WO2018131689A1 - 液圧式打撃装置 - Google Patents
液圧式打撃装置 Download PDFInfo
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- WO2018131689A1 WO2018131689A1 PCT/JP2018/000703 JP2018000703W WO2018131689A1 WO 2018131689 A1 WO2018131689 A1 WO 2018131689A1 JP 2018000703 W JP2018000703 W JP 2018000703W WO 2018131689 A1 WO2018131689 A1 WO 2018131689A1
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- piston
- chamber
- pressure
- stroke
- striking device
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- 230000001965 increasing effect Effects 0.000 claims abstract description 60
- 230000007246 mechanism Effects 0.000 claims abstract description 29
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 230000001133 acceleration Effects 0.000 description 23
- 238000010586 diagram Methods 0.000 description 18
- 230000008859 change Effects 0.000 description 12
- 230000014509 gene expression Effects 0.000 description 9
- 230000007423 decrease Effects 0.000 description 7
- 238000004904 shortening Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 239000007787 solid Substances 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000009527 percussion Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000644 propagated effect Effects 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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Classifications
-
- 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
- B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B1/00—Percussion drilling
- E21B1/12—Percussion drilling with a reciprocating impulse member
- E21B1/24—Percussion drilling with a reciprocating impulse member the impulse member being a piston driven directly by fluid pressure
- E21B1/26—Percussion drilling with a reciprocating impulse member the impulse member being a piston driven directly by fluid pressure by liquid pressure
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B1/00—Percussion drilling
- E21B1/38—Hammer piston type, i.e. in which the tool bit or anvil is hit by an impulse member
-
- 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
Definitions
- the present invention relates to a hydraulic hitting device such as a rock drill or a breaker.
- 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 able to advance and retreat.
- 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 front chamber 110 formed by the difference in diameter between the large diameter portion 201 and the medium diameter portion 203 and the pressure receiving area of the piston rear chamber 111 formed by the difference in diameter between the large diameter portion 202 and the small diameter portion 204 are The chamber 111 side is larger (hereinafter, the difference in pressure receiving area between the piston front chamber 110 and the piston rear chamber 111 is referred to as “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 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.
- FIG. 9 shows a piston displacement-velocity diagram for a long stroke and a short stroke in a conventional hydraulic striking device.
- the dotted line is a diagram for setting the long stroke
- L 1 is the full stroke
- L 2 is the piston reverse acceleration section (the piston forward control port communicates with the piston front chamber after the piston starts moving backward).
- valve is switched until after the piston chamber is switched to high pressure
- L 3 is a piston retraction deceleration section (piston rear chamber is switched to the high pressure until the piston reaches the rear stroke end)
- V long is the striking point Piston speed.
- the solid line is a diagram of a short-stroke setting, similarly, L 1'is full stroke, L 2'piston backward acceleration zone, L 3'piston backward deceleration section, V short is at piston speed of the striking point is there.
- the position of the piston advance control port is moved forward.
- the front chamber is connected to a high pressure
- the piston advance control port is connected to a low pressure. It is sealed by the piston large diameter part. If the position of the piston advance control port is moved forward, the length of the seal between the front chamber will be shortened, and there will be a problem that leakage will increase and efficiency will be reduced. There is a limit to shortening the stroke.
- the present invention has been made paying attention to such a problem, and without changing the hydraulic circuit arrangement and maintaining the impact energy, shortening the piston stroke to increase the impact output. It is an object to provide a possible hydraulic striking device.
- 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 hydraulic striking device that is driven by pressure oil supplied and discharged from the piston control port, and is provided behind the piston.
- the biasing means includes a biasing means that abuts the piston in the middle of a piston retreating stroke and biases the piston forward, and the biasing means has a timing at which the biasing means and the piston start abutting, The piston is set earlier than the timing at which the piston is braked by the switching valve mechanism.
- the biasing means for biasing the piston forward by abutting against the piston at the timing when the braking force acts on the piston during the piston retreating stroke is provided. Since it is provided at the rear, the backward stroke of the piston is shortened, and the forward movement of the piston is accelerated and the piston speed does not decrease, so that high output can be achieved. At this time, if the pressure receiving area of the urging means does not change, the shortening amount of the reverse stroke is determined by the contact position between the piston and the urging means, so there is no need to change the hydraulic circuit arrangement such as the piston control port, There is no reduction in efficiency due to a decrease in seal length.
- FIG. 3 is a schematic diagram ((a) to (f)) showing an operating state of the first embodiment.
- FIG. 3 is a displacement-velocity diagram according to the first embodiment.
- FIG. 3 is a time-displacement diagram of the first embodiment.
- FIG. 3 is a displacement-speed diagram of the first embodiment, and shows a case where the contact position between the acceleration piston and the striking piston is changed.
- FIG. 3 is a displacement-speed diagram of the first embodiment, and shows a case where the thrust ratio between the speed increasing piston and the striking piston is changed.
- 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 the conventional hydraulic striking device.
- It is a displacement-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 alternately communicate with the high pressure circuit 101 and the low pressure circuit 102 via the piston rear chamber passage 121 by switching a switching valve 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 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 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 slidably contacted with the inner diameter of the pressurizing chamber 402, and the end surface 403 and the stepped surface 413 come into contact with each other, whereby a hydraulic chamber is defined 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 diameters of the piston inner diameter portion 203 and the rear end portion of the rod 310 are set to substantially the same dimensions.
- 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 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 striking mechanism of the hydraulic striking device according to the present embodiment is characterized in that a speed increasing piston 410 is provided on the back head 400 with respect to the conventional hydraulic striking device.
- the pilot chamber (not shown) of the switching valve mechanism 130 becomes low pressure through the valve control passage 122 and the oil discharge passage 123. Connected. As a result, the internal spool is switched, and the piston rear chamber 111 becomes low pressure by communicating the piston rear chamber passage 121 to the low pressure circuit 102, so that the piston 200 starts to move backward. (See the figure (a))
- the piston 200 is in the middle of the reverse stroke of the piston, before the piston 200 is retracted and the piston advance control port 112 is opened, that is, after the switching valve mechanism 130 is switched.
- the piston 200 contacts the acceleration piston 410 at a timing before the chamber 111 becomes high pressure and the piston 200 is braked.
- the thrust (referred to as “auxiliary thrust”) by the speed increasing piston 410 of the present embodiment acts on the piston 200 (see FIG. 5B).
- the piston 200 continues to move backward, the piston advance control port 112 is opened, the switching valve mechanism 130 is switched, and the piston rear chamber 111 is pressurized to be braked.
- the above-mentioned auxiliary thrust and the thrust due to the pressure receiving area difference between the front chamber 110 and the rear chamber 111 (referred to as “normal thrust”) act on the piston 200 together (see FIG. 10C).
- the piston 200 continues to move backward due to inertia.
- the piston 200 moves forward from backward 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. 4D).
- the piston 200 Immediately after the piston 200 turns forward, the pressure oil accumulated in the high-pressure accumulator 140 is quickly supplied to the pressurizing chamber 402. Therefore, the piston 200 is strongly urged by the acceleration piston 410 and accelerates quickly. Subsequently, until the stepped surface 413 comes into contact with the end surface 403 and reaches the front stroke of the speed increasing piston 410, the piston 200 is subjected to the auxiliary thrust by the speed increasing piston 410 and the pressure receiving area difference between the front chamber 110 and the rear chamber 111. Since the normal thrust acts as a sum, the acceleration becomes a large value corresponding to the auxiliary thrust (from FIG. 2D to FIG. 2E).
- the piston 200 moves away from the speed increasing piston 410 only by the normal thrust ((e) in the figure)
- the rod 310 is hit after reaching a predetermined hitting position ((f) in the figure). Thereafter, the hitting operation is continuously performed by repeating the above-described cycle.
- FIG. 3 shows a displacement-velocity diagram in the hydraulic striking device of this embodiment.
- a case where the speed increasing piston 410 of the present embodiment is not provided is also indicated by a broken line (a diagram positioned at the rightmost in the figure).
- the broken line portion has the same profile as the long stroke diagram in the conventional hydraulic striking device (FIG. 9), and each stroke is L 1 to L 3 .
- the aspect ratio is changed with respect to FIG. 9 for convenience of explanation.
- Displacement shown in FIG. 3 - the relationship between the speed diagram and FIG. 2, until the piston 200 abuts against the accelerated piston 410 retracts corresponds to L 21.
- the piston 200 comes into contact with the acceleration piston 410 (FIG. 2 (b)), retreats while being braked, and the rear chamber 111 is switched to a high pressure (FIG. 2 (c)), that is, during reverse acceleration.
- the state where only the backward force and auxiliary thrust due to the front chamber pressure act on the piston 200 corresponds to the L 2b section.
- the reverse deceleration section where the reverse thrust is applied to the piston 200 (FIG. 2D), that is, the combined thrust of the auxiliary thrust and the normal thrust acts on the piston 200 corresponds to the L 3b section.
- the piston impact speed is not affected by the contact position with the acceleration piston 410 Piston mass m, front chamber pressure area S f , rear chamber pressure area S r , acceleration piston pressure area S b , impact the pressure P w.
- the front / rear chamber pressure receiving area difference ⁇ S S r ⁇ S f and the ratio of the front chamber pressure receiving area S f to ⁇ S is n. As shown in FIG.
- Equation (7) is equal to Equation (5). That is, the piston kinetic energy E 12 ′ when the piston 200 integrated with the speed increasing piston 410 is separated from the speed increasing piston 410 in the forward travel is equal to that when the piston without the speed increasing piston passes the same position in the forward travel. equal to the piston kinetic energy E 12. That is, it can be seen that the piston speed does not change. Again, when compared with no speed-increasing piston has accelerated the piston, the case with the speed increasing piston, regardless of the collision position of the piston 200, and the job E B speed increasing piston 410 reduces the piston kinetic energy by retraction stroke Conversely, work E F increase the piston kinetic energy in the forward stroke is equal absolute value orientation different.
- Equation (10) the required time T 21 of the backward stroke L 21 interval is given by the following expression (11).
- equation (21) By substituting equation (20) into equation (18), the required time T 1b of the preceding travel distance L 3b + L 2b section becomes equation (21) below.
- One hit cycle Tc is obtained by adding equations (11), (15), (17), (21), and (25), and obtaining the following equation (26).
- one striking cycle Tc is a function of the striking pressure, the piston mass, the front and rear chamber pressure receiving area, the piston stroke, the valve switching position, and the pressure receiving area of the acceleration piston 410 and the collision position. is there.
- the number of impacts is calculated by changing the contact position for several combinations of piston 200 and speed increasing piston 410 with different specifications, and focusing on the relationship between the impact position and the number of impacts, the timing of contact is generally switched. The earlier the timing is reached (in other words, the more the contact position moves before the valve switching position), the more the number of hits rises, but the peak hits at a certain timing and position. Tend to decrease.
- the rate of change of the number of hits and the position where the peak is reached vary depending on the specifications of the piston 200, that is, the relationship between the pressure receiving area of the front and rear chambers and the pressure receiving area of the speed increasing piston 410.
- FIG. 5 shows a case where the contact positions of the piston 200 and the acceleration piston 410 are changed back and forth with reference to FIG. 3 without changing the specifications of the piston 200 and the acceleration piston 410.
- the piston speed at the time of contact changes from V 21 to V 210 and V 211 , and the stroke L until the valve is switched. 2b is changed to L 2b0 and L 2b1.
- the piston speed V 12 when the piston 200 moves away from the speed increasing piston 410 changes to V 120 and V 121 .
- the subsequent stroke speed diagram draws the same locus as in the case without the acceleration piston. Therefore, the piston striking speed V 1 was constant.
- the contact position L 21 of the piston 200 and the speed-increasing piston 410 is constant, the specifications of the piston 200 and the speed-increasing piston 410, shows the case of changing the basis of FIG.
- piston speed when the valve retraction switching changes to V 2b' and V 2b "from V 2b, the valve stroke L 3b from retracted control position until the piston after the top dead center is changed to L 3b 'and L 3b ".
- the stroke speed diagram after the acceleration piston 410 leaves draws the same locus. Therefore, the piston striking speed V 1 was constant.
- a short stroke can be achieved.
- the short stroke is performed by collecting and releasing kinetic energy by the high-pressure accumulator 140, so that no additional power is required.
- the piston striking speed V 1 of the when the piston 200 may be replaced with a short-stroke strikes the rod 310 does not change. Therefore, since the number of hits is increased without reducing the hit energy per hit, the output of the hitting mechanism can be increased.
- a short stroke can be achieved without changing the hydraulic circuit arrangement such as the piston control port, and there is no reduction in efficiency due to the reduction in the seal length.
- the stroke shortening amount can be flexibly set according to the contact position between the piston 200 and the speed increasing piston 410 and the relationship between the reverse thrust of the piston 200 and the thrust of the speed increasing piston 410. Control can be easily performed by extending or shortening the length of the small diameter portion or increasing or decreasing the pressure receiving area of the speed increasing piston 410.
- the piston 200 is not limited to a solid shape, and a through hole or a blind hole may be formed in the axial center portion of the piston 200.
- the large-diameter portions before and after the piston 200 may have a diameter difference instead of the same outer diameter.
- the outer diameter of the small diameter portion of the speed increasing piston 410 may not be aligned with the outer diameter of the piston middle diameter portion.
- the hydraulic striking device according to the above-described embodiment is a so-called “rear chamber high / low pressure switching type” liquid in which the piston front chamber is always at a high pressure and the piston rear chamber is switched to a high / low pressure to move the piston 200 forward and backward.
- the pressure-type 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 pressure oil accumulated in the high-pressure accumulator 140 is promptly supplied to the pressurizing chamber 402 via the pressurizing passage 404.
- the present invention is not limited to this.
- the biasing accumulator 142 may be further provided.
- the second embodiment is different from the configuration of the first embodiment in that the urging accumulator 142 dedicated to the acceleration piston 410 is provided in the pressurizing passage 404 ′ as shown in FIG.
- the biasing accumulator 142 is interposed at a position near the pressurizing chamber 402 with respect to the pressurizing passage 404 ′. If it is the structure of 2nd embodiment, while arrange
- the piston 200 abuts on the speed increasing piston 410 during the retreating process, and the braking force by the pressure oil acting on the piston 200 and the forward thrust acting on the speed increasing piston 410 cooperate.
- the piston stroke is shortened.
- there is an impact that is, the two collide. Is inevitable.
- the hydraulic striking device of the first embodiment shown in FIG. 1 when the piston 200 moves backward and collides with the speed increasing piston 410, the impact is applied to the pressurizing passage 404 via the pressure oil in the pressurizing chamber 402.
- the pressure oil is applied to the switching valve mechanism 130, the operation of the switching valve mechanism 130 may become unstable.
- the passage area relative to the pressure receiving area is increased. It can be seen that the passage 404 side is smaller.
- the fact that 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 pressure loss on the speed increasing piston 410 side is relatively large, there is a possibility that the speed increasing action of the present invention may not be sufficiently exerted in a phase where the piston 200 and the speed increasing piston 410 move forward integrally.
- increasing the passage area as a countermeasure is limited in terms of cost and layout. Therefore, in the second embodiment, in the pressurizing passage 404 ′ connecting the pressurizing chamber 402 and the high pressure circuit 101, further on the upstream side of the biasing accumulator 142 (that is, on the side of the pump P that is the supply source of the pressure oil).
- a check valve as direction restricting means that allows only supply of pressure oil to the pressurizing chamber 402 side.
- the utilization efficiency of the urging accumulator 142 is dramatically increased by the direction restricting means. Therefore, the urging accumulator 142 is used as a pressure oil supply source for exerting the speed increasing action of the present invention. It is more preferable in taking a role. That is, the pressure passage 404 'does not need to take pressure loss into consideration, and the passage area can be set small. Moreover, since the utilization efficiency of the urging accumulator 142 is improved by the direction restricting means, the shock buffering action of the pressure oil in the pressurizing chamber 402 is also effectively performed. Although the check valve has been described as an example of the direction regulating means, the same effect can be obtained even if a throttle is employed instead of the check valve.
- the resistance generated in the throttle is proportional to the square of the flow velocity of the pressure oil passing therethrough, and therefore, when flowing into the pressurizing chamber 402 and when the speed increasing piston 410 moves backward, the pressurizing chamber 402 to the pump P.
- the value of outflow is excessively large. Therefore, when the throttle allows the pressure oil to be supplied to the pressurizing chamber 402 and restricts the movement of the pressure oil in the reverse direction, an excessively large value flows out to the pressurizing chamber 402 side. It functions as a direction regulating means that allows only supply of pressure oil.
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Abstract
Description
フロントヘッド300は、シリンダ100の前側に配設され、ロッド310が前進後退可能に摺嵌される。フロントヘッド300の内部には、打撃室301が形成され、打撃室301内でロッド310の後端をピストン200の先端が打撃する。バックヘッド400Pは、シリンダ100の後側に配設され、バックヘッド400Pの内部に形成された後退室401P内をピストン200の後端部が前後に移動する。
これにより、大径部201と中径部203の径差からなるピストン前室110の受圧面積、および大径部202と小径部204の径差からなるピストン後室111の受圧面積は、ピストン後室111側の方が大きくなっている(以下、ピストン前室110とピストン後室111の受圧面積の差を「受圧面積差」という)。
高圧回路101はポンプPに接続され、高圧回路101の途中部分に高圧アキュムレータ140が設けられている。低圧回路102はタンクTに接続され、低圧回路102の途中部分に低圧アキュムレータ141が設けられている。切換弁機構130は、シリンダ100Pの内外の適所に配設される公知の切換弁であり、後述するバルブ制御通路122から給排される圧油によって作動し、ピストン後室111を高圧と低圧とに交互に切換える。
ピストン前進制御ポート112は、前側のショートストロークポート112a、および後側のロングストロークポート112bを有し、ショートストロークポート112aとバルブ制御通路122との間に設けられた可変絞り112cの操作によってショートストロークとロングストロークの間を無断階に切換え可能になっている。可変絞り112cを全開にするとショートストロークとなり、全閉にするとロングストロークとなる。
切換弁機構130は、ピストン前進制御ポート112がピストン前室110と連通してバルブ制御通路122に圧油が供給されると、ピストン後室通路121を高圧回路101に連通する位置に切換えられる。また、切換弁機構130は、ピストン後退制御ポート113が排油ポート114と連通して圧油がバルブ制御通路122からタンクTへと排出されると、ピストン後室通路121を低圧回路102に連通する位置へと切換えられる。
ここで、図8において、従来の液圧式打撃装置では、ピストン前進制御ポート112には、ロングストロークポート112bとショートストロークポート112aとが併設されていることを説明したが、ショートストローク化することによって、ロングストロークの設定よりも打撃数を増加することができる。
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。
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。
上記ピストン200は、シリンダ100の内部に摺嵌されることで、シリンダ100内にピストン前室110とピストン後室111とがそれぞれ画成されている。ピストン前室110は、ピストン前室通路120を介して高圧回路101に常時接続されている。一方、ピストン後室111は、後述する切換弁130の切換えによって、ピストン後室通路121を介して高圧回路101と低圧回路102とをそれぞれ交互に連通可能になっている。
ピストン前室110とピストン後室111との間には、前方から後方に向けてそれぞれ所定間隔離隔して、ピストン前進制御ポート112、ピストン後退制御ポート113、および排油ポート114が設けられている。ピストン前進制御ポート112とピストン後退制御ポート113には、バルブ制御通路122から分岐した通路がそれぞれ接続されている。排油ポート114は排油通路123を介してタンクTに接続されている。
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。
一般的な液圧式打撃装置においては、ピストン200とロッド310の打撃界面、すなわち、ピストン中径部203とロッド310の後端部の外径は略同じ寸法に設定されている。その理由は、ピストン200がロッド310を打撃して発生する応力波の伝達効率を高めるためであり、同様の理由で、本実施形態では、増速ピストン410の小径部411の外径がピストン小径部204の外径と略同径に設定されている。
本実施形態の液圧式打撃装置は、ピストン前室110が常時高圧接続されているので、ピストン200は常時後方へと付勢され、ピストン後室111が切換弁機構130の作動により高圧接続されると、上記受圧面積差によってピストン200は前進し、ピストン後室111が切換弁機構130の作動により低圧接続されるとピストン200は後退する。
ここで、本実施形態の液圧式打撃装置の打撃機構は、従来の液圧式打撃装置に対して、バックヘッド400に増速ピストン410を設けた点に特徴がある。
そして、本実施形態の液圧式打撃装置では、一のピストン後退行程の途中であって、ピストン200が後退してピストン前進制御ポート112が開く前、すなわち、切換弁機構130が切り換って後室111が高圧となりピストン200が制動を受ける前のタイミングでピストン200が増速ピストン410に当接する。これにより、ピストン200には、本実施形態の増速ピストン410による推力(「補助推力」とする)が作用する(同図(b)参照)。
その後もピストン200は慣性によって後退を続けるが、上述の補助推力と通常推力とが合算してピストン200に作用するため、ピストン200は、通常の後方ストロークエンドよりも前方の位置で後退から前進に転じる。この間に加圧室402から排出された圧油は高圧アキュムレータ140に蓄圧される(同図(d)参照)。
やがて、上記段付面413が端面403に当接して増速ピストン410の前方ストロークに達すると、ピストン200は、増速ピストン410と離れて通常推力のみで前進し(同図(e))、所定の打撃位置まで達してロッド310を打撃する(同図(f))。以下、上述のサイクルを繰り返すことにより、打撃動作が連続して行われる。
図3に示す変位-速度線図と図2との関係は、ピストン200が後退して増速ピストン410に当接するまで(図2(a))はL21に相当する。また、ピストン200が増速ピストン410と当接し(図2(b))、制動を受けながら後退して後室111が高圧に切換えられる(図2(c))まで、すなわち、後退加速中のピストン200に、前室圧による後退力と補助推力のみが作用する状態はL2b区間に相当する。さらに、後方ストロークエンドまで後退(図2(d))、すなわち、ピストン200に補助推力と通常推力の合算推力が作用する後退減速区間はL3b区間に相当する。
図3に示すように、本実施形態の液圧式打撃装置においては、ピストン200が増速ピストン410と当接している区間以外は、ロングストローク仕様の打撃機構として作動しており、後退時の最大速度はV2からV21に変化しているが、ピストン200がロッド310を打撃する際の速度は、V1のままで変わらないことが見て取れる。
(1)ピストン打撃速度が増速ピストン410との当接位置に影響を受けないことについて
ピストン質量m、前室受圧面積Sf、後室受圧面積Sr、増速ピストン受圧面積Sb、打撃圧Pwとする。前後室受圧面積差ΔS=Sr-Sfとし、前室受圧面積SfのΔSに対する比をnとする。
図3に示すように、バルブ切換位置が打撃点からL2の距離にある打撃装置において、増速ピストン410がバルブ切換位置よりもL2b手前でピストン200と当接する場合、増速ピストンなしの場合のバルブ切換時のピストン後退最高速度をV2、その時のピストン運動エネルギをE2、増速ピストン410と衝突する時のピストン速度をV21とすると、その時のピストン運動エネルギE21は、以下の式(1)となる。
改めて、増速ピストンありを増速ピストンなしと比較すると、増速ピストンありの場合、ピストン200との衝突位置に関わらず、増速ピストン410が後退行程でピストン運動エネルギを減少させる仕事EBと、逆に、前進行程でピストン運動エネルギを増加させる仕事EFは向きが異なるだけで絶対値が等しい。つまり、
|EB|=|EF|=SbPW(L2b+L3b)
したがって、これらは相殺される。すなわち、増速ピストン410と当接前後のピストン200の運動エネルギは、増速ピストンなしの場合と何ら変わらないことになる。
図4において、各行程の所要時間を求める。まず、後退行程L21区間のピストン200に作用する力積と運動量変化の関係は、以下の式(8)となる。
実際に幾つかの異なる仕様のピストン200・増速ピストン410の組合せに対し、当接位置を変えて打撃数を計算し、衝突位置と打撃数の関係に着目すると、総じて当接するタイミングをバルブ切換タイミングよりも早くすればするほど(言い換えれば、当接位置をバルブ切換位置より前に移動するほど)打撃数は上昇するが、あるタイミング・位置でピークを迎え、それを超えると逆に打撃数が減少する傾向にある。打撃数の変化率やピークを迎える位置は、ピストン200の仕様、即ち前後室受圧面積の関係や増速ピストン410の受圧面積により変化する。
図5からわかるように、当接位置L21を、L210およびL211に変更すると、当接時のピストン速度は、V21からV210とV211へと変化し、バルブ切換までのストロークL2bは、L2b0とL2b1へと変化する。また、ピストン200が増速ピストン410から離れる際のピストン速度V12は、V120とV121へと変化する。しかし、いずれの場合も、その後のストローク速度線図は、増速ピストンなしの場合と同じ軌跡を描く。そのため、ピストン打撃速度V1は一定である。
図6からわかるように、ピストン後退時の推力に対して増速ピストン410の推力を増減すると、バルブ後退切替時のピストン速度は、V2bからV2b´とV2b"へと変化し、バルブ後退切換え位置からピストン後死点までのストロークL3bは、L3b´とL3b"へと変化する。しかし、いずれの場合も、増速ピストン410が離れて以降のストローク速度線図は、同じ軌跡を描く。そのため、ピストン打撃速度V1は一定である。
また、本実施形態の液圧式打撃装置では、ショートストローク化してもピストン200がロッド310を打撃する際のピストン打撃速度V1は変化しない。そのため、1打撃当たりの打撃エネルギを減ずることなく打撃数を増加させるので、打撃機構の高出力化が可能となる。
以上、本発明の一実施形態について図面を参照して説明したが、本発明に係る液圧式打撃装置は、上記実施形態に限定されるものではなく、本発明の主旨を逸脱しなければ、その他の種々の変形や各構成要素を変更することが許容されることは勿論である。
また、上記実施形態に係る液圧式打撃装置は、ピストン前室を常時高圧とするとともに、ピストン後室を高低圧に切り替えてピストン200を前進後退させる、いわゆる「後室高低圧切換え式」の液圧式打撃装置を例に説明したが、これに限定されない。
また、例えば上記第一実施形態では、ピストン200が前進に転じた直後、高圧アキュムレータ140に蓄圧された圧油が加圧通路404を介して加圧室402へと速やかに供給され、これにより、ピストン200が増速ピストン410によって強力に付勢されて速やかに加速する例を示したが、これに限定されず、例えば、図7に第二実施形態を示すように、増速ピストン410専用の付勢アキュムレータ142を更に備える構成とすることができる。
第二実施形態の構成であれば、付勢アキュムレータ142を加圧室402の近傍に配置することで、アキュムレータの利用効率を高め、また、切換弁機構130の作動への影響を抑制するとともに、増速ピストン410の作動の一層の安定化を図ることができる。
ここで、図1に示す、第一実施形態の液圧式打撃装置において、ピストン200が後退して増速ピストン410に衝突すると、その衝撃は加圧室402の圧油を介して加圧通路404に伝搬して切換弁機構130へ達するところ、切換弁機構130に圧油の衝撃が作用すると切換弁機構130の作動が不安定となるおそれがある。
ここで、全ての油圧回路において、通路面積が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に示す、第一実施形態液圧式打撃装置において、高圧通路121とピストン後室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すると、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。受圧面積に対して通路面積が小さいということは圧力損失が大きいということであり、すなわち、高圧通路121に対して加圧通路404は相対的に圧力損失が大きいといえる。
なお、方向規制手段として逆止弁を例に説明したが、逆止弁に代えて絞りを採用しても同様の作用効果を得ることができる。すなわち、絞りで発生する抵抗は、通過する圧油の流速の二乗に比例することから、加圧室402へと流入する場合と、増速ピストン410の後退に伴い加圧室402からポンプPへと流出する場合とでは、流出する方が過剰に大きい値となる。したがって、絞りは加圧室402への圧油の供給を許容するとともに逆方向への圧油の移動を規制する際、流出する方が過剰に大きい値となるため、加圧室402側への圧油の供給のみを許容する方向規制手段として機能する。
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
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
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
403 端面
404 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
P ポンプ
T タンク
Claims (5)
- 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、
前記シリンダの前記ピストン前室と前記ピストン後室との間に配設され、前記ピストンの前後進動によって前記高圧回路と前記低圧回路とに接断されるピストン制御ポートとを備え、前記切換弁機構を前記ピストン制御ポートから給排される圧油によって駆動する液圧式打撃装置であって、
前記ピストンの後方に設けられて前記ピストンにピストン後退行程の途中で当接して前記ピストンを前方へと付勢する付勢手段を備え、
前記付勢手段は、当該付勢手段と前記ピストンとが当接を開始するタイミングが、前記ピストンが前記切換弁機構によって制動を受けるタイミングよりも早く設定されてい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に記載の液圧式打撃装置。
- 前記高圧回路には、高圧回路用の高圧アキュムレータが介装されており、
前記増速ピストンは、前記ピストンの後方に設けられた加圧室内に摺嵌され、
前記加圧室は、前記高圧アキュムレータが介装された位置よりも下流側の位置で前記高圧回路に接続された加圧通路を介して前記高圧回路からの圧油が供給されるように構成されている請求項2に記載の液圧式打撃装置。 - 前記加圧通路には、前記加圧室の近傍の位置に、増速ピストン用の付勢アキュムレータが介装されている請求項3に記載の液圧式打撃装置。
- 前記加圧通路に、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、前記加圧室への圧油の供給を許容するとともに逆方向への圧油の移動を規制する方向規制手段を更に備える請求項4に記載の液圧式打撃装置。
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PCT/JP2018/000703 WO2018131689A1 (ja) | 2017-01-12 | 2018-01-12 | 液圧式打撃装置 |
Country Status (7)
Country | Link |
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US (1) | US11207769B2 (ja) |
EP (1) | EP3569362B1 (ja) |
JP (1) | JP7099964B2 (ja) |
KR (1) | KR102425266B1 (ja) |
CN (1) | CN110177658B (ja) |
FI (1) | FI3569362T3 (ja) |
WO (1) | WO2018131689A1 (ja) |
Families Citing this family (1)
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US11686157B1 (en) * | 2022-02-17 | 2023-06-27 | Jaime Andres AROS | Pressure reversing valve for a fluid-actuated, percussive drilling tool |
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2018
- 2018-01-12 EP EP18739319.4A patent/EP3569362B1/en active Active
- 2018-01-12 CN CN201880005777.3A patent/CN110177658B/zh active Active
- 2018-01-12 JP JP2018561432A patent/JP7099964B2/ja active Active
- 2018-01-12 KR KR1020197018769A patent/KR102425266B1/ko active IP Right Grant
- 2018-01-12 US US16/477,355 patent/US11207769B2/en active Active
- 2018-01-12 FI FIEP18739319.4T patent/FI3569362T3/fi active
- 2018-01-12 WO PCT/JP2018/000703 patent/WO2018131689A1/ja unknown
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Also Published As
Publication number | Publication date |
---|---|
US20200391368A1 (en) | 2020-12-17 |
JPWO2018131689A1 (ja) | 2019-11-07 |
FI3569362T3 (fi) | 2023-03-03 |
KR20190101386A (ko) | 2019-08-30 |
EP3569362B1 (en) | 2023-01-11 |
EP3569362A1 (en) | 2019-11-20 |
EP3569362A4 (en) | 2020-01-15 |
CN110177658A (zh) | 2019-08-27 |
US11207769B2 (en) | 2021-12-28 |
CN110177658B (zh) | 2022-12-20 |
KR102425266B1 (ko) | 2022-07-25 |
JP7099964B2 (ja) | 2022-07-12 |
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