WO2005080052A1 - 打撃装置 - Google Patents
打撃装置 Download PDFInfo
- Publication number
- WO2005080052A1 WO2005080052A1 PCT/JP2004/015246 JP2004015246W WO2005080052A1 WO 2005080052 A1 WO2005080052 A1 WO 2005080052A1 JP 2004015246 W JP2004015246 W JP 2004015246W WO 2005080052 A1 WO2005080052 A1 WO 2005080052A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- piston
- receiving surface
- chamber
- switching valve
- Prior art date
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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
- B25D9/14—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
Definitions
- the present invention relates to a hydraulic hitting device or the like, and more particularly, to a hitting device capable of adjusting a hitting force according to the hardness of a rock or the like to be crushed.
- Patent Document 1 JP-A-8-216051
- the present invention has been made in view of such a point, and an object thereof is to make it possible to adjust the amount of increase in the impact force when the hardness of a crushed rock or the like is harder than in the above-described conventional example. It is to provide a hitting device.
- the invention according to claim 1 has a piston having a striking pressure receiving surface on which a fluid pressure such as hydraulic pressure acts upon striking and a reversing pressure receiving surface on which the fluid pressure acts upon inversion.
- a striking device in which a ston is mounted in a cylinder so as to be able to advance and retreat in the axial direction, wherein the piston is provided with an additional pressure receiving surface for striking capable of pressurizing the fluid pressure.
- the switching means sets the A striking device characterized by switching to a state in which the fluid pressure can be supplied to an additional pressure receiving surface.
- the switching means for switching between a state in which the supply of the fluid pressure acting on the hitting pressure receiving surface capable of pressurizing the fluid pressure formed in the piston and a state in which the supply of the fluid pressure is not possible is performed by the piston
- the state is switched to a state where the fluid pressure can be supplied to the additional pressure receiving surface for striking.
- the invention according to claim 2 is the invention according to claim 1, wherein the switching means is controlled by a fluid pressure rising due to the rebound.
- the switching means is controlled by the fluid pressure which rises due to the rebound, it becomes easy for the switching means to detect the rebound.
- the switching means is controlled by a first fluid path switching unit (for example, a switching valve) and the first fluid path switching unit.
- a second fluid path switching unit the first fluid path switching unit being controlled by a fluid pressure rising due to the rebound, and the second fluid path switching unit having a fluid flowing to the striking additional pressure receiving surface. Switching between a state in which pressure is supplied and a state in which pressure is not supplied.
- the first fluid path switching unit of the switching means switches the fluid path under the control of the fluid pressure rising due to the rebound, and the switching of the fluid path causes the second fluid path switching unit to operate the additional pressure receiving device for the impact. Since fluid pressure is supplied to the surface, it is easy for the piston to automatically increase the striking force even when the change in hydraulic pressure due to the rebound is small.
- FIG. 1 is an explanatory view schematically showing a striking device according to a first embodiment.
- FIG. 2 is an explanatory diagram showing an operation state of the impact device of FIG. 1.
- FIG. 3 is an explanatory view showing an operation state following FIG. 2;
- FIG. 4 is an explanatory diagram showing an operation state subsequent to FIG. 3.
- FIG. 5 is an explanatory view schematically showing a striking device according to a second embodiment.
- FIG. 6 is an explanatory diagram showing an operation state of the impact device of FIG. 5.
- FIG. 7 is an explanatory diagram showing an operation state subsequent to FIG. 6.
- FIG. 8 is an explanatory diagram showing an operation state subsequent to FIG. 7;
- FIG. 9 is an explanatory diagram showing features of a hitting device according to a third embodiment.
- FIG. 10 is an explanatory diagram showing an operation state of the impact device of FIG. 9.
- FIG. 1 schematically shows a striking device according to a first embodiment
- FIGS. 2 to 4 show the operating states of the striking device sequentially.
- the impact device uses hydraulic pressure as fluid pressure.
- the cylinder 1 includes a hydraulically operated cylinder 1 and a piston 2 that slides on the inner wall of the cylinder 1 to move in and out of the axial direction.
- the right force shown in the figure also includes a minimum diameter portion 2a, a small diameter portion 2b having a diameter larger than the minimum diameter portion 2a, a first large diameter portion 2c, a groove-shaped communication portion 2d, and a second large diameter. It has a portion 2e and a middle diameter portion 2f (the diameter is larger than the small diameter portion 2b and smaller than the large diameter portions 2c and 2e).
- the illustrated right end face of the first large diameter portion 2c is a ring-shaped striking pressure receiving surface 2u
- the illustrated right end face force of the small diameter portion 2b is an S ring-shaped striking additional pressure receiving surface 2v.
- the left end surface in the figure of the second large diameter portion 2e is a ring-shaped pressure receiving surface for reversal 2w.
- a chisel 3 is provided on the left side of the middle diameter portion 2f of the piston 2 in the drawing.
- a high-pressure chamber 4, a pilot chamber 5, a low-pressure chamber 6, a first pressurizing chamber 7, and a second pressurizing chamber 8 are each formed in the shape of a ring in the order of leftward force in the drawing. Further, a gas filling chamber 9 is formed at the right end of the cylinder 1 in the figure.
- the high-pressure chamber 4, the pilot chamber 5, the low-pressure chamber 6, the first pressurizing chamber 7, the second pressurizing chamber 8, and the gas filling chamber 9 are each partitioned by the inner wall of the cylinder 1.
- a hydraulic pump 14 serving as a hydraulic pressure source is connected to the high-pressure chamber 4 and disposed so as to be connectable to the first pressurizing chamber 7 via the first switching valve 11. Further, the oil tank 15 is connected to the low-pressure chamber 6 and is disposed so as to be connectable to the first pressurizing chamber 7 via the throttle valve 18 and the first switching valve 11.
- the first switching valve 11 is disposed so as to switch the hydraulic path so that either the hydraulic pump 14 or the oil tank 15 is connected to the first pressurizing chamber 7. This switching is performed by the hydraulic pressure of the pilot chamber 5 applied to the pilot port of the first switching valve 11, and as shown in FIG.
- the pilot chamber 5 communicates with the low-pressure chamber 6 through the communication portion 2d, and the pilot
- the first switching valve 11 When the oil pressure in the chamber 5 is low (the oil pressure in the oil tank 15), the first switching valve 11 is in a state of connecting the oil tank 15 to the first pressurizing chamber 7 via the throttle valve 18.
- the throttle valve 18 functions to delay a decrease in the hydraulic pressure of the first pressurizing chamber 7.
- the pilot chamber 5 is connected to the high-pressure chamber 4 via the middle diameter portion 2f and the inner wall of the cylinder 1, and the hydraulic pressure of the pilot chamber 5 is high (the hydraulic pressure of the hydraulic pump 14).
- the first switching valve 11 switches to a state in which the hydraulic pump 14 is connected to the first pressurizing chamber 7.
- the switching means 101 for switching the hydraulic pressure of the second pressurizing chamber 8 includes a second switching valve 12 and a third switching valve 13.
- the hydraulic pressure of the first pressurizing chamber 7 is connected so as to be applied to the pilot port of the second switching valve 12 via the check valve 16.
- a throttle valve 17 is connected in parallel with the check valve 16.
- the second switching valve 12 disconnects either the hydraulic pump 14 or the oil tank 15 for the third time. It is arranged to switch the hydraulic path so as to be connected to the pilot port of the switching valve 13! This switching is performed by the hydraulic pressure of the first pressurizing chamber 7 which is connected to the pilot port of the second switching valve 12, and as shown in FIG. When the pressure of the tank 15 is increased, the second switching valve 12 connects the hydraulic pump 14 to the pilot port of the third switching valve 13.
- the third switching valve 13 is arranged to switch the hydraulic path so that either the first pressurizing chamber 7 or the oil tank 15 is connected to the second caropressure chamber 8. This switching is performed by the hydraulic pressure applied to the pilot port of the third switching valve 13. As shown in FIG. 1, when the hydraulic pressure of the pilot port is high (the hydraulic pressure of the hydraulic pump 14), the third switching is performed. The valve 13 is in a state in which the oil tank 15 is connected to the second pressurizing chamber 8, and as shown in FIG. 3, when the oil pressure of the pilot port becomes low (the oil pressure of the oil tank 15), the third switching valve 13 is turned on. The state is switched to a state in which the first pressurizing chamber 7 and the second pressurizing chamber 8 are connected.
- the hitting device having the above configuration operates as follows.
- the tip of the piston 2 (the tip of the middle diameter portion 2f) is at the hit point (the position where the chisel 3 is hit).
- the reversing pressure receiving surface 2w of the hydraulic pressure piston 2 of the high pressure chamber 4 receives a reversing force (rightward force in the figure), and the impact pressure receiving surface 2u is applied by the hydraulic pressure (low pressure) of the first pressure chamber 7.
- the leftward force in the figure and the additional pressure receiving surface 2v does not receive the force (the leftward force) from the hydraulic pressure (low pressure) in the second pressurizing chamber 8, so that the piston 2 moves rightward in the figure.
- the state shown in FIG. 2 is obtained.
- the state shown in Fig. 2 is a state in which the impact stroke is started.
- the tip of the piston 2 is at the top dead center, and the pilot chamber 5 communicates with the high-pressure chamber 4 through the gap between the inner wall of the cylinder 1 and the middle diameter portion 2f, so that the first switching valve 11 is switched.
- the hydraulic pressure of the first pressurizing chamber 7 becomes high.
- the hydraulic pressure in the second pressurizing chamber 8 remains at a low pressure. Since the area of the impact pressure receiving surface 2u receiving the hydraulic pressure of the first pressure chamber 7 is larger than the area of the reversing pressure receiving surface 2w receiving the hydraulic pressure of the high pressure chamber 4, the piston 2 moves to the left in the figure.
- the first chamber 11 communicates with the low pressure chamber 6 by switching the slot chamber 5, and the first switching valve 11 switches.
- 7 is the first switching valve Even if the oil pressure is connected to the oil tank 15 via the throttle valve 11 and the throttle valve 18, the hydraulic pressure of the first pressurizing chamber 7 is maintained at a substantially high pressure for a while because of the throttle valve 18. In this state, the rebound of the piston 2 striking the chisel 3 for crushing rock (not shown) becomes larger than a predetermined value, and the rebound causes the hydraulic pressure of the first pressurizing chamber 7 to become high (the hydraulic pressure of the hydraulic pump 14).
- the second switching valve 12 switches to a state in which the oil tank 15 is connected to the pilot port of the third switching valve 13. Thereby, the third switching valve 13 is switched, and the first caropressure chamber 7 is connected to the second pressurizing chamber 8 via the third switching valve 13.
- the pilot chamber 5 communicates with the high-pressure chamber 4 as in FIG. 2, so that the first switching valve 11 is switched, and the hydraulic pump 14 is switched to the second switching valve 11 via the first switching valve 11.
- the first pressure chamber 7 is connected to the first pressure chamber 7, and the first pressure chamber 7 is connected to the second pressure chamber 8 via the third switching valve 13. For this reason, the hydraulic pressure in the first pressurizing chamber 7 and the second pressurizing chamber 8 becomes high.
- both the striking pressure receiving surface 2u receiving the hydraulic pressure in the first pressurizing chamber 7 and the additional pressure receiving surface 2v receiving the hydraulic pressure in the second pressurizing chamber 8 receive a leftward force in the drawing.
- the chisel 3 is struck by a leftward force as shown in the figure, which is obtained by adding the force received by the additional pressure receiving surface 2v by the hydraulic pressure of the second pressurizing chamber 8 to the force in the case of.
- the throttle valve 17 functions to delay the decrease in the hydraulic pressure of the pilot port of the second switching valve 12, so that the state of the second switching valve 12 is maintained until the piston 2 hits the chisel 3. . Since the force received by the additional pressure receiving surface 2v is proportional to the area of the additional pressure receiving surface 2V, the force received by the additional pressure receiving surface 2v can be changed by changing the area of the additional pressure receiving surface 2v.
- the switching means 101 for switching between a state in which the hydraulic pressure acting on the additional pressure receiving surface 2v for striking and capable of pressurizing the hydraulic pressure formed in the piston 2 can be supplied and a state in which the hydraulic pressure cannot be supplied are provided.
- the hydraulic pressure can be supplied to the additional pressure receiving surface 2v when the rebound of the piston 2 due to the recoil when the piston 2 hits the chisel 3 at the advancing end (hit point) of the piston 2 is larger than a predetermined value. Since the state is switched, the hydraulic pressure can also automatically increase the striking force received by the piston 2 when the rebound is greater than a predetermined value. Further, since the switching means 101 is controlled by the hydraulic pressure which rises due to the rebound, it becomes easy for the switching means 101 to detect the rebound.
- the second switching valve 12 serving as the first fluid path switching section of the switching means 101 is controlled by the hydraulic pressure rising by the rebound to switch the oil path, and the switching of the oil path causes the switching of the second fluid path. Since the third switching valve 13 serving as a part supplies hydraulic pressure to the additional pressure receiving surface 2v, it is easy to automatically increase the striking force that the piston 2 also receives hydraulic pressure. Further, since the second switching valve 12 can be made smaller than the third switching valve 13, it is easy to form the second switching valve 12 integrally with the cylinder 1.
- the second embodiment is as follows.
- the impact device according to the second embodiment is a modified example of the first embodiment, and uses hydraulic pressure as a fluid pressure similarly to the first embodiment.
- the cylinder 21 is provided with an operating cylinder 21 and a piston 22 which is movable in the axial direction within the cylinder 21.
- the right force shown in the figure also includes a small-diameter portion 22a, a middle-diameter portion 22b having a larger diameter than the small-diameter portion 22a, a first large-diameter portion 22c having a larger diameter than the middle-diameter portion 22b, a groove-shaped communication portion 22d, and a middle-diameter.
- a second large diameter portion 22e having a larger diameter than the portion 22b and a minimum diameter portion 22f having a smaller diameter than the small diameter portion 22a are provided.
- the illustrated right end face of the first large diameter portion 22c is a ring-shaped impact pressure receiving surface 22u
- the illustrated right end face of the middle diameter portion 22b is a ring-shaped additional impact pressure receiving surface 22v.
- it is a reversing pressure receiving surface 22w in the shape of a crown on the left end surface in the figure of the second large diameter portion 22e.
- a chisel 23 is provided on the left side of the minimum diameter portion 22f of the piston 22 in the drawing.
- a second pressurizing chamber 28 On the inner wall of the cylinder 21, a second pressurizing chamber 28, a high-pressure chamber 24, a pilot chamber 25, a low-pressure chamber 26, and a first pressurizing chamber 27 are respectively formed in the shape of a ring from the right side in the figure. Further, a gas filling chamber 29 is formed at the right end of the cylinder 21 in the figure.
- a hydraulic pump 34 serving as a hydraulic pressure source is connected to the high-pressure chamber 24 and arranged so as to be connectable to the first pressurizing chamber 27 via the first switching valve 31.
- the low-pressure oil tank 35 is connected to the low-pressure chamber 26 and arranged so as to be connectable to the first pressurizing chamber 27 via the first switching valve 31.
- the first switching valve 31 is arranged to switch the hydraulic path so that either the hydraulic pump 34 or the oil tank 35 is connected to the first pressurizing chamber 27. This switching is performed by the hydraulic pressure of the pilot chamber 25 applied to the pilot port of the first switching valve 31, and as shown in FIG. 5, the pilot chamber 25 is moved through the gap between the inner wall of the cylinder 21 and the middle diameter portion 22b.
- the first switching valve 31 When the hydraulic pressure in the pilot chamber 25 is high (the hydraulic pressure of the hydraulic pump 34) and the first switching valve 31 is connected to the high-pressure chamber 24 and the hydraulic pump 34 is connected to the first pressurizing chamber 27, as shown in FIG. As shown, when the pilot chamber 25 communicates with the low-pressure chamber 26 via the communication portion 22d and the hydraulic pressure in the pilot chamber 25 is low (the hydraulic pressure of the oil tank 35), the first switching valve 31 connects the oil tank 35 to the 1 Switches to the state where it is connected to the pressure chamber 27.
- the switching means 102 for switching the hydraulic pressure of the second pressurizing chamber 28 includes a second switching valve 32 and a third switching valve 33.
- the hydraulic pressure of the high-pressure chamber 24 is connected so as to be applied to a pilot port of the second switching valve 32 via a check valve 36.
- a throttle valve 37 is connected in parallel with the check valve 36.
- the second switching valve 32 switches the hydraulic path so that either the hydraulic pump 34 or the oil tank 35 is connected to the pilot port of the third switching valve 33. It is arranged in. This switching is performed by the hydraulic pressure of the high-pressure chamber 24 connected to the pilot port of the second switching valve 32. As shown in FIG. 5, usually, the second switching valve 32 switches the hydraulic pump 34 to the third switching position.
- the rebound of the piston 22 causes the hydraulic pressure of the high-pressure chamber 24 to become high (the hydraulic pressure of ),
- the second switching valve 32 switches to a state in which the oil tank 35 is connected to the pilot port of the third switching valve 33.
- the throttle valve 37 functions to delay a decrease in the hydraulic pressure of the pilot port of the second switching valve 32.
- the third switching valve 33 is disposed so as to switch the hydraulic path so as to connect either the hydraulic pump 34 or the oil tank 35 to the second pressurizing chamber 28. ⁇ This switching is performed by the hydraulic pressure applied to the pilot port of the third switching valve 33.
- the third switching valve 33 When the hydraulic pressure of the pilot port of the third switching valve 33 is high (the hydraulic pressure of the hydraulic tank 34), the third switching valve 33 is When the oil tank 35 is connected to the second pressurizing chamber 28 and the hydraulic pressure of the pilot port of the third switching valve 33 becomes low (the oil pressure of the oil tank 35), the third switching is performed as shown in FIG.
- the valve 33 switches to a state in which the hydraulic pump 34 is connected to the second pressurizing chamber 28.
- an accumulator 38 is connected to the hydraulic pump 34
- an accumulator 39 is connected to the oil tank 35.
- the hitting device having the above configuration operates as follows.
- the tip of the piston 22 is at a hit point (a position where the chisel 23 is hit), and the hydraulic pressure of the second pressurizing chamber 28 is low.
- the hydraulic pressure in the first pressurizing chamber 27 is high, and the hydraulic pressure in the first pressurizing chamber 27 is also reduced by the reversing force (force in the right direction in the figure) received by the reversing pressure receiving surface 22w of the piston 22. Since the force received by the striking pressure receiving surface 22u of the piston 22 that also receives the hydraulic pressure (the force in the left direction in the figure) is greater than that of the piston 22, the piston 22 moves rightward in the figure and enters the state shown in FIG.
- the state shown in Fig. 6 is a state in which the impact stroke is started.
- the tip of the piston 22 is at the top dead center, and the pilot chamber 25 communicates with the low-pressure chamber 26, so that the first switching valve 31 is switched, and the hydraulic pressure in the first pressurizing chamber 27 becomes low.
- the hydraulic pressure in the second pressurizing chamber 28 remains at a low pressure. Then, since the striking pressure receiving surface 22u receives the oil pressure of the high-pressure chamber 24, the piston 22 moves leftward in the drawing to strike the chisel 23.
- the area of the reversing pressure receiving surface 22w that receives the oil pressure of the first pressure chamber 27 is equal to the area of the impact pressure receiving surface 22u that receives the oil pressure of the high pressure chamber 24, and the additional pressure receiving surface that receives the oil pressure of the second pressure chamber 28. Since the area is larger than the total area of 22v, the piston 22 moves rightward in the figure to be in the state of FIG.
- the tip of the piston 22 is at the top dead center, and the pilot chamber 25 communicates with the low-pressure chamber 26, so that the first switching valve 31 is switched, and the oil tank 35 is connected to the first switching valve 31. Is connected to the first pressurizing chamber 27 via For this reason, the piston 22 hits the chisel 23 by receiving the leftward force in the figure by the force of the striking pressure receiving surface 22u receiving the oil pressure of the high-pressure chamber 24 and the additional pressure receiving surface 22v receiving the oil pressure of the second pressure chamber 28. .
- the switching means 102 for switching between a state in which the hydraulic pressure acting on the additional pressure receiving surface 22v for striking, which is capable of pressurizing the hydraulic pressure formed in the piston 22, can be supplied and a state in which the hydraulic pressure cannot be supplied.
- Force When the piston 22 hits the chisel 23 at the advancing end (strike point) of the piston 22 and the rebound of the piston 22 due to the recoil is larger than a predetermined value, when the hydraulic pressure can be supplied to the additional pressure receiving surface 22v.
- the hydraulic pressure can also automatically increase the striking force received by the piston 22.
- the switching means 102 is controlled by the hydraulic pressure which rises due to the rebound, it becomes easy for the switching means 102 to detect the rebound.
- the second switching valve 32 and the third switching valve 33 are switched, and the hydraulic pump is connected to the additional pressure receiving surface 22v.
- the oil pressure of 34 does not work.
- the second switching valve 32 serving as the first fluid path switching unit of the switching means 102 is controlled by the hydraulic pressure that rises due to the rebound, and switches the oil path. By switching this oil path, the second fluid path switching is performed.
- the third switching valve 33 serving as a part supplies hydraulic pressure to the additional pressure receiving surface 22v, it is easy to automatically increase the striking force that the piston 22 also receives hydraulic pressure. Further, since the second switching valve 32 can be made smaller than the third switching valve 33, it is easy to form the second switching valve 32 integrally with the cylinder 21.
- the third embodiment is as follows.
- the third embodiment is a modification of the second embodiment, and FIG. 9 shows the characteristics of the hitting device according to the third embodiment, and FIG. 10 shows the operation state of the hitting device of FIG. .
- the striking device uses hydraulic pressure as the fluid pressure similarly to the second embodiment.
- the cylinder 41 includes a hydraulically operated cylinder 41 and a piston 42 that can move in and out of the cylinder 41 in the axial direction.
- the piston 42 also has a right-hand force shown in the order of a first diameter part 42a, a second diameter part 42b having a diameter larger than the first diameter part 42a, a third diameter part 42c having a diameter larger than the second diameter part 42b, and a groove-shaped part.
- the communication part 42d, a fourth diameter part 42e having a diameter larger than the third diameter part 42c, and a fifth diameter part 42f having a diameter smaller than the fourth diameter part 42e are provided.
- the illustrated right end surface of the third radial portion 42c is a ring-shaped impact pressure receiving surface 42u
- the illustrated right end surface force of the second radial portion 42b is an S ring-shaped additional pressure receiving surface 42v for impact.
- the left end surface in the figure of the fourth diameter portion 42e is a ring-shaped reverse pressure receiving surface 42w.
- the area of the reversing pressure receiving surface 42w is formed to be larger than the sum of the area of the impact pressure receiving surface 42u and the area of the additional pressure receiving surface 42v.
- a chisel 43 is provided on the left side of the fifth diameter portion 42f of the piston 42 in the drawing.
- a second pressurizing chamber 48, a high-pressure chamber 44, a pilot chamber 45, a first low-pressure chamber 46a, a second low-pressure chamber 46b, and a first pressurizing chamber 47 are respectively formed on the inner wall of the cylinder 41 in order from the right side in the figure. It is formed in a shape.
- the oil tank (not shown) is connected to the first pressurizing chamber 47 via the first low-pressure chamber 46a, the second low-pressure chamber 46b, and the first switching valve 51.
- the first low-pressure chamber 46a communicates with the second low-pressure chamber 46b via a gap between the inner wall of the cylinder 41, the third diameter portion 42c, and the communication portion 42d.
- the first low-pressure chamber 46a is connected to the inner wall of the cylinder 41 and the communication portion 42d. Is communicated with the second low-pressure chamber 46b through the gap of the second low-pressure chamber 46b. Others are the same as in the second embodiment.
- the hitting device having the above configuration operates as follows.
- the state shown in FIG. 10 is a state at the time of the start of impact where the tip of the piston 42 is at the top dead center. Since the piston 42 moves to the left in the drawing at the time of impact, oil in the gap between the inner wall of the cylinder 41 and the fifth diameter portion 42f on the left side of the reversing pressure receiving surface 42w is supplied from the first pressurizing chamber 47 to the first switching valve. By returning to the gap between the inner wall of the cylinder 41 and the communicating portion 42d via the 51 and the second low-pressure chamber 46b, the resistance of the oil discharged from the first pressurizing chamber 47 can be reduced. Therefore, the speed at which the piston 42 moves to the left in the drawing increases, and the chisel 43 can be hit hard. Others are the same as the second embodiment.
- the switching means 101 and 102 include the second switching valve and the third switching valve, respectively.
- the present invention is not limited to this. It may be configured with only three switching valves.
- the pilot port of the third switching valve receives the instantaneous increase in the hydraulic pressure due to the rebound of the piston, and It is necessary to switch the switching valve.
- the hydraulic pressure is not limited to the hydraulic pressure, but may be the pneumatic pressure that can drive the piston.
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- Automation & Control Theory (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004044757A JP2007196293A (ja) | 2004-02-20 | 2004-02-20 | 打撃装置 |
JP2004-044757 | 2004-02-20 |
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Publication Number | Publication Date |
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WO2005080052A1 true WO2005080052A1 (ja) | 2005-09-01 |
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PCT/JP2004/015246 WO2005080052A1 (ja) | 2004-02-20 | 2004-10-15 | 打撃装置 |
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JP (1) | JP2007196293A (ja) |
WO (1) | WO2005080052A1 (ja) |
Families Citing this family (1)
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US9840000B2 (en) | 2014-12-17 | 2017-12-12 | Caterpillar Inc. | Hydraulic hammer having variable stroke control |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02298475A (ja) * | 1989-05-10 | 1990-12-10 | Mazda Motor Corp | 打撃工具 |
-
2004
- 2004-02-20 JP JP2004044757A patent/JP2007196293A/ja active Pending
- 2004-10-15 WO PCT/JP2004/015246 patent/WO2005080052A1/ja active Application Filing
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02298475A (ja) * | 1989-05-10 | 1990-12-10 | Mazda Motor Corp | 打撃工具 |
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