 moves forward due to the pressure receiving area difference, and when the piston rear chamber 111 is connected to the low pressure by the operation of the switching valve mechanism 130, the piston 200 moves backward.
- the switching valve mechanism 130 switches the piston rear chamber passage 121 to a position communicating with the high pressure circuit 101.
- the reverse control port 113 communicates with the oil discharge port 114 and the pressure oil is discharged from the valve control passage 122 to the tank T, the piston rear chamber passage 121 is switched to a position communicating with the low pressure circuit 102.
- the piston advance control port is set to a long stroke with the variable throttle 112c fully closed.
- the striking mechanism of the hydraulic striking device is characterized in that a speed increasing piston 410 is provided on the back head 400 with respect to the conventional hydraulic striking device. That is, in FIG. 2, at the same time as the piston 200 hits the rod 310 shown in FIG. 2D, the pilot chamber (not shown) of the switching valve mechanism 130 is lowered to the low pressure through the valve control passage 122 and the oil discharge passage 123. Since the internal spool is switched because the connection is made and the piston rear chamber passage 121 is connected to the low pressure circuit 102, the piston rear chamber 111 becomes low pressure, so that the piston 200 starts to move backward. (See the figure (a))
- the piston advance control port 112 is opened and the switching valve mechanism 130 is switched, and the piston 200 comes into contact with the speed increasing piston 410 at a timing when the piston rear chamber 111 becomes high pressure.
- the piston 200 adds the thrust (referred to as “normal thrust”) due to the difference in pressure receiving area between the front chamber 110 and the rear chamber 111 (referred to as “normal thrust”) to the piston 200 (referred to as “additional thrust”). It works (see FIG. 2B).
- the speed increasing piston 410 abuts on the piston 200 during the retraction process of the piston 200 and applies the piston 200 forward in cooperation with the normal thrust (braking force) by the pressure oil acting on the piston 200.
- the added thrust force is applied to the piston 200.
- the piston 200 continues to move backward due to inertia.
- the piston 200 moves from backward to forward at a position ahead of the normal rear stroke end. Turn.
- the pressure oil discharged from the pressurizing chamber 402 is accumulated in the high-pressure accumulator 140 (see FIG. 5C).
- the piston 200 Immediately after the piston 200 turns forward, the pressure oil accumulated in the high-pressure accumulator 140 is supplied to the pressurizing chamber 402. Therefore, the piston 200 is urged by the acceleration piston 410 and accelerates quickly. Eventually, when the stepped surface 413 comes into contact with the end surface 403 and reaches the front stroke end of the speed increasing piston 410, the piston 200 moves away from the speed increasing piston 410 only by normal thrust and hits the rod 310 ( (See (d) in the figure). Thereafter, the above cycle is repeated.
- FIG. 3 shows a piston stroke-speed diagram in the hydraulic striking device of the present embodiment.
- the case where the speed increasing piston 410 of this embodiment is not provided is also indicated by a broken line.
- the conventional piston stroke-velocity diagram without the speed increasing piston 410 has the same profile as the long stroke diagram in FIG. 10, and the dotted line is used for the display as in FIG. ⁇ L3.
- the striking mechanism operates as a long stroke specification, and the piston 200 is a rod. It can be seen that there is no change in the speed V1 when hitting 310 and the maximum speed V2 during reverse.
- the difference depending on the presence or absence of the acceleration piston 410 of the present embodiment is only the stroke of the section where the piston 200 is in contact with the acceleration piston 410, and the stroke of the contact section is shortened from L3 to LB3. is doing. Therefore, the entire stroke is shortened from L1 to LB1.
- the speed increasing piston 410 temporarily enlarges the pressure receiving area of the piston rear chamber 111 only in a part of the piston reverse stroke, that is, only in the LB3 section process from the deceleration reverse to the rear stroke end to the acceleration forward. It can be said that the mechanism.
- the pressure receiving area increases, so that the braking force increases and the piston 200 stops the retreat operation in a short time. At this time, the time during which the pressure oil discharged from the rear chamber 111 and the pressurizing chamber 402 is accumulated in the high-pressure accumulator 140 is also shortened.
- the stroke is shortened by shortening the recovery / release time of the kinetic energy by the high-pressure accumulator 140 as compared with the hydraulic striking device that does not include the speed increasing piston 410.
- the cycle time 2T b in the phase of the LB3 section where the piston 200 abuts on the speed increasing piston 410 and is braked and stopped, and then turns forward and accelerates is the speed increasing piston 410.
- a conventional hydraulic striking device not equipped with a cycle time 2T p in the L3 section 2 (1 + a) A p / (A p + A b ) T p , so that a short stroke is possible.
- the mass ratio a of the speed increasing piston 410 against the piston 200 is small, also the short-stroke becomes possible larger the pressure receiving area A b of the speed increasing piston 410.
- the short stroke is performed by collecting and releasing kinetic energy by the high-pressure accumulator 140, so that no additional power is required. Furthermore, when designing the actual apparatus, the weight ratio a of the speed increasing piston 410 against the piston 200 is negligibly small, i.e. it is preferably set as small as possible mass m b of the speed increasing piston 410.
- the speed V1 when the piston 200 strikes the rod 310 does not change even if the stroke is shortened. Therefore, since the number of hits is increased without reducing the hit energy per hit, the output of the hitting mechanism can be increased.
- the pressurizing chamber 402 ′ is formed with a closed space by the back head 400 and the large-diameter portion 412 of the speed increasing piston 410 compared to the first embodiment described above. Is different.
- the pressurizing chamber 402 ′ is filled with high-pressure gas, and the acceleration piston 410 is thrust forward by this gas pressure.
- the reverse stroke of the acceleration piston 410 is regulated by an annular end surface 408.
- Other configurations are the same as those in the first embodiment. According to the second embodiment, since the hydraulic circuit is not required for the urging means, the configuration of the hydraulic striking device can be simplified.
- the inner diameter of the back head 400 is more forward than the boundary between the retreat chamber 401 and the pressurizing chamber 402 (that is, the end surface 403).
- a partition wall 405 slidably in contact with the diameter is formed, and a switching chamber 405 a is provided on the partition wall 405 on the pressure chamber 402 side.
- a switching passage 406 is connected to the switching chamber 405a, and the switching passage 406 and the pressurizing passage 404 communicate with either the high-pressure circuit 101 or the low-pressure circuit 102 via the switching valve mechanism 420.
- Other configurations are the same as those in the first embodiment.
- the switching valve mechanism 420 in the state where the switching valve mechanism 420 is in the position shown in FIG. 5, it is possible to operate the acceleration piston 410 as described above to shorten the striking mechanism.
- the switching valve mechanism 420 when the switching valve mechanism 420 is switched from the position shown in FIG. 5 to the state shown in the lower part of FIG. 5, pressure oil is supplied to the switching chamber 405a, so that the acceleration piston 410 retreats to the rear stroke end.
- the striking mechanism can be operated with a normal stroke so as not to contact the piston 200. That is, the additional component part of this modification functions as an operation selection means (on / off switch) of the speed increasing piston 410.
- the pressurizing chamber 402 is connected to the piston rear chamber passage 121 via the pressurizing passage 407.
- Other configurations are the same as those in the first embodiment.
- the pressurizing passage 407 that is a pressure oil supply passage to the speed increasing piston 410 is provided to be branched from the piston rear chamber passage 121 that supplies the pressure oil to the piston rear chamber 111. Therefore, supply and discharge of pressure oil to and from the pressurizing chamber 402 and the rear chamber 111 are performed in synchronization. Therefore, the timing at which the above-described acceleration piston 410 is actuated can be exactly matched with the reverse deceleration stroke start timing of the piston 200. Therefore, before the piston 200 starts decelerating, the piston 200 and the acceleration piston 410 do not collide and energy is not wasted.
- a biasing accumulator 142 is provided in the pressurizing passage 404 ′ connecting the pressurizing chamber 402 and the high pressure circuit 101 in the vicinity of the pressurizing chamber 402.
- Other configurations are the same as those in the first embodiment.
- the piston 200 abuts on the speed increasing piston 410 during the retreating process, and the braking force and pressure increase due to the pressure oil acting on the piston 200 are increased.
- the forward thrust acting on the high speed piston 410 cooperates to urge the piston 200 forward, thereby shortening the piston stroke. Therefore, when the piston 200 comes into contact with the speed increasing piston 410, an impact is accompanied.
- the biasing accumulator 142 is provided closer to the pressurizing chamber 402 than the high-pressure accumulator 140. , And the impact accumulator 142 absorbs the impact more effectively than the high pressure accumulator 140. Therefore, the operation of the switching valve mechanism 130 is not adversely affected. Further, when the volume of the pressurizing chamber 402 is suddenly changed due to the displacement of the acceleration piston 410, the biasing accumulator 142 can absorb and release the oil with a lower pipe resistance than the high-pressure accumulator 140. .
- the passage area is smaller than the pressure receiving area means that the pressure loss is large. That is, it can be said that the pressure passage 404 has a relatively large pressure loss with respect to the high pressure passage 121.
- the speed increasing action of the present invention is performed in a phase where the piston 200 and the speed increasing piston 410 move forward integrally. Although there is a possibility that it may not be sufficiently exhibited, increasing the passage area as a countermeasure is limited in terms of cost and layout.
- a biasing accumulator 142 is provided in the pressurizing passage 404 ′′ connecting the pressurizing chamber 402 and the high pressure circuit 101 in the vicinity of the pressurizing chamber 402. Further, on the upstream side of the urging accumulator 142 (that is, the pump P side that is the supply source of pressure oil), a check is made as a direction restricting means that allows only supply of pressure oil to the pressure chamber 402 side. A valve 143 is provided. Other configurations are the same as those in the first embodiment.
- the check valve 143 by providing the check valve 143, it is possible to suppress the backflow of oil to the pressurizing passage 404 ′′, and the utilization efficiency of the biasing accumulator 142 is dramatically increased. Therefore, the urging accumulator 142 can play a more active role as a pressure oil supply source for demonstrating the speed increasing action of the present invention. Therefore, the pressurizing passage 404 ′′ does not need to take pressure loss into consideration, and the passage area can be set small. Further, the use efficiency of the urging accumulator 142 is improved by the check valve 143, so that the impact buffering action of the pressure oil in the pressurizing chamber 402 is effectively performed.
- the piston is not limited to a solid shape, and a through hole or a blind hole may be formed in the axial center of the piston.
- the large diameter part before and behind a piston may provide a diameter difference instead of the same outer diameter.
- the outer diameter of the small diameter portion of the speed increasing piston may not be aligned with the outer diameter of the piston middle diameter portion.
- the timing at which the piston contacts the acceleration piston may be slightly different from the timing at which the piston rear chamber switches to high pressure.
- the hydraulic striking device is a so-called “rear chamber high / low pressure switching type” hydraulic type in which the piston front chamber is always at a high pressure and the piston rear chamber is switched to high / low pressure to move the piston forward and backward.
- the impact device has been described as an example, the present invention is not limited to this.
- the hydraulic striking device is a so-called “front / rear chamber high / low pressure switching type” hydraulic striking device in which the piston front chamber and the piston rear chamber are alternately switched between high pressure and low pressure to advance and retreat the piston.
- the piston rear chamber is always at high pressure, and the piston front chamber is switched between high pressure and low pressure to move the piston forward and backward, so-called “front chamber high / low pressure switching type” hydraulic striking device It is also applicable to.
- the hydraulic striking device of the fourth embodiment shown in FIG. 6 is a “rear chamber high / low pressure switching type” or “front / rear chamber high / low pressure switching type” hydraulic type that switches the piston rear chamber between high pressure and low pressure. Only when applied to the striking device, the function and effect of synchronizing with the rear chamber are exhibited.
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- Automation & Control Theory (AREA)
- Percussive Tools And Related Accessories (AREA)
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Abstract
Description
これにより、後述するピストン前室110およびピストン後室111におけるピストン200の受圧面積、すなわち大径部201と中径部203の径差、および大径部202と小径部204の径差は、ピストン後室111側の方が大きくなっている(以下、受圧面積差という)。
同図において、点線がロングストローク設定の線図であり、L1が全ストローク、L2がピストン後退加速区間(ピストンが後退を開始してから、ピストン前進制御ポートがピストン前室と連通してバルブが切換えられてピストン後室が高圧に切換えられるまで)、L3がピストン後退減速区間(ピストン後室が高圧に切換えられてピストンが後方ストロークエンドに到るまで)、Vlongが打撃点におけるピストン速度である。また、実線がショートストローク設定の線図であり、同様に、L1´が全ストローク、L2´がピストン後退加速区間、L3´がピストン後退減速区間、Vshortが打撃点におけるピストン速度である。
また、本発明の一態様に係る液圧式打撃装置において、前記付勢手段は、前記高圧回路から供給される圧油によって推力が発生する増速ピストンであることは好ましい。
また、本発明の一態様に係る液圧式打撃装置において、前記付勢手段は、閉空間内に充填されたガス圧により推力が発生する増速ピストンであることは好ましい。
また、前記切換弁機構は、少なくとも前記ピストン後室を前記高圧回路と前記低圧回路とに交互に切換えて前記ピストンを駆動するように構成され、前記増速ピストンへの圧油供給通路は、前記ピストン後室に圧油を供給する通路から分岐して設けられていることは好ましい。
また、本発明の一態様に係る液圧式打撃装置において、前記圧油供給通路に、前記付勢アキュムレータよりも圧油供給源側であり、かつ、前記付勢アキュムレータに近接する位置に、前記付勢手段への圧油の供給のみを許容する方向規制手段を設けることは好ましい。
ピストン200は、中実の円筒体であり、その略中央に大径部201、202を有する。大径部201の前側には中径部203が、大径部202の後側には小径部204がそれぞれ設けられている。大径部201と202の略中央には、円環状のバルブ切換溝205が形成されている。
ピストン中径部203の外径は、ピストン小径部204の外径よりも大きく設定されている。これにより、後述するピストン前室110およびピストン後室111におけるピストン200の受圧面積、すなわち大径部201と中径部203の径差、および大径部202と小径部204の径差はピストン後室111側の方が大きくなっている。
バックヘッド400は、シリンダ100の後側に配設されている。バックヘッド400の内部には、後退室401およびその後方に加圧室402が形成されている。後退室401の内径は、ピストン小径部204が前後移動する際に影響が無いように設定され、加圧室402の内径は、後退室401の内径よりも径大に設定されている。後退室401と加圧室402の境界には端面403が形成されている。
すなわち、図2において、同図(d)に示す、ピストン200がロッド310を打撃すると同時に、切換弁機構130のパイロット室(不図示)は、バルブ制御通路122および排油通路123を経て低圧に接続されるため内部のスプールが切換り、ピストン後室通路121を低圧回路102に連通することでピストン後室111が低圧となるのでピストン200は後退動作を開始する。(同図(a)参照)
ピストン200の減速後退時に受圧面積が拡大することで制動力が増大して短時間でピストン200は後退動作を停止する。この時、後室111と加圧室402から排出される圧油が高圧アキュムレータ140に蓄圧される時間も短縮される。
-mpVp=Fp・Tp
一方、増速ピストンを追加した本発明の液圧式打撃装置でピストン200が図3のLB3区間の速度V2からゼロに至る後退減速行程において、この間に高圧アキュムレータ140がピストン200及び増速ピストン410に作用する力をFb、作用する時間をTbとすると、ピストン200とピストン410に作用する力積と運動量の変化は、
-(mp+mb)Vp=Fb・Tb
ここで、mb=a・mpと置くと、
-(mp+mb)Vp=-(1+a)mp・Vp=(1+a)Fp・Tp=Fb・Tb
∴ Tb=(1+a)(Fp/Fb)Tp
ここで、ピストン200の前室110と後室111の受圧面積差をAp、増速ピストン410大径部412の受圧面積をAb、油圧をΔPとすると、
Fp=Ap・ΔP
Fb=(Ap+Ab)ΔP
∴Tb=(1+a)Ap/(Ap+Ab)Tp
因みに、従来の液圧式打撃装置のL3区間の前進加速行程の所要時間、並びに本発明の液圧打撃装置のLB3区間の前進加速行程の所要時間は同様に各々Tp、Tbとなる。
なお、このショートストローク化は、高圧アキュムレータ140よる運動エネルギーの回収・放出によって行われるので追加の動力は必要としない。また、実際の装置を設計する際には、ピストン200に対する増速ピストン410の質量比aは無視し得るほど小さく、すなわち増速ピストン410の質量mbを可能な限り小さく設定することが好ましい。
同図に示すように、この第二実施形態においては、加圧室402´は、上述した第一実施形態に対し、バックヘッド400と増速ピストン410の大径部412とによって閉空間が形成されている点が異なる。
第二実施形態では、加圧室402´には高圧ガスが充填されており、増速ピストン410はこのガス圧によって前方へと推力が付与されている。増速ピストン410の後退ストロークは、円環状の端面408によって規制されている。それ以外の構成は、上記第一実施形態と同じである。
この第二実施形態によれば、付勢手段に油圧回路を必要としないので、液圧式打撃装置の構成を簡素化することができる。
同図に示すように、この第三実施形態は、バックヘッド400において、後退室401と加圧室402の境界(つまり端面403)よりも前方に、その内径が増速ピストン小径部411の外径と摺接する隔壁405を形成し、隔壁405の加圧室402側に切換室405aを設けている。切換室405aには切換通路406が接続されており、切換通路406と加圧通路404とは、切換弁機構420を介して高圧回路101と低圧回路102のいずれかに連通するようになっている。それ以外の構成は、上記第一実施形態と同じである。
同図に示すように、第四実施形態においては、加圧室402は、加圧通路407を介してピストン後室通路121に接続されている。それ以外の構成は第一実施形態と同じである。
同図に示すように、第五実施形態においては、加圧室402と高圧回路101を接続する加圧通路404´に、加圧室402に近接して付勢アキュムレータ142が設けられている。それ以外の構成は第一実施形態と同じである。
それに対して、図7に示すように、この第五実施形態においては、付勢アキュムレータ142が高圧アキュムレータ140よりも加圧室402に近接して設けられているので、ピストン200と増速ピストン410とが衝突して加圧室402の圧油に衝撃が伝搬した場合、付勢アキュムレータ142は高圧アキュムレータ140よりも効果的に衝撃を緩衝する。そのため、切換弁機構130の作動に悪影響を及ぼすことはない。また、増速ピストン410の変位により加圧室402の容積が急激に変動した場合、付勢アキュムレータ142は高圧アキュムレータ140よりも低い管路抵抗でその分の油の吸収・放出を行うことができる。
ここで、全ての油圧回路において、通路面積は大きいほど圧力損失が少なくなり油圧効率が向上するところ、図1に示した第一実施形態の液圧式打撃装置において、高圧通路121と後室111の受圧面積の関係と、加圧通路404と加圧室402の受圧面積の関係とに着目すると、仮に、高圧通路121と加圧通路404の通路面積を同じに設定した場合、受圧面積に対する通路面積は、加圧通路404側の方が小さいことが見て取れる。
101 高圧回路
102 低圧回路
110 ピストン前室
111 ピストン後室
112 ピストン前進制御ポート
112a ショートストロークポート
112b ロングストロークポート
112c 可変絞り
113 ピストン後退制御ポート
114 排油ポート
120 ピストン前室通路
121 ピストン後室通路
122 バルブ制御通路
123 排油通路
130 切換弁機構
140 高圧アキュムレータ
141 低圧アキュムレータ
142 付勢アキュムレータ
143 逆止弁(方向規制手段)
200 ピストン
201 大径部(前)
202 大径部(後)
203 中径部
204 小径部
205 バルブ切換溝
300 フロントヘッド
301 打撃室
310 ロッド
400 バックヘッド
401 後退室
402 加圧室
402´ 加圧室
404´、404´´ 加圧通路
403 端面
404 加圧通路
405 隔壁
405a 切換室
406 切換通路
407 加圧通路
410 増速ピストン(付勢手段)
411 小径部
412 大径部
413 段付面
420 切換弁機構
P ポンプ
T タンク
Claims (8)
- シリンダと、該シリンダの内部に摺嵌されたピストンと、該ピストンの外周面と前記シリンダの内周面との間に画成されて軸方向の前後に離隔配置されたピストン前室およびピストン後室と、前記ピストン前室および前記ピストン後室の少なくとも一方を高圧回路および低圧回路の少なくとも一方に切換えて前記ピストンを駆動する切換弁機構と、前記ピストンの後方に設けられ、前記ピストンの後退工程中に前記ピストンに当接して、前記ピストンに作用する圧油による制動力と協働して前記ピストンを前方へと付勢する付勢手段とを備えることを特徴とする液圧式打撃装置。
- 前記付勢手段は、前記ピストンの後退工程中に、前記ピストンに圧油による制動力が作用するタイミングで前記ピストンに当接する請求項1に記載の液圧式打撃装置。
- 前記付勢手段は、前記高圧回路から供給される圧油によって推力が発生する増速ピストンである請求項1または2に記載の液圧式打撃装置。
- 前記付勢手段は、閉空間内に充填されたガス圧により推力が発生する増速ピストンであることを特徴とする請求項1または2に記載の液圧式打撃装置。
- 前記付勢手段を作動させないときに、前記付勢手段を前記ピストンと当接しない位置まで退避させる作動選択手段を備える請求項1~3のいずれか一項に記載の液圧式打撃装置。
- 前記切換弁機構は、少なくとも前記ピストン後室を前記高圧回路と前記低圧回路とに交互に切換えて前記ピストンを駆動するように構成され、
前記増速ピストンへの圧油供給通路は、前記ピストン後室に圧油を供給する通路から分岐して設けられている請求項3に記載の液圧式打撃装置。 - 前記高圧回路から前記付勢手段への圧油供給通路に、前記付勢手段に近接する位置に付勢アキュムレータを設けたことを特徴とする請求項3に記載の液圧式打撃装置。
- 前記圧油供給通路に、前記付勢アキュムレータよりも圧油供給源側であり、かつ、前記付勢アキュムレータに近接する位置に、前記付勢手段への圧油の供給のみを許容する方向規制手段を設けたことを特徴とする請求項7に記載の液圧式打撃装置。
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KR20180014779A (ko) | 2018-02-09 |
US20180207782A1 (en) | 2018-07-26 |
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